CN115405503A

CN115405503A - Diaphragm pump or diaphragm compressor and method for controlling the same

Info

Publication number: CN115405503A
Application number: CN202110584253.8A
Authority: CN
Inventors: 高峰; 刘在祥; 陈艳凤; 蔡园丰; 王兵; 牛争艳
Original assignee: Shanghai Xingye Material Technology Co Ltd
Current assignee: Shanghai Xingye Material Technology Co Ltd
Priority date: 2021-05-27
Filing date: 2021-05-27
Publication date: 2022-11-29
Anticipated expiration: 2041-05-27
Also published as: CN115405503B

Abstract

The present application relates to a diaphragm pump or a diaphragm compressor and a control method thereof, wherein the diaphragm pump or the diaphragm compressor includes: the diaphragm is provided with a motor for providing driving force for the diaphragm; the drive path of the motor to the diaphragm includes: and the flywheel is arranged on the clutch on the transmission downstream side of the flywheel. The diaphragm pump or the diaphragm compressor can intermittently provide large short-time power and/or large short-time power for a long time, and is helpful for completing part of tasks which are difficult to complete originally.

Description

Diaphragm pump or diaphragm compressor and method for controlling same

Technical Field

The present application relates to a diaphragm pump or a diaphragm compressor and a control method thereof.

Background

The diaphragm pump and the diaphragm compressor are similar in structure, and both include: the power device comprises a working chamber, a power chamber, a diaphragm arranged between the working chamber and the power chamber, and a motor for providing power. When the diaphragm pump works, the motor drives the diaphragm to move through the power transmission system, so that the diaphragm extrudes working fluid in the working chamber to do work.

However, in practical applications, for various reasons, such as in the case of small power supply (e.g. small photovoltaic power supply) and in the case of very restricted space in which the equipment can be placed, it is not possible to arrange a very powerful motor in the diaphragm pump or the diaphragm compressor, which results in that it is not possible to perform certain tasks, such as delivering water from a low place to a height of several hundred meters, and compressing carbon dioxide as a refrigerant into a high pressure state or even into a liquid state, and the application scenarios are greatly limited.

Disclosure of Invention

The technical problem that this application will solve is: a diaphragm pump or a diaphragm compressor capable of intermittently supplying a large short-term power and/or a large short-term motive power for a long time, contributing to its accomplishment of a part of tasks which were difficult to accomplish originally, and a control method thereof are proposed.

The technical scheme of the application is as follows:

in a first aspect, the present application proposes a diaphragm pump or a diaphragm compressor comprising:

a diaphragm sheet, and

a motor providing a driving force to the diaphragm;

the drive path of the motor to the diaphragm includes:

flywheel, and

and the clutch is arranged on the transmission downstream side of the flywheel.

In an alternative design, the clutch is an electronically controlled clutch communicatively coupled to a controller, the controller configured to: controlling the clutch to be disengaged or engaged.

In an optional design, the controller further comprises a motor speed sensor for detecting a speed of the motor and communicatively connected to the controller, and the controller is configured to: and acquiring the rotating speed of the motor from the motor rotating speed sensor, and controlling the clutch to be disengaged or engaged based on the rotating speed.

In an optional design, the driving path of the motor to the diaphragm further includes a speed reducer disposed on a transmission downstream side of the flywheel.

In a second aspect, the present application proposes a control method applied to a diaphragm pump or a diaphragm compressor according to the first aspect, the control method comprising:

the clutch is controlled to alternately disengage and engage at a first frequency during operation of the electric machine.

In an alternative design, prior to the controlling the clutch to alternately disengage and engage at a first frequency, the control method further includes:

determining that the rotating speed of the motor is in a first rotating speed range; wherein the rated rotating speed of the motor is in the first rotating speed interval.

In an optional design, during the controlling of the clutch to alternately disengage and engage at a first frequency, the control method further comprises:

alternately disengaging and engaging the clutch at a third frequency if it is determined that the rotational speed of the electric machine is continuously decreasing for the first period of time; wherein a ratio of an engaging period to a disengaging period of the clutch in each cycle of the third frequency < a ratio of an engaging period to a disengaging period of the clutch in each cycle of the first frequency.

In an optional design, the control method further includes:

if the rotation speed of the motor is determined to be less than the first rotation speed threshold value, controlling the clutch to be continuously disengaged; wherein the first rotation speed threshold is smaller than a lower limit of the first rotation speed interval.

In an optional design, the control method further includes:

controlling the clutch to be continuously engaged if it is determined that the rotational speed of the electric machine is greater than a second rotational speed threshold; wherein the second rotation speed threshold is greater than an upper limit of the first rotation speed interval.

In a third aspect, the present application provides a control method applied to a diaphragm pump or a diaphragm compressor as set forth in the first aspect, the control method comprising:

acquiring the rotating speed of the motor in real time;

controlling the clutch to continuously disengage if it is determined that the rotational speed is less than a first rotational speed threshold;

controlling the clutch to continue to engage if it is determined that the rotational speed is greater than a second rotational speed threshold; wherein the second rotational speed threshold is not less than the first rotational speed threshold.

The application has at least the following beneficial effects:

1. in the diaphragm pump or the diaphragm compressor of the present application, a flywheel and a clutch located on the downstream side of transmission of the flywheel are disposed in a driving path from a power motor to a diaphragm. During the operation of the motor, the clutch can be alternately disengaged and engaged according to a set frequency, and then the driving path from the flywheel to the diaphragm can be alternately disengaged and engaged at the frequency, so that the flywheel and the diaphragm intermittently do work in each period time of the frequency, and the motor periodically stores energy to the flywheel. Generally, if the energy provided by the continuously operating motor keeps balance with the work energy consumption of the diaphragm which only does work in a part of the period of time in each cycle, the diaphragm pump or the diaphragm compressor can continuously and stably operate, and can intermittently provide large short-time power and/or large short-time power, which is helpful for the diaphragm pump or the diaphragm compressor to complete part of tasks which cannot be completed originally, such as smoothly conveying the working fluid to a required position or compressing the working fluid into a required state.

2. In addition, the diaphragm pump or the diaphragm compressor of this application can remove the power transmission to the diaphragm with the clutch separation when motor speed is lower, and then makes the motor only do work to the flywheel, makes the rotational speed and the kinetic energy of flywheel promote steadily. After the rotating speed of the motor is increased to a certain value, the clutch is engaged, the kinetic energy stored in the flywheel is utilized to do work on the working fluid, and intermittent high-power work can be done.

Drawings

In order to more clearly illustrate the technical solutions of the embodiments of the present application, the drawings of the embodiments will be briefly introduced below, and it is apparent that the drawings in the following description only relate to some embodiments of the present application and are not limiting on the present application.

Fig. 1 is a longitudinal sectional view of a diaphragm pump according to a first embodiment of the present application.

Fig. 2 is a schematic external view of a diaphragm pump according to an embodiment of the present invention.

Fig. 3 is a partial schematic structural diagram of a transmission system in an embodiment of the present application.

Fig. 4 is a partial cross-sectional view of a diaphragm pump according to a first embodiment of the present application.

Fig. 5 is a partial schematic structural diagram of a transmission system according to an embodiment of the present application.

Fig. 6 is a schematic transmission diagram of a transmission system according to a first embodiment of the present application.

Fig. 7 is a graph showing the relationship between the moving speed of the lower end of the first link and the included angle β according to the first embodiment of the present application.

FIG. 8 is a graph of piston travel speed versus angle β.

Fig. 9 is a variation of fig. 6.

Fig. 10 is a block diagram of a control system of the valve of fig. 1.

Fig. 11 is a partial structural schematic view of a diaphragm pump according to an embodiment of the present application.

Fig. 12 is a longitudinal sectional view of fig. 11.

Fig. 13 is an exploded view of fig. 11.

Fig. 14 is a longitudinal sectional view of a diaphragm pump in a first operation state according to a second embodiment of the present application.

Fig. 15 is a longitudinal sectional view of the diaphragm pump in the second operating state in the second embodiment of the present application.

Fig. 16 is a partial schematic structural diagram of a transmission system according to a second embodiment of the present application.

Fig. 17 is a longitudinal sectional view of a diaphragm pump in the third embodiment of the present application.

Fig. 18 is a partial schematic structural diagram of a transmission system in the third embodiment of the present application.

Fig. 19 is a schematic external view of a diaphragm pump according to a fourth embodiment of the present application.

FIG. 20 is a longitudinal sectional view of a diaphragm pump according to a fourth embodiment of the present invention

FIG. 21 is a schematic view of a portion of a transmission system according to a fourth embodiment of the present application.

Fig. 22 is a longitudinal sectional view of a diaphragm pump according to a fifth embodiment of the present application.

FIG. 23 is a schematic view of a portion of a transmission system according to a fifth embodiment of the present invention.

Fig. 24 is a longitudinal sectional view of a diaphragm pump in accordance with the sixth embodiment of the present application.

Fig. 25 is a block diagram of a control system of the clutch of fig. 24.

Fig. 26 is a longitudinal sectional view of a diaphragm pump in an embodiment seven of the present application.

Fig. 27 is an enlarged view of the X1 portion of fig. 26.

Fig. 28 is a block diagram showing a control system of the electric control valve in fig. 27.

Fig. 29 is a longitudinal sectional view of a diaphragm pump in an eighth embodiment of the present application.

Fig. 30 is an enlarged view of the X2 portion of fig. 29.

Fig. 31 is a block diagram showing the construction of a control system of the electrically controlled valve in fig. 30.

Fig. 32 is a longitudinal sectional view of a diaphragm pump in an embodiment nine of the present application.

Fig. 33 is a block diagram showing a control system of the discharge valve in fig. 32.

Fig. 34 is a longitudinal sectional view of a diaphragm pump in accordance with a tenth embodiment of the present application.

Fig. 35 is a block diagram showing a control system of the suction valve in fig. 34.

Fig. 36 is a longitudinal sectional view of a diaphragm pump in an eleventh embodiment of the present application.

Fig. 37 is an enlarged view of the X3 portion of fig. 36.

FIG. 38 is a transverse sectional view of a diaphragm pump in an eleventh embodiment of the present application

FIG. 39 is a schematic view of a portion of a transmission system according to an eleventh embodiment of the present application.

Fig. 40 is a longitudinal sectional view of a diaphragm pump according to a twelfth embodiment of the present application.

Fig. 41 is a longitudinal sectional view of a diaphragm pump in accordance with a thirteenth embodiment of the present application.

Fig. 42 is a transverse sectional view of a diaphragm pump in accordance with a thirteenth embodiment of the present application.

Fig. 43 is a longitudinal sectional view of a diaphragm pump in a fourteenth embodiment of the present application.

Fig. 44 is a partial exploded view of the diaphragm pump according to the fourteenth embodiment of the present invention.

Fig. 45 is a schematic external view of a diaphragm pump according to a fifteenth embodiment of the present application.

Fig. 46 is a longitudinal sectional view of a diaphragm pump in accordance with a fifteenth embodiment of the present application.

Fig. 47 is a partially enlarged view of fig. 46.

Fig. 48 is a schematic view of the portion of fig. 47 after the push-pull rod has been moved to the left.

Fig. 49 is a transverse sectional view of a diaphragm pump according to a fifteenth embodiment of the present application.

Fig. 50 is a longitudinal sectional view of a diaphragm pump in accordance with a sixteenth embodiment of the present application.

Fig. 51 is a longitudinal sectional view of a diaphragm pump in a seventeenth embodiment of the present application.

Fig. 52 is a longitudinal sectional view of a diaphragm pump in an eighteenth embodiment of the present application.

Fig. 53 is a longitudinal sectional view of a diaphragm pump in nineteenth embodiment of the present application.

Fig. 54 is a longitudinal sectional view of a diaphragm pump in embodiment twenty of the present application.

Fig. 55 is a schematic structural diagram of an air conditioning system according to twenty one embodiment of the present application.

Fig. 56 is a block diagram showing a control system of the throttle valve of fig. 55.

Fig. 57 is a schematic structural diagram of an air conditioning system according to twenty-two embodiments of the present application.

Fig. 58 is a block diagram showing the construction of a control system of the electric control valve in fig. 57.

Fig. 59 is a schematic structural diagram of an air conditioning system according to twenty-third embodiment of the present application.

Fig. 60 is a block diagram of a control system for the valve on the compressor of fig. 59.

In order to facilitate a reader to clearly observe the structure of the diaphragm pump or the diaphragm compressor, part of the attached drawings are specially hidden with working fluid and power fluid, and part of the attached drawings are hidden with a guide moving seat.

Description of the reference numerals:

a-working fluid, b-motive fluid, O-pivot axis of crankshaft;

1-a working chamber, 2-a power chamber, 2 a-a first half chamber, 2 b-a second half chamber, 3-a diaphragm, 3 a-a deformation fold of the diaphragm, 4-a piston, 5-a motor, 6-an inlet port, 7-an outlet port, 8-an intake valve, 9-an outlet valve, 10-a power fluid storage chamber, 11-a valve, 12-a reducer, 13-a crankshaft, 14-a first connecting rod, 15-a second connecting rod, 16-a push-pull rod, 17-a transmission chamber, 18-a third connecting rod, 19-a fourth connecting rod, 20-a fifth connecting rod, 21-a sixth connecting rod, 22-a pivot, 23-a guide and displacement seat, 23 a-a guide and displacement groove, 24-a flywheel, 25-a coupler, 26-a leather bag, 27-a barrier net, 28-a linear bearing, 29-a hoop, 30-a rigid ring sleeve, 31-a flexible ring sheet, 31a deformation fold of the flexible ring sheet, 32-a pressure bearing seat, 32 a-a ring groove, 33-a housing, 34-a ring, 35-a pressure sensor, 39-an electric control clutch cover, 39-an electric control valve;

100-compressor, 200-condenser, 300-throttle valve, 400-evaporator.

Detailed Description

In the description of the present specification and claims, the terms "first", "second", and the like, if any, are used solely to distinguish one from another object described, and not necessarily in any sequential or technical sense. Thus, an object defined as "first," "second," etc. may explicitly or implicitly include one or more of the object. Also, the use of the terms "a" or "an" and the like, do not denote a limitation of quantity, but rather denote the presence of at least one, and the terms "a" or "an" denote the presence of no less than two. As used herein, "plurality" means no less than two.

In the description of the present application and in the claims, the terms "connected," "mounted," "secured," and the like are used broadly, unless otherwise indicated. For example, "connected" may be a separate connection or may be integrally connected; can be directly connected or indirectly connected through an intermediate medium; may be non-detachably connected or may be detachably connected. The specific meaning of the foregoing terms in this application will be understood by those skilled in the art as the case may be.

In the description of the present application and in the claims, if there is an orientation or positional relationship indicated by the terms "upper", "lower", "horizontal", etc., based on the orientation or positional relationship shown in the drawings, it is merely for the convenience of clearly and simply describing the present application, and it is not intended to indicate or imply that the elements referred to must have a specific orientation, be constructed and operated in a specific orientation, and these directional terms are relative concepts, are used for descriptive and clarifying purposes, and may be changed accordingly depending on the orientation in which the components in the drawings are placed. For example, if the device in the figures is turned over, elements described as "below" other elements would then be oriented "above" the other elements.

In the description of the specification and claims of this application, the terms "based on" and "based on," if any, are used to describe one or more factors that affect the determination. The term does not exclude additional factors that influence the determination. That is, the determination may be based solely on these factors or at least partially on these factors. For example, the phrase "determine B based on a," in which case a is a factor that affects the determination of B, does not exclude that the determination of B may also be based on C.

In the description of the present specification and claims, the term "configured to" if present, may generally be interchangeable with "having 8230capabilities", "designed to", "for" or "capable", depending on the context.

Now, embodiments of the present application are described with reference to the drawings.

The first embodiment is as follows:

fig. 1 and 2 show a diaphragm pump, which is similar to some existing diaphragm pumps, and the diaphragm pump of this embodiment also includes an inlet port 6 and an outlet port 7 for a working fluid a, a working chamber 1 fluidly connected between the inlet port 6 and the outlet port 7, a power chamber 2, a diaphragm 3 sealingly disposed between the working chamber and the power chamber, a piston 4 movably disposed in the power chamber, and a motor 5 connected to the piston through a transmission system to drive the piston to reciprocate. An intake valve 8 is provided between the inlet port 6 and the working chamber 1, and an exhaust valve 9 is provided between the exhaust port 7 and the working chamber 1. It can be understood that the structure of the diaphragm pump of the present embodiment is also applicable to the diaphragm compressor.

The term "diaphragm 3 sealingly disposed between the working chamber and the power chamber" as used herein means that the diaphragm 3 is not only disposed between the working chamber 1 and the power chamber 2, but also seals and separates the working chamber 1 and the power chamber 2, so that the working fluid a in the working chamber 1 does not enter the power chamber 2, and the power fluid b in the power chamber 2 does not enter the working chamber 1.

The suction valve 8 and the discharge valve 9 are both check valves. Referring to figure 1, in use, the power chamber 2 is filled with a power fluid b. When the motor 5 drives the piston 4 to move leftward in fig. 1, the internal pressure of the power chamber 2 < the internal pressure of the working chamber 1, and the diaphragm 3 deforms leftward. The working chamber 1 increases in volume and the internal pressure decreases. At this time, the suction valve 8 is opened because the left side pressure is lower than the right side pressure, and the discharge valve 9 is closed because the left side pressure is lower than the right side pressure. The working fluid a in flow state at the inlet port 6 enters the working chamber 1 through the open suction valve 8. When the motor 5 drives the piston 4 to push the power fluid b to move rightwards in fig. 1, the diaphragm 3 deforms rightwards, and the volume of the working chamber 1 is reduced. At this time, the suction valve 8 is closed when the left pressure is higher than the right pressure, and the discharge valve 9 is opened when the left pressure is higher than the right pressure. The working fluid a in the working chamber 1 is discharged to the discharge port 7 through the open discharge valve 9, and is discharged through the discharge port 7. The operating motor 5 drives the piston 4 to reciprocate in the left-right direction in fig. 1, thereby constantly sucking the working fluid supplied to the inlet port 6 into the working chamber 1, and discharging the working fluid a sucked into the working chamber 1 to the outlet port 7 and out of the outlet port 7. The working fluid a is continuously fed in this way.

The motor 5 indirectly drives the piston 4 to reciprocate through a transmission system, and the moving piston 4 indirectly drives the diaphragm 3 to move by virtue of the power fluid b filled in the power chamber, so that the working fluid a is pumped in and pushed out. The motor 5 is operated to drive the diaphragm 3 to do work, the transmission system connecting the motor and the piston, the piston 4 and the power fluid b filled in the power chamber are all arranged on a driving path from the motor 5 to the diaphragm 3, and the driving path from the motor 5 to the diaphragm 3 comprises the transmission system, the piston 4 and the power fluid b filled in the power chamber.

The suction valve 8 and the discharge valve 9 having the above-mentioned functions are very common in the field of diaphragm pumps and diaphragm compressors and can be directly purchased in the market, and thus will not be described herein.

The power fluid b is usually hydraulic oil, the working fluid a is usually water, and the diaphragm pump is often used for conveying water.

Referring again to fig. 1, the diaphragm pump is also provided with a power fluid storage chamber 10 and a third valve 11 in addition to the suction valve 8 and the discharge valve 9 described above. Wherein the motive fluid storage chamber 10 communicates with the motive chamber 2 for receiving the motive fluid b discharged from the motive chamber 2 and for providing the motive fluid b to the motive chamber 2. A valve 11 is provided in the communication path between the motive fluid storage chamber 10 and the motive chamber 2 for opening and closing the communication path between the motive fluid storage chamber 10 and the motive chamber 2.

In addition, the diaphragm pump is provided with a flywheel 24 and a speed reducer 12 in a transmission path between the motor 5 and the piston 4, that is, in the aforementioned transmission system. Wherein the flywheel 24 is connected between the motor 5 and the speed reducer 12, and the speed reducer 12 is connected between the flywheel 24 and the piston 4. The flywheel 24 is connected between the motor 5 and the speed reducer 12, and the power provided by the motor 5 needs to be transmitted to the speed reducer 12 through the flywheel 24. The speed reducer 12 is connected between the flywheel 24 and the piston 4, and the power provided by the flywheel 24 needs to pass through the speed reducer 12 to be transmitted to the downstream piston 4 and the diaphragm 3. The reducer 12 functions to reduce the transmission ratio to raise the torque, and thus the driving force to which the piston 4 and the diaphragm 3 are subjected. The flywheel 24 serves to store energy and provide sufficient driving power and driving force to the diaphragm 3.

The diaphragm pump of the present embodiment is provided with the above-described motive fluid storage chamber 10, valve 11, and flywheel 24, and can intermittently apply work to the outside with a large power when the output power of the motor 5 itself is small. The specific analysis is as follows:

as shown with reference to fig. 1. In the starting stage of the motor 5, the rotating speed of the motor 5 and the flywheel 24 is low, the kinetic energy of the flywheel is low, and the motor 5 and the flywheel 24 cannot drive the diaphragm 3 to do work at high power. At this time, the valve 11 is opened. When the piston 4 moves to the right, the hydraulic oil in the power chamber 2 as the power fluid b easily flows into the power fluid storage chamber 10 through the valve 11 under the thrust action of the piston 4, and the hydraulic oil in the power chamber 2 does not obviously push the diaphragm 3 with higher load to deform and do work. When the piston 4 moves to the left, hydraulic oil in the power fluid storage chamber 10 is easily drawn into the power chamber 2 again. It is clear that neither pushing hydraulic oil from the power chamber 2 into the power fluid storage chamber 10 nor pumping hydraulic oil from the power fluid storage chamber 10 into the power chamber 2 consumes much power. In the process, the power provided by motor 5 and flywheel 24 to piston 4 is relatively small, motor 5 mainly applies work to flywheel 24, and the mechanical energy output by motor 5 is mainly converted into the kinetic energy of flywheel 24, so that the rotating speed of flywheel 24 is higher and higher, and the kinetic energy is larger and larger. Obviously, the rotation speed of motor 5 is positively correlated with the rotation speed of flywheel 24. Specifically, in the present embodiment, the rotation speed ratio of motor 5 to flywheel 24 is 1. When the rotational speed of the motor 5 has risen to a set value, for example, when the motor 5 reaches the rated rotational speed, the valve 11 is closed. The communication path of the motive fluid storage chamber 10 with the motive chamber 2 is cut off, and the hydraulic oil of the motive chamber 2 cannot enter the motive fluid storage chamber 10. The piston 4 moving to the right can only push hydraulic oil in the power chamber 2 to squeeze the diaphragm 3 to the right, so that the diaphragm 3 deforms to the right to squeeze working fluid a in the working chamber 1 to do work. Even if the working load of the diaphragm pump is large, the flywheel 24 storing a large amount of kinetic energy can apply a large rightward thrust to the piston 4, and further, the diaphragm 3 is pushed to deform rightwards by the hydraulic oil in the power chamber 2, and a sufficient pressure is applied to the working fluid a in the working chamber 1, so that a large-power work on the working fluid a, such as pushing water to hundreds of meters of high altitude, is completed.

The power source of the diaphragm pump is a motor 5, and the motor 5 drives the diaphragm 3 to move sequentially through a moving flywheel 24 and a piston 4 to do work. Based on this, it is clear that such a dynamic relationship exists: the motor 5 provides driving force for the flywheel 24, the piston 4 and the diaphragm 3, the flywheel 24 provides driving force for the piston 4 and the diaphragm 3, and the piston 4 provides driving force for the diaphragm 3.

If the valve 11 is kept in the closed state all the time during operation of the motor 5. The motor 5 as a power source cannot provide energy for the diaphragm 3 to work continuously with high power because of low power. The energy consumed by the diaphragm 3 to do work comes from the conversion of the additional electric energy by the motor 5 and the kinetic energy originally stored in the flywheel 24. Therefore, under the condition that the newly added energy continuously provided by the motor 5 cannot meet the requirement of continuously doing work by the diaphragm 3, the flywheel 24 provides the supplementary energy for the work of the diaphragm 3. This results in a continuous decrease in kinetic energy of flywheel 24 and a smaller and smaller rotational speed. This not only results in an unstable operating speed of the motor 5, but ultimately renders the diaphragm 3 inoperable because of insufficient energy supply. Thus, the present embodiment provides the following diaphragm pump control method to solve the foregoing problems, the control method including:

s101, during the operation of the motor 5, controlling the valve 11 to open and close alternately at a first frequency.

That is, during the operation of the motor 5, the valve 11 is alternately opened for a twenty-third duration-closed for a twenty-fourth duration-opened for a twenty-third duration-closed for a twenty-fourth duration \8230;, at a set first frequency. That is, the drive path (or drive force transmission path) of the control flywheel 24 to the diaphragm 3 is alternately disconnected and connected at the first frequency. In each cycle of this first frequency, the valve 11 has a continuous open duration and a continuous closed duration, the values of which can be set as desired. It will be appreciated that the greater the ratio of the opening duration to the closing duration of valve 11, the greater the proportion of flywheel 24 that is charged in each cycle; the smaller the ratio of the opening period to the closing period of the valve 11, the smaller the energy charging time ratio of the flywheel 24 in each cycle.

For example, during the operation of the motor, the valve 11 is opened and closed alternately at a frequency of 10 times/minute and 2 seconds and 4 seconds for each opening. Wherein 10 times/minute means that the valve is opened 10 times and the valve is closed 10 times every 1 minute, and the opening and closing are alternately performed. Specifically, valve open 2 seconds (open and hold open 2 seconds) -close valve 4 seconds (close and hold close 4 seconds) -valve open 2 seconds-close valve 4 seconds-valve close 4 seconds \8230;, and valve close 4 seconds.

During the operation of the motor 5, the valve 11 is opened and closed alternately according to the set first frequency, so that the driving path of the flywheel 24 to the diaphragm 3 is opened and closed alternately, the flywheel 24 and the diaphragm 3 do work intermittently in each cycle time of the first frequency, and the motor 5 stores energy to the flywheel 24 periodically. Generally, in each cycle time, for example, 2+4=6 seconds as above, the energy provided by the continuously operating motor 5 and the energy consumption for working of the diaphragm 3 only in a partial period (for example, 4 seconds as above) keep balance, and then the diaphragm pump can continuously and stably operate.

It will be appreciated that with the valve 11 closed, the flywheel 24 is engaged into the drive path of the diaphragm 3, and that the valve is closed for a period of time = the period of time for which the flywheel is engaged into the drive path of the diaphragm. When the valve 11 is opened, the flywheel 24 is disconnected from the drive path to the diaphragm 3, and the valve opening period = the disconnection period of the flywheel from the drive path to the diaphragm. For convenience of description, herein, the engagement period of the flywheel 24 to the drive path of the diaphragm 3 is simply referred to as "engagement period of the drive path", and the disconnection period of the flywheel 24 to the drive path of the diaphragm 3 is simply referred to as "disconnection period of the drive path".

It is not appropriate to adopt this control strategy of S101 if the motor 5 is rotating at a low speed (e.g., just started). Therefore, the control strategy of S101 may be adopted only when it is determined that the rotation speed of the motor 5 is in the set first rotation speed section. That is, during operation of the motor 5, if it is determined that the current rotational speed of the motor 5 is in the first rotational speed interval, the drive path of the flywheel 24 to the diaphragm 3 is controlled to be alternately disconnected and engaged at a first frequency.

The first rotation speed range is preferably a range around the rated rotation speed of the motor 5. For example, if the nominal rotational speed of the electric machine 5 is 10000 rpm, the first rotational speed interval can be selected to be an interval of 9000-11000 rpm.

Of course, the switching frequency of the valve 11 may be adjusted correspondingly when the motor 5 is in different rotational speed intervals. For example, if it is determined that the speed of the electric motor 5 is in a second speed interval, different from and not intersecting the first speed interval, and smaller than the first speed interval, the valve 11 is alternately opened and closed at a second frequency, different from the first frequency. That is, if it is determined that the rotation speed of the motor 5 is in the second rotation speed section, the drive path of the flywheel 24 to the diaphragm 3 is controlled to be alternately disconnected and engaged at the second frequency. The second frequency differs from the first frequency primarily by: the ratio of the engaging time length and the disconnecting time length of the flywheel to the diaphragm driving path in each period of the second frequency is not equal to the ratio of the engaging time length and the disconnecting time length of the flywheel to the diaphragm driving path in each period of the first frequency.

S102, in the process of the control valve 11 alternately opening and closing at the first frequency in S101, if it is detected that the rotation speed of the motor 5 is continuously reduced for the first time period, the control valve 11 alternately opening and closing at the third frequency; wherein the ratio of the closing period to the opening period of the valve 11 in each cycle of the third frequency < the ratio of the closing period to the opening period of the valve 11 in each cycle of the first frequency. The aforementioned first duration is typically several times to tens of times the single period of the first frequency.

That is, in the process of controlling the flywheel 24 to alternately open and engage the drive path of the diaphragm 3 at the first frequency in S101, if it is determined that the rotation speed of the motor 5 continuously decreases for the first time period, the flywheel 24 is controlled to alternately open and engage the drive path of the diaphragm 3 at the third frequency. Wherein the ratio of the engagement duration to the disengagement duration of the drive path in each cycle of the third frequency < the ratio of the engagement duration to the disengagement duration of the drive path in each cycle of the first frequency.

During operation of the motor 5, the rotational speed thereof may vary due to certain factors, if it is detected that the rotational speed of the motor 5 decreases continuously for a set, longer first period of time, for example for two minutes, indicating that the energy supplied by the motor 5 is less than the energy consumed by the diaphragm 3 to do work. Therefore, it is necessary to reduce the duty ratio of the working time of the diaphragm 3 or increase the duty ratio of the dead time of the flywheel 24. Thus, when it is detected that the rotation speed of the motor 5 continuously decreases for the first period, the control valve 11 is alternately opened and closed at the third frequency. Wherein the ratio of the engagement duration to the disengagement duration of the drive path in each cycle of the third frequency < the ratio of the engagement duration to the disengagement duration of the drive path in each cycle of the first frequency.

Illustratively, the third frequency may be: opening valve 4 sec-closing valve 2 sec- \ 8230; \ 8230;, switching was still cycled 10 times per minute. Of course, the third frequency can be adjusted to cycle on and off 3, 6, or 20 times per minute, etc.

It is known to those skilled in the art that the determination of whether the rotation speed of the motor 5 is continuously decreasing for the set first period of time may be performed by: in the process of the above-mentioned S101 control valve 11 alternately opening and closing at the first frequency, the rotation speed of the motor 5 is periodically acquired, and if the N motor rotation speeds acquired in the consecutive N cycles have a tendency to gradually decrease and the total time period of the aforementioned N cycles is equal to or greater than the first time period, it is said that the rotation speed of the motor 5 continuously decreases for the first time period. In some embodiments, a reduction threshold may also be provided, and the control valve 11 may be alternately opened and closed at the third frequency only when the rotation speed of the motor 5 is continuously reduced for the first period and the reduction value exceeds the set reduction threshold. Obviously, this control manner of setting the reduction threshold is included in the range of "if the rotation speed of the motor 5 is detected to be continuously reduced for the first period, the control valve 11 is alternately opened and closed at the third frequency".

S103, in the process of the control valve 11 alternately opening and closing at the third frequency in the above S102, if it is detected that the rotation speed of the motor 5 continuously decreases for the second period of time, the control valve 11 alternately opens and closes at the fourth frequency; wherein the ratio of the closing time period to the opening time period of the valve 11 in each cycle of the fourth frequency < the ratio of the closing time period to the opening time period of the valve 11 in each cycle of the third frequency.

That is, in the process of controlling the flywheel 24 to alternately open and engage with the third frequency in S102, if it is determined that the rotation speed of the motor 5 continuously decreases for the second period of time, the flywheel 24 is controlled to alternately open and engage with the fourth frequency in the driving path of the diaphragm 3; wherein the ratio of the engagement duration to the disengagement duration of the drive path in each cycle of the fourth frequency < the ratio of the engagement duration to the disengagement duration of the drive path in each cycle of the third frequency.

The rotational speed of the motor 5 is continuously reduced during a second period of time, which means that the energy supplied by the motor 5 is still less than the energy consumed by the diaphragm 3. Therefore, it is necessary to further reduce the duty ratio of the working time of the diaphragm 3 or further increase the duty ratio of the dead time of the flywheel 24. Thus, when it is detected that the rotation speed of the motor 5 continuously decreases for the second period of time, the control valve 11 is alternately opened and closed at the above-described fourth frequency.

Illustratively, at the fourth frequency: opening valve 5 seconds-closing valve 1 seconds-opening valve 5 seconds-closing valve 1 seconds \8230 \, 8230 @, still cycling 10 times per minute. Also illustratively, opening the valve for 10 seconds-closing the valve for 2 seconds-opening the valve for 10 seconds-closing the valve for 2 seconds \8230;, is closed.

S104, in the process of alternately opening and closing the control valve 11 at the third frequency in the above S102, if it is detected that the rotation speed of the motor 5 continuously increases in the third period, the control valve 11 is alternately opened and closed at the fifth frequency; wherein the ratio of the closing duration to the opening duration of the valve 11 in each cycle of the first frequency > the ratio of the closing duration to the opening duration of the valve 11 in each cycle of the fifth frequency > the ratio of the closing duration to the opening duration of the valve 11 in each cycle of the third frequency.

That is, in the process of controlling the flywheel 24 to alternately open and engage the drive path to the diaphragm 3 at the third frequency in S102, if it is determined that the rotation speed of the motor 5 continuously increases for the third period of time, the flywheel 24 is controlled to alternately open and engage the drive path to the diaphragm 3 at the fifth frequency; wherein a ratio of the engagement duration to the disengagement duration of the drive path in each cycle of the first frequency > a ratio of the engagement duration to the disengagement duration of the drive path in each cycle of the fifth frequency > a ratio of the engagement duration to the disengagement duration of the drive path in each cycle of the third frequency.

The rotational speed of the motor 5 is continuously increased during a third period of time, which means that the energy supplied by the motor 5 is greater than the energy consumed by the diaphragm 3. Therefore, the working time ratio of the diaphragm 3 can be properly increased, or the no-load energy storage time ratio of the flywheel 24 can be properly reduced, so as to improve the working efficiency of the motor 5. Thus, when it is detected that the rotation speed of the motor 5 is continuously increased for the third period of time, the control valve 11 is alternately opened and closed at the above-described fifth frequency.

Illustratively, at this fifth frequency: opening valve 3.5 seconds-closing valve 2.5 seconds-opening valve 3.5 seconds-closing valve 2.5 seconds \ 8230; \ 8230;, and.

S105, in the process of the control valve 11 alternately opening and closing at the first frequency in the above S101, if it is detected that the rotation speed of the motor 5 continuously increases for a fourth time period, the control valve 11 alternately opens and closes at a sixth frequency; wherein the ratio of the closing period to the opening period of the valve 11 in each cycle of the sixth frequency > the ratio of the closing period to the opening period of the valve 11 in each cycle of the first frequency.

That is, in the process of controlling the driving path of the flywheel 24 toward the diaphragm 3 to be alternately disconnected and connected at the first frequency in S101, if it is determined that the rotation speed of the motor 5 continuously increases for the fourth time period, the driving path of the flywheel 24 toward the diaphragm 3 is controlled to be alternately disconnected and connected at the sixth frequency; wherein a ratio of the engagement duration to the disengagement duration of the drive path in each cycle of the sixth frequency > a ratio of the engagement duration to the disengagement duration of the drive path in each cycle of the first frequency.

The rotational speed of the motor 5 is continuously reduced during a fourth period of time, which means that the energy supplied by the motor 5 is greater than the energy consumed by the diaphragm 3. Therefore, the working time ratio of the diaphragm 3 can be increased, or the no-load energy storage time ratio of the flywheel 24 can be shortened, so as to improve the working efficiency of the motor 5. Thus, when it is detected that the rotation speed of the motor 5 continuously decreases for the fourth time period, the control valve 11 is alternately opened and closed at the sixth frequency.

Illustratively, the sixth frequency may be: opening valve 4 sec-closing valve 11 sec- \ 8230; \ 8230;, cycling on and off 4 times per minute.

And S106, in the process of the control valve 11 alternately opening and closing at the sixth frequency in the above S105, if it is detected that the rotation speed of the motor 5 continuously increases for the fifth period of time, the control valve 11 alternately opens and closes at the seventh frequency. Wherein the ratio of the closing time period to the opening time period of the valve 11 in each cycle of the seventh frequency > the ratio of the closing time period to the opening time period of the valve 11 in each cycle of the sixth frequency.

That is, in the process of controlling the flywheel 24 to alternately open and engage the drive path to the diaphragm 3 at the sixth frequency in S105, if it is determined that the rotation speed of the motor 5 continuously increases in the fifth period, the flywheel 24 is controlled to alternately open and engage the drive path to the diaphragm 3 at the seventh frequency; wherein the ratio of the engagement duration to the disengagement duration of the drive path in each cycle of the seventh frequency > the ratio of the engagement duration to the disengagement duration of the drive path in each cycle of the sixth frequency.

The rotational speed of the electric motor 5 is continuously increased during a fifth time period, which means that the energy provided by the electric motor 5 is still greater than the work energy consumption of the diaphragm 3 during this fifth time period. Therefore, the working time ratio of the diaphragm 3 can be further increased, or the idle energy storage time ratio of the flywheel 24 can be further reduced, so that the working efficiency of the motor 5 can be further improved. Thus, when it is detected that the rotation speed of the motor 5 continuously decreases for the fifth period of time, the control valve 11 is alternately opened and closed at the above-described seventh frequency.

Illustratively, at this seventh frequency: valve 4 sec was opened-valve 12 sec was closed-valve 4 sec \8230; \\ \ 8230;, and.

S107, in the process of the above S105 in which the control valve 11 is alternately opened and closed at the sixth frequency, if it is detected that the rotation speed of the motor 5 is continuously decreased for the sixth period of time, the control valve 11 is alternately opened and closed at the eighth frequency; wherein the ratio of the closing period to the opening period of the valve 11 in each cycle of the sixth frequency > the ratio of the closing period to the opening period of the valve 11 in each cycle of the eighth frequency > the ratio of the closing period to the opening period of the valve 11 in each cycle of the first frequency.

That is, in the process of controlling the flywheel 24 to alternately open and engage the drive path to the diaphragm 3 at the sixth frequency in S105, if it is determined that the rotation speed of the motor 5 continuously increases in the sixth period, the flywheel 24 is controlled to alternately open and engage the drive path to the diaphragm 3 at the eighth frequency; wherein the ratio of the engagement duration to the disengagement duration of the drive path in each cycle of the sixth frequency > the ratio of the engagement duration to the disengagement duration of the drive path in each cycle of the eighth frequency > the ratio of the engagement duration to the disengagement duration of the drive path in each cycle of the first frequency.

The rotational speed of the motor 5 is continuously reduced during a sixth time period, which means that the energy supplied by the motor 5 is less than the energy consumed by the diaphragm 3 during this sixth time period. Therefore, the duty ratio of diaphragm 3 can be appropriately reduced, or the dead time ratio of flywheel 24 can be appropriately increased. Thus, when it is detected that the rotation speed of the motor 5 is continuously increased for the sixth period, the control valve 11 is alternately opened and closed at the above-described eighth frequency.

Illustratively, at the eighth frequency: opening valve 4 sec-closing valve for 10 sec- \ 8230; \ 8230;, respectively.

S108, if the rotation speed of the motor 5 is detected to be less than the first rotation speed threshold value, the control valve 11 is continuously opened; wherein the first rotation speed threshold is smaller than the lower limit of the first rotation speed interval.

I.e. if it is determined that the rotational speed of the motor 5 is less than a relatively small first rotational speed threshold, the drive path of the flywheel 24 towards the diaphragm 3 is controlled to be continuously disconnected.

The first speed threshold is a relatively small value which is smaller than the lower limit of the first speed interval. When the rotation speed of the motor 5 is less than the first smaller rotation speed threshold, it indicates that the energy of the motor 5 and the flywheel 24 is already seriously insufficient, so that the valve 11 can be continuously opened at this time to keep the driving path of the flywheel 24 to the diaphragm 3 in a disconnected state, so as to avoid serious overload of the motor 5.

S109, in the process of continuously opening the control valve 11 in S108, if it is detected that the rotation speed of the motor 5 is greater than the second rotation speed threshold, continuously closing the control valve 11; and the second rotating speed threshold value is not less than the first rotating speed threshold value.

That is, in the process of controlling the driving path of the flywheel 24 to the diaphragm 3 to be continuously disconnected, if it is determined that the rotation speed of the motor 5 is greater than the second rotation speed threshold value, the driving path of the flywheel 24 to the diaphragm 3 is controlled to be continuously engaged; and the second rotating speed threshold value is not less than the first rotating speed threshold value.

It is understood that after executing S108, flywheel 24 is always maintained in the idle energy storage state, and the energy provided by motor 5 is completely converted into the kinetic energy of flywheel 24. When the rotational speed of motor 5 and flywheel 24 is high enough and the kinetic energy is large enough, the membrane pump runs idle, if valve 11 is still kept open, and there is a waste of energy. Thus, when it is detected that the rotation speed of the motor 5 is greater than the second rotation speed threshold value, the valve 11 is switched from the continuously open state to the continuously closed state, so that the flywheel 24 is continuously engaged with the drive path of the diaphragm 3, and the flywheel 24 continuously drives the diaphragm 3 to apply work.

It is to be understood that "continuously" in "continuously open" and "continuously closed" and "alternately" in "alternately open and closed" are relative concepts in the present application. Continuously open means that the valve is kept in an open state, and continuously closed means that the valve is kept in a closed state; and alternately opening and closing the valve means periodically opening the valve for a preset period of time and closing the valve for a preset period of time at a set frequency.

It is to be understood that the execution of S109 is not necessarily premised on S108. In other embodiments, regardless of the operating state of the valve 11, the valve 11 may be controlled to be continuously closed as long as the rotation speed of the motor 5 is detected to be greater than the second rotation speed threshold.

The second rotation speed threshold value should not be smaller than the first rotation speed threshold value, and the second rotation speed threshold value is preferably a value not in the above-described first rotation speed range. More preferably, the second rotation speed threshold value is a value greater than the upper limit of the first rotation speed section.

Obviously, during the above-mentioned process of S109, if it is detected that the rotation speed of the motor 5 returns to the aforementioned first rotation speed interval, the valve 11 may be controlled to continue to open and close alternately at the first frequency.

In addition, we can also abandon the strategies of S101-S107 and use the strategies of S108 and S109 alone to control the diaphragm pump:

that is, if it is determined that the rotation speed of motor 5 is less than the first rotation speed threshold value, flywheel 24 is controlled to be continuously disconnected from the drive path to diaphragm 3. Controlling flywheel 24 to continue engaging the drive path of diaphragm 3 if it is determined that the speed of rotation of motor 5 is greater than the second speed threshold; and the second rotating speed threshold value is not less than the first rotating speed threshold value. In this control scheme using the strategies S108 and S109 alone, the second rotational speed threshold may be generally equal to the first rotational speed threshold. The disadvantages are that: the rotation speed of the motor 5 may be unstable.

As shown in fig. 10, in order to better implement the control strategy of S101-S109, the valve 11 of the present embodiment adopts an electrically controlled valve that can be opened and closed electrically, and is further provided with a motor speed sensor 34 for detecting the speed of the motor 5, and the motor speed sensor 34 and the valve 11 are both connected in communication with the controller 35. The controller 35 is configured to acquire the rotation speed of the motor 5 from the motor rotation speed sensor 34, and control the opening and closing of the valve 11 based on the rotation speed, so as to implement the control method. It is to be noted that the opening and closing of the control valve 11 may also not be based on the rotational speed of the motor 5. In other embodiments of the present application, the motor speed sensor 34 is removed and the valve 11 is controlled to "alternately open and close at a first frequency" using only the controller 35 in communication with the valve 11.

Specifically, the controller 35 includes a memory, a processor connected to the memory, and computer instructions stored in the memory and executable by the processor, and when the computer instructions are executed by the processor, the various control methods are implemented.

Such as:

during the operation of the motor 5, the controller 35 acquires the rotation speed of the motor 5 from the motor rotation speed sensor 34;

if it is determined that the rotational speed of the electric motor 5 is in the first rotational speed interval, the controller 35 sends a control command to the electrically controlled valve 11 so as to control the valve 11 to alternately open and close at a first frequency.

Another example is as follows:

if it is determined that the speed of rotation of the electric motor 5 is less than the first speed threshold, the controller 35 sends a command signal to the electronically controlled valve 11 to control the valve 11 to continuously open;

if it is determined that the speed of the electric motor 5 is greater than the second speed threshold, the controller 35 sends a different command signal to the electrically controlled valve 11 to control the valve 11 to close continuously; and the second rotating speed threshold value is not less than the first rotating speed threshold value.

For another example:

during operation of the motor 5, the controller 35 causes the valve 11 to alternately open and close at a first frequency by receiving a user command (e.g., pressing an operating button connected to the controller).

In the description of the above control method, "opening" the valve 11 generally includes two situations: 1) If the valve 11 is originally in the closed state, the controller 35 sends a command signal to the valve 11 to control the valve 11 to switch to the open state. 2) If the valve 11 is already in the open state, for example, if the valve 11 is normally open, the controller 35 may not send a command signal to the valve 11 to open the valve 11, but may send a command signal to the valve 11.

Similarly, two situations are generally also included for the "closed" valve 11: 1) If the valve 11 is originally in the open state, the controller 35 sends a command signal to the valve 11 to control the valve 11 to switch to the closed state. 2) If the valve 11 is already closed, for example, if the valve 11 is normally closed, the controller 35 may not act on the valve 11, or may send a command signal to the valve 11 to close the valve 11.

Thus, if the valve 11 is a normally closed valve, the "control valve 11 alternately opens and closes at a first frequency", this can be achieved: the controller 35 alternately sends and stops sending command signals to the valve 11 at a first frequency to cause the valve to open. When the controller 35 sends a command signal to open the valve 11, the valve 11 opens; when the controller 35 stops sending the command signal for opening the valve 11, the valve 11 is automatically closed. It is also within the scope of the present application to control valve closure that controller 35 stops sending command signals to open valve 11, causing normally closed valve 11 to close automatically. In particular only in that it "controls" the valve 11 to close, by stopping the transmission of the relevant signal or in what is called a non-functioning way.

The valve 11 is typically an electromagnetic valve, and for simplicity of control, the valve 11 is preferably a normally closed valve or a normally open valve.

Those skilled in the art will understand that: the obtaining of the rotation speed information of the motor 5 is one of the conditions for smoothly implementing the control methods of S101 to S109, for example, the rotation speed of the motor 5 may be obtained in real time during the operation of the motor 5, and once it is determined that the rotation speed of the motor satisfies the corresponding conditions, the control valve 11 may perform corresponding response actions, such as the control valve 11 alternately opening and closing at a first frequency when the rotation speed of the motor is determined to be in a preset first rotation speed interval, and the control valve 11 continuously opening when the rotation speed of the motor is determined to be greater than a preset second rotation speed threshold.

As mentioned above, the motor 5 does work outwards only when running at a high speed, one reason is that the flywheel 24 is also in a high-speed motion state and has a large kinetic energy, and the flywheel 24 running at a high speed and storing a large amount of kinetic energy can do work outwards with a large power. Therefore, the mass of flywheel 24 can be increased by increasing the mass of flywheel 24, preferably by 5kg or more, to increase the kinetic energy of flywheel 24 at high speed, and the mass of flywheel 24 can further increase the short-term power of the diaphragm pump.

Flywheel 24 is typically made of metal or carbon fiber.

Some motors 5 have a small output power when starting or running at a low speed, and only after the rotating speed of the motor 5 reaches a certain value, the output power is considerable, which is also one of the reasons for adopting the design.

It will be appreciated that even when the motor 5 is operating at high speed, its power is not significantly increased. As long as the kinetic energy of flywheel 24 is large enough, it can do work with large power outwards only by means of the inertia of flywheel 24. The kinetic energy of flywheel 24 is mainly derived from its speed, and the upper limit of the speed of flywheel 24 is determined by motor 5, so we can select motor 5 as a high-speed motor with rated rotation speed not less than 10000 r/min. Of course, the speed of the transfer system and the piston 4 must not be too high, otherwise mechanical damage is easily caused. Therefore, when the rotational speed limit of the motor 5 is high, it is preferable to arrange a speed reducer 12 in the transmission system, so that mechanical damage can be reduced and the driving force applied to the diaphragm 3 can be raised.

It should be noted that the motor speed sensor 34 may directly detect the rotation speed of the motor 5, or may indirectly detect the rotation speed of the motor 5 by detecting the speed of other elements in transmission connection with the motor 5, such as directly detecting the rotation speed of the flywheel 24 or the speed reducer 12 or the crankshaft 13 described below to indirectly detect the rotation speed of the motor 5. Even the rotation speed of the motor 5 can be indirectly determined by detecting other physical quantities related to the rotation speed of the motor, and such a sensor can be regarded as a motor rotation speed sensor as long as the related physical quantities detected by the sensor have high correlation with the rotation speed of the motor 5. The detection of the rotation speed of the motor 5 by the motor rotation speed sensor 34 may be direct or indirect, and the present application is not limited thereto.

The present embodiment arranges the power fluid storage chamber 10 above the power chamber 2 so that when the valve 11 is in the open state, the power fluid b (hydraulic oil) in the power fluid storage chamber 10 automatically flows into the power chamber 2 with the increased volume (when the piston is retracted) under its own weight, so that the transmission of the power fluid b between the power fluid storage chamber 10 and the power chamber 2 is more smooth.

The power fluid storage chamber 10 is formed in a square oil tank.

The above-mentioned transmission system for connecting the piston 4 and the motor 5 adopts a crankshaft connecting rod structure, as follows:

referring to fig. 1, 3 and 4, the transmission system includes the flywheel 24, the reducer 12, the crankshaft 13, the first connecting rod 14, the second connecting rod 15 and the push-pull rod 16, which are arranged in this order along the transmission direction. Wherein, the input shaft of the speed reducer 12 is connected with the output shaft of the motor 5 through a coupling 25, and the output shaft of the speed reducer 12 is connected with one end of the crankshaft 13 through the coupling 25. The other end of the crankshaft 13 is pivotally supported on the housing 33 of the diaphragm pump. The first connecting rod 14 has one end pivotally connected to the curved portion of the crankshaft 13 and the other end pivotally connected to one end of the second connecting rod 15 via a pivot 22. The other end of the second link 15 is pivotally connected to the push-pull rod 16 by a second pivot 22. The other end of the push-pull rod 16 is fixedly connected to the piston 4, although it is also possible to pivotally connect the other end of the push-pull rod 16 to the piston 4.

The crankshaft 13, the first connecting rod 14, the second connecting rod 15, and the push-pull rod 16 are accommodated in a transmission chamber 17 formed in the housing 33. The push-pull rod 16 is a linear rod extending left and right, i.e., linearly along the direction of movement of the piston 4.

Referring again to fig. 1, in order to ensure that, during operation, the pivot 22 pivotally connecting the second connecting rod 15 and the push-pull rod 16 can only move horizontally in the front-rear direction perpendicular to the paper in fig. 1, and thus better convert the rotational movement of the crankshaft 13 into the left-right movement of the push-pull rod 16, a guide-moving seat 23 is fixedly disposed in the transmission chamber 17, a guide-moving groove 23a extending in the front-rear direction (perpendicular to the moving direction of the piston) perpendicular to the paper in fig. 1 is formed in the guide-moving seat 23, and the pivot 22 pivotally connecting the second connecting rod 15 and the push-pull rod 16 is slidably disposed in the guide-moving groove 23 a.

In this embodiment, the guide seat 23 is integrally connected to the housing 33 of the diaphragm pump, that is, the guide seat 23 is integrally formed in the housing 33, as shown in fig. 1 and 4. Of course, the guide holder 23 may be a separate member separately connected to the housing 33, as shown in fig. 5.

In operation, the motor 5 drives the crankshaft 13 to pivot about the pivot axis O via the reducer 12. The crankshaft 13 rotates (revolves) one end of the first connecting rod 14 about a pivot axis O of the crankshaft. The other end of the first link 14 drives one end of the second link 15 to reciprocate along the guide groove 23 a. The other end of the second link 15 drives the push-pull rod 16 to reciprocate in the left-right direction in fig. 1.

Obviously, the above structural design is also applicable to a diaphragm compressor for compressing a working fluid.

In many application scenarios, during the process of moving the piston 4 of the diaphragm pump or the diaphragm compressor towards the diaphragm 3, the volume of the working chamber 1 becomes smaller and smaller, and when the working fluid a in the working chamber is not discharged or is not in time to be discharged in the process, the internal pressure of the working chamber becomes larger and larger (especially when the gaseous fluid in the working chamber is subjected to a compression treatment). Therefore, the piston 4 is subjected to a larger and larger reaction force in a direction away from the diaphragm 3 by the motive fluid b, which requires that the push-pull rod 16 must be capable of providing a larger and larger driving force to the piston 4 to ensure the normal operation of the diaphragm pump or the diaphragm compressor, which puts a higher demand on the output power of the motor 5. Ingeniously, even if the output power, especially the output torque, of the motor 5 is not changed in the process, the driving force exerted by the push-pull rod 16 on the piston 4 can be increased during the rightward movement of the piston 4, and the driving force is perfectly adapted to the application scenario, which is specifically analyzed as follows:

as shown in fig. 6 and with reference to fig. 4 and 5, an acute angle between the second connecting rod 15 and the push-pull rod 16 is defined as α, an angle between the curved portion of the crankshaft 13 and the horizontal plane is defined as β, and β =0 in fig. 5. When the crankshaft 13 rotates clockwise around the pivot axis O of the crankshaft 13 in fig. 6, the curved portion of the crankshaft 13 drives the left end portion of the second connecting rod 15 to move downward through the first connecting rod 14, so as to push the push-pull rod 16 to move rightward, and in the process, the included angle β gradually increases, and the included angle α gradually decreases. When the reduction ratio of the reducer 12 is fixed, the transmission ratio from the motor 5 to the crankshaft 13 is a constant value, so that each time the motor 5 rotates by one angle, β changes by a corresponding angle value in proportion, and at any equal short time, Δ β (i.e., the change value of β) is the same. By simple geometric analysis it is possible to estimate: in the process of turning the curved portion of the crankshaft 13 from the state shown in fig. 5 to the downward vertical state. On the one hand, the included angle β increases from zero to 90 ° (Π/2) at a uniform rate, and correspondingly, in a first phase, the downward movement speed of the lower end of the first connecting rod 14 (or the left end of the second connecting rod 15) increases gradually at first until reaching a maximum downward movement speed of the lower end of the first connecting rod 14 when the first connecting rod 14 is substantially perpendicular to the curved portion of the crankshaft (i.e., the portion indicated by reference numeral 13 in fig. 6); then, in the second stage, the downward moving speed of the lower end of the first connecting rod 14 is smaller and smaller, and when the first connecting rod 14 is aligned with the crank portion in fig. 6, the instantaneous downward moving speed of the lower end of the first connecting rod 14 is reduced to zero, and the piston 4 moves to the right limit position; then, in the third stage, the lower end of the first connecting rod 14 moves upwards, and the piston 4 is driven to retract leftwards. It can be seen that the downward movement speed of the lower end of the first connecting rod 14 is smaller and smaller in the latter half period before the piston 4 moves rightward to the limit position, i.e., in the aforementioned second stage. On the other hand, in the first and second stages, the included angle α is always gradually decreased, and accordingly, even if the lower end of the first connecting rod 14 and the left end of the second connecting rod 15 move downward at a constant speed, the rightward movement speed of the push-pull rod 16 is necessarily gradually decreased as the angle α becomes smaller, and even in the second stage, the downward movement speed of the left end of the second connecting rod 15 is gradually decreased, so that in the second stage, the rightward movement speed of the piston 4 is decreased, and the second stage is exactly the latter half of the rightward movement of the piston 4.

In order to make the reader more intuitively understand the above inference, referring to fig. 6 again, in fig. 6, points O, a, B, C, D, E respectively indicate the pivot axis of the crankshaft 13, the transition point of the first connecting rod 14 and the crank curve, the transition point of the first connecting rod 14 and the second connecting rod 15, the transition point of the second connecting rod 15 and the push-pull rod 16, a position point on the guide groove 23a which is flush with the transition point of the second connecting rod and the push-pull rod in the piston moving direction, and a position point on the guide groove 23a which is flush with the pivot axis of the crankshaft in the piston moving direction. OA is the known radial dimension of the curve of the crankshaft 13, i.e. the distance of the first connecting rod 14 from the transition point of the crankshaft 13 to the crankshaft pivot axis O. AB is the known length of the first link 14. BC is the known length of the second link 15. DE length is known and EO length is known.

An angle between the curved portion of the crankshaft 3 and the horizontal plane is set to be β.

The length of the CD can be known through geometric operation as follows:

by taking the derivative of equation (1), it can be seen that the rate of change of the CD length when β is in the range of 0 to Π/2 is:

assuming AO =2,ej0 =2,ab =8,bc =8,de =10, it can be derived from the above equation (2) that the rate of change of the CD length, i.e. the velocity of the piston 4, is plotted against the angle β in fig. 8, from which fig. 8 it can be readily seen that: when the beta is gradually increased in the range of 0 to pi/2, the CD is lengthened more and more slowly, namely the transmission ratio from the motor 5 to the piston 4 is smaller and smaller (the reduction ratio is larger and larger), the piston 4 is moved to the right more and more slowly, and under the condition that the output power of the motor 5 is constant, the driving force applied to the piston 4 is larger and larger, which proves the inference. More ingeniously, it can be seen from fig. 8 that the very low operating speed is maintained for a longer period of time before the piston 4 reaches the right limit position. This is perfectly adapted to many conditions in practical applications of membrane pumps or membrane compressors, especially membrane compressors. For example, the diaphragm compressor of this structure is applied to an air conditioning system to compress a gaseous refrigerant into a high pressure state or even a liquid state, and then discharged from the discharge valve 9. Obviously, during the refrigerant discharge process, the diaphragm 3 only needs to provide a relatively stable pushing force to push out the refrigerant in the working chamber 1, the driving force applied by the push-pull rod 16 to the piston 4 does not need to be greatly increased, and the working condition is perfectly matched with the curve of fig. 8, namely the reduction ratio of the tail section is not sharply reduced, but is relatively gradually reduced, and the piston is basically maintained at a reasonable and relatively gradually speed. Thus, the refrigerant compressed in the working chamber can be discharged quickly without reducing the driving force of the piston, and the work efficiency is improved.

In addition, a relation graph of the speed of the lower end (namely, the point B) of the first connecting rod 14 and the included angle β is obtained through geometric calculation as shown in fig. 7, and it is easy to see that the running speed of the lower end of the first connecting rod 14 is increased, then reduced, and then reversely moved upwards, which also proves the estimation.

To make better use of the above characteristics, in fig. 6, it is preferable to ensure that the left end (point B) of the second connecting rod 15 always moves back and forth above or flush with the transition of the second connecting rod to the push-pull rod (point C) when the crankshaft rotates 360 °, i.e., point B always moves on the same side of the straight line CD (including the point B overlapping the straight line CD). The line CD is a straight line parallel to the direction of movement of the piston 4 and passing through point C. In other words, point B always moves on the same side (upper side in fig. 9) of the line that passes point C and is parallel to the direction of motion of the piston 4.

Obviously, if the sum of the radial dimension of the curved portion of the crankshaft 13 (the length A0 in fig. 6, i.e., the distance between the first connecting rod and the crankshaft adapter and the pivot axis) and the length dimension of the first connecting rod 14 is not greater than the length ED, the above function is necessarily achieved.

It can be seen that the more the transmission system is at the rear stage of the action (moving to the right in fig. 1) of the piston 4, the larger the reduction ratio is, the more the rear stage of the action of the piston 4, the larger the rightward driving force is, and the driving force applied to the piston 4 can be kept at a (relatively stable) larger value for a longer time before the piston reaches the action limit position, which is perfectly adapted to many working conditions of the diaphragm pump and the diaphragm compressor in practical application.

Further, the present embodiment arranges the guiding groove 23a and the pivot axis O in the same plane and perpendicular to each other, i.e. the distance between the point E and the point O in fig. 6 is zero. Thus, when the transition point between the first connecting rod 14 and the crankshaft 13 is rotated to the lowest point in fig. 9, the first connecting rod 14 is just in line with the curved portion of the crankshaft 13. Further, it is also possible to arrange the sum of the radial dimension of the crank curve and the length of the first connecting rod 14 in fig. 9 to be equal to the vertical spacing of the pivot axis from the point of transition of the second connecting rod and the push-pull rod. Thus, when the curved portion of the crankshaft 13 rotates in the direction of the second connecting rod 15 to and on the same line as the first connecting rod 14 (vertical line in fig. 9), the first connecting rod 14 is just perpendicular to the second connecting rod 15, and the second connecting rod 15 is just parallel to the moving direction of the piston 4. This contributes to an increase in the compactness of the transmission system.

In order to improve the adaptability of the diaphragm 3 to deform leftwards and rightwards and further improve the service life of the diaphragm 3, the diaphragm 3 of the present embodiment is integrally provided with annular deformation wrinkles 3a protruding rightwards in the thickness direction of the diaphragm.

The main purpose of the operation of the motor 5 is to provide a driving force to the diaphragm 3 to drive the movement of the diaphragm 3 to squeeze and draw the working fluid. The piston 4 and the transmission system connecting the motor and the piston, including the flywheel 24, are all arranged in a drive path from the motor 5 to the diaphragm 3, and the piston 4 and the transmission system connecting the motor and the piston are all part of the drive path from the motor 5 to the diaphragm 3. The crankshaft 13 is located on the transmission downstream side of the speed reducer 12, the first connecting rod 14 is located on the transmission downstream side of the crankshaft 13, the second connecting rod 15 is located on the transmission downstream side of the first connecting rod 14, and the piston 4 is located on the transmission downstream side of the transmission system.

The motive fluid b filled in the motive force chamber 2 is also provided in a driving path for transmitting a driving force from the motor 5 to the diaphragm 3, and has a function of transmitting the driving force to the diaphragm 3, so that the motive fluid b filled in the motive force chamber 2 is also a component of the driving path for the motor 5 (or the flywheel 24, or the piston 4) to the diaphragm 3.

Further, the deformation folds 3a are of a circular ring structure to adapt to the leftward and rightward deformation characteristics of the diaphragm 3. The diaphragm 3 is composed of a first portion housed inside the working chamber 1 and the power chamber 2 and a second portion located outside the working chamber 1 and the power chamber 2, and the deformed wrinkles 3a are formed specifically on the first portion.

The deformation fold 3a is arranged close to the outer edge of the first part of the diaphragm, so that the enclosed area of the deformation fold 3a is as large as possible, and the purpose of the arrangement is to promote the leftward and rightward deformation of the diaphragm 3, and further promote the extrusion amount of the working fluid.

The enclosed area of the deformed pleats 3a is preferably not less than 80% of the area of the first portion of the membrane sheet.

The second embodiment:

fig. 14 and 15 show a second diaphragm pump, which is basically the same in structure as the first embodiment, with the main differences as follows:

the embodiment further optimizes the structure of the transmission system. As shown in fig. 14 and 15, the transmission system includes a flywheel (not shown), a speed reducer (not shown), a crankshaft 13, two connecting rods (a first connecting rod 14 and a second connecting rod 15, respectively), four parallel connecting rods, and a push-pull rod 16, which are arranged in sequence along a transmission direction (or power transmission direction). Wherein: the input shaft of the speed reducer is connected with the output shaft of the motor through a coupling, and the output shaft of the speed reducer is connected with one end of the crankshaft 13 through the coupling. The other end of the crankshaft 13 is pivotally supported on the housing 33 of the membrane pump. The parallel four-bar linkage is composed of a third connecting bar 18, a fourth connecting bar 19, a fifth connecting bar 20 and a sixth connecting bar 21 which are sequentially connected end to end in a pivoting manner along the circumferential direction. The junction (i.e. the pivotal connection) between the third link 18 and the fourth link 19, the junction between the fourth link 19 and the fifth link 20, the junction between the fifth link 20 and the sixth link 21, and the junction between the sixth link 21 and the third link 18 respectively form four vertex angles of the parallel four links. The first connecting rod 14 has one end pivotally connected to the curved portion of the crankshaft 13 and the other end connected to an adapter portion of the third connecting rod 18 and the fourth connecting rod 19. One end of the second connecting rod 15 is pivotally connected to the other curved portion of the crankshaft 13, and the other end is connected to the junction portion of the fifth connecting rod 20 and the sixth connecting rod 21. One end of the push-pull rod 16 is connected to the junction of the fourth link 19 and the fifth link 20, and the other end is connected to the piston 4.

When the electric motor works, the motor 5 drives the crankshaft 13 to rotate through the speed reducer. The crankshaft 13 rotates (revolves) one ends of the first and second connecting

rods

14 and 15 about a pivot axis of the crankshaft. The other ends of the first link 14 and the second link 15 bring the upper and lower vertex angles of the four parallel links to and from periodically in fig. 14, and the horizontal dimension of the four parallel links in fig. 14 is extended and shortened periodically, thereby bringing the piston 4 to reciprocate in the left-right direction in fig. 14 by the push-pull rod 16.

Referring to fig. 16 again, specifically, the third link 18 and the fourth link 19, the fourth link 19 and the fifth link 20, the fifth link 20 and the sixth link 21, and the sixth link 21 and the third link 18 are pivotally connected by corresponding pivot shafts 22. The aforementioned "other end" of the first link 14 is connected to the pivot 22 that pivotally connects the third link 18 and the fourth link 19, the aforementioned "other end" of the second link 15 is connected to the pivot 22 that pivotally connects the fifth link 20 and the sixth link 21, and one end of the push-pull rod 16 is connected to the pivot 22 that pivotally connects the fourth link 19 and the fifth link 20.

It will be understood that, during operation, the vertical component of the pushing or pulling force of the push-pull rod 16 exerted by the fourth link 19 is always opposite to the vertical component of the pushing or pulling force of the push-pull rod 16 exerted by the fifth link 20. The total vertical force exerted by the parallel four-bar linkage on the push-pull rod 16 is smaller or even zero, so that the radial external force exerted by the push-pull rod 16 on the piston 4 is reduced, the service life of the piston 4 and a piston cylinder sleeve (in the embodiment, the piston cylinder sleeve is a main component for forming a power chamber) which is not shown in fig. 14 and 15 but not marked is prolonged, and the possibility or severity of oil leakage at the joint of the piston 4 and the power chamber 2 is reduced.

In order to ensure that the vertical component of the pushing force or the pulling force of the fourth connecting rod 19 on the push-pull rod 16 and the vertical component of the pushing force or the pulling force of the fifth connecting rod 20 on the push-pull rod 16 are completely offset to zero all the time in the working process, so that the driving force applied to the piston 4 is always parallel to the inner wall surface of the power chamber, the lengths of the third connecting rod 18, the fourth connecting rod 19, the fifth connecting rod 20 and the sixth connecting rod 21 are set to be equal, the parallel four connecting rods are in a diamond structure, and one diagonal of each diamond parallel four connecting rod is parallel to the movement direction of the piston 4.

Further, the first link 14 and the second link 15 have the same length, so that the parallelogram linkage structure operates more smoothly.

It should be understood that the structural combination formed by the crankshaft 13, the first connecting rod 14, the fourth connecting rod 19 and the push-pull rod 16 in the transmission system of the present embodiment is substantially the same as that in the first embodiment shown in fig. 6 or fig. 9, and the motion trajectory during operation is also substantially the same, so that the transmission system of the present embodiment also has the same transmission characteristics as the transmission system of the first embodiment: the more the piston 4 moves to the right to do work, the larger the reduction ratio of the motor 5 to the piston 4 is, the larger the driving force applied to the piston 4 is.

In addition, the linear bearing 28 is sleeved outside the push-pull rod 16, the linear bearing 28 is fixed with the shell 33 of the diaphragm pump, and the linear bearing 28 supports and guides the reciprocating motion of the push-pull rod 16, so that the service life of the piston 4 is further prolonged.

To better convert the rotational movement of the crankshaft 13 into a left-right translation of the push-pull rod 16, the present embodiment fixedly (or pivotally) connects the pivot 22 that pivotally connects the third link 18 and the sixth link 21 to the housing 33 of the diaphragm pump. When the crankshaft 13 drives the parallel four-bar linkage to open and close through the first connecting bar 14 and the second connecting bar 15, the relative position of the pivot 22 pivotally connecting the third connecting bar 18 and the sixth connecting bar 21 with the housing 33 is always unchanged, so that the pivot 22 pivotally connecting the fourth connecting bar 19 and the fifth connecting bar 20 translates to the left or the right, and further drives the piston 4 to translate to the left or the right, as shown in fig. 14 and 15.

Example three:

the diaphragm pump of the present embodiment is different from the second embodiment only in the structure of the transmission system, which is specifically as follows:

as shown in fig. 17 and 18, the drive system of the diaphragm pump of the present embodiment includes: a flywheel and a reduction gear, not shown in the figure, a crankshaft 13, a first connecting rod 14, a second connecting rod 15, a third connecting rod 18, a fourth connecting rod 19 and a push-pull rod 16. The input shaft of the speed reducer is connected to the output shaft of a motor, not shown, via a coupling, and the output shaft of the speed reducer is connected to one end of the crankshaft 13 via a coupling. The other end of the crankshaft 13 is pivotally supported on the housing 33 of the diaphragm pump. One end, i.e., an upper end in fig. 18, of the first connecting rod 14 is pivotally connected to the curved portion of the crankshaft 13, and the other end, i.e., a lower end in fig. 18, is pivotally connected to one end, i.e., a left end in fig. 18, of the third connecting rod 18 by a pivot 22. One end, i.e., an upper end in fig. 18, of the second connecting rod 15 is pivotally connected to the other curved portion of the crankshaft 13, and the other end, i.e., a lower end in fig. 18, is pivotally connected to one end, i.e., a left end in fig. 16, of the fourth connecting rod 19 by a pivot 22. The other end of the third link 18, i.e., the right end in fig. 16, is pivotally connected to the other end of the fourth link 19, i.e., the right end in fig. 16, by a pivot 22. The push-pull rod 16 is connected at one end to the pivot 22 that pivotally connects the third 18 and fourth 19 links and at the other end to the piston 4. In order to convert the rotational movement of the crankshaft 13 into a lateral translation of the push-pull rod 16, a guide shoe 23 is also provided, which is fixed (to the housing 33) in the transmission chamber. The guide and shift base 23 is formed with a guide and shift groove 23a extending vertically as shown in fig. 18. The pivot 22 pivotally connecting the third link 18 and the first link 14 and the pivot 22 pivotally connecting the fourth link 19 and the second link 15 are slidably disposed in the aforementioned guide groove 23a such that the two pivots 22 can only move up and down (toward or away from each other) along the guide groove 23 a.

When the electric motor works, the crankshaft 13 is driven to rotate by the motor through the speed reducer. The crankshaft 13 rotates the upper ends of the first and second connecting

rods

14 and 15 about the pivot axis of the crankshaft. The lower end of the first connecting rod 14 and the lower end of the second connecting rod 15 respectively drive the left end of the third connecting rod 18 and the left end of the fourth connecting rod 19 to move up and down, so that the left end of the third connecting rod 18 and the left end of the fourth connecting rod 19 are vertically close to or far away from each other, and the push-pull rod 16 and the piston 4 move left and right.

It will be understood that, during operation, the vertical component of the pushing or pulling force of the push-pull rod 16 by the third connecting rod 18 and the vertical component of the pushing or pulling force of the push-pull rod 16 by the fourth connecting rod 19 are always in opposite directions, and the total vertical force applied to the push-pull rod 16 is relatively small or even zero, so as to reduce the radial acting force applied to the piston 4 by the push-pull rod 16, further improve the service life of the piston 4 and the piston cylinder sleeve (in the embodiment, the piston cylinder sleeve is a main component for forming the power chamber) shown in fig. 17 but not labeled, and reduce the problem of oil leakage at the joint of the piston 4 and the power chamber 2.

In order to ensure that the vertical component of the pushing or pulling force of the third connecting rod 18 on the push-pull rod 16 and the vertical component of the pushing or pulling force of the fourth connecting rod 19 on the push-pull rod 16 are completely offset to zero all the time during the operation, so that the driving force applied to the piston 4 is always parallel to the inner wall surface of the power chamber 2, the lengths of the third connecting rod 18 and the fourth connecting rod 19 are set to be equal in the present embodiment.

Further, the first link 14 and the second link 15 also have the same length, so that the link transmission structure operates more smoothly.

It is understood that the structural combination formed by the crankshaft 13, the first connecting rod 14, the third connecting rod 18 and the push-pull rod 16 in the transmission system of the present embodiment is basically the same as that of the structural combination in fig. 6 or 9 of the first embodiment, and the motion track during operation is also basically the same. Therefore, the transmission system in the first embodiment has the same transmission characteristics as the transmission system in the second embodiment: the more the piston 4 moves to the right to do work, the larger the reduction ratio from the motor 5 to the piston 4 is, the larger the driving force applied to the piston 4 becomes.

In addition, the linear bearing 28 is fixed in the housing 33 and sleeved outside the push-pull rod 16, and the linear bearing 28 supports and guides the reciprocating motion of the push-pull rod 16, so as to further prolong the service life of the piston 4.

It is obvious that the transmission system of the present embodiment is equivalent to the second embodiment in which the third link and the sixth link are removed, and the guiding and moving seat 23 for limiting the lower end portions of the first link and the second link to move only vertically is provided.

Example four:

fig. 19 and 20 show a fourth diaphragm pump that adds a pump head to the first embodiment to provide work on both portions of the working fluid. The method comprises the following specific steps:

the membrane pump is provided with a total of two working chambers 1, two power chambers 2, two membrane discs 3 and two pistons 4. The motor 5 drives the two pistons 4 to reciprocate in the left-right direction in fig. 19 through a set of transmission system, thereby driving the left and right diaphragm sheets 3 to work on the working fluid a of the left and right working chambers 1, respectively.

As shown in fig. 21 and with reference to fig. 20, the structure of the driving system in the diaphragm pump according to the present embodiment is similar to that of the first embodiment, except that two second connecting rods 15 and two push-pull rods 16 are provided. The two push-pull rods 16 are respectively connected with the two pistons 4 on the left side and the right side. One ends of the two second links 15 are pivotally connected to the lower end of the first link 14 via a pivot 22, and the other ends of the two second links 15 are pivotally connected to the two push-pull rods 16 on the left and right sides, respectively, via another pivot.

When the motor 5 drives the crankshaft 13 to rotate, the crankshaft 13 drives the first connecting rod 14 to move, and no matter where the lower end of the first connecting rod 14 moves, the crankshaft necessarily drives the at least one push-pull rod 16 to move left and right, and further drives the at least one piston 4 to move. However, in order to ensure that, during operation, the pivot 22 pivotally connecting the first link 14 and the two second links 15 can only move horizontally in the front-rear direction perpendicular to the paper in fig. 20, thereby enabling both the pistons 4 to move left and right, a guide-shift seat 23 is provided fixedly (fixed to the housing of the diaphragm pump) in the transmission chamber 17, a guide-shift groove 23a extending in the front-rear direction perpendicular to the paper in fig. 20 is formed in the guide-shift seat 23, and the pivot 22 pivotally connecting the second link 15 and the push-pull rod 16 is slidably disposed in the guide-shift groove 23 a.

Further, in the present embodiment, the two second connecting rods 15 have the same length, so that the two push-pull rods 16 move away from or close to each other synchronously along the left-right direction when the crankshaft 13 rotates, and thus the left and right pump heads operate synchronously.

In operation, the motor 5 drives the crankshaft 13 to rotate through the reducer 12. The crankshaft 13 rotates (revolves) the upper end of the first connecting rod 14 about the pivot axis of the crankshaft. The lower end of the first link 14 simultaneously drives one ends of the two second links 15 to reciprocate along the guide groove 23a, so that the other ends of the second links 15 drive the push-pull rod 16 to reciprocate in the left-right direction in fig. 20.

In this embodiment, the transfer guide base 23 is an independent member separately connected to the housing of the diaphragm pump. Of course, the displacement guide seat 23 and the housing may be made as a single structure as in the first embodiment.

It is understood that the structural combination formed by the crankshaft 13, the first connecting rod 14, the second connecting rod 15 and the push-pull rod 16 in the transmission system of the present embodiment has substantially the same structure and motion locus as those of the structural combination in fig. 6 or fig. 9 of the first embodiment, so that the transmission system of the present embodiment also has the same transmission characteristics as the transmission system of the first embodiment: the more the piston 4 moves to the right to do work, the larger the reduction ratio of the motor 5 to the piston 4 is, the larger the driving force applied to the piston 4 is.

Example five:

fig. 22 shows a fifth diaphragm pump which, like the fourth embodiment, also has two pump heads, so that work can be done on both parts of the working fluid at the same time. The difference between the present embodiment and the fourth embodiment lies in the structure of the transmission system, which is specifically as follows:

as shown in fig. 22 and 23, the transmission system for connecting the motor and the piston in the present embodiment includes, arranged in order along the transmission direction: a flywheel, a reducer, a crankshaft 13, two connecting rods (a first connecting rod 14 and a second connecting rod 15, respectively), four parallel connecting rods, two push-pull rods 16, which are not shown in the figure. Wherein: the input shaft of the speed reducer is connected with the output shaft of the motor through a coupling, and the output shaft of the speed reducer is connected with one end of the crankshaft 13 through the coupling. The other end of the crankshaft 13 is pivotally supported on the housing 33 of the membrane pump. The parallel four-bar linkage is composed of a third connecting bar 18, a fourth connecting bar 19, a fifth connecting bar 20 and a sixth connecting bar 21 which are sequentially connected end to end in a pivoting manner along the circumferential direction. The first connecting rod 14 has one end pivotally connected to one curved portion of the crankshaft 13 and the other end connected to an intermediate portion of the third connecting rod 18 and the fourth connecting rod 19. One end of the second connecting rod 15 is pivotally connected to the other curved portion of the crankshaft 13, and the other end is connected to an adapter portion of the fifth connecting rod 20 and the sixth connecting rod 21. One end of the right push-pull rod 16 is connected to the junction of the fourth connecting rod 19 and the fifth connecting rod 20, and the other end is connected to the right piston 4. One end of the left push-pull rod 16 is connected to the junction of the third connecting rod 18 and the sixth connecting rod 21, and the other end is connected to the left piston 4.

Specifically, as shown in fig. 23 and with reference to fig. 22, the third link 18 and the fourth link 19, the fourth link 19 and the fifth link 20, the fifth link 20 and the sixth link 21, and the sixth link 21 and the third link 18 are respectively pivotally connected by corresponding pivot shafts 22. The aforementioned "other end" of the first link 14 is connected specifically to the pivot 22 that pivotally connects the third link 18 and the fourth link 19. The aforementioned "other end" of the second link 15 is connected to the pivot 22 that pivotally connects the fifth link 20 and the sixth link 21. One end of the right push-pull rod 16 is connected to a pivot 22 that pivotally connects the fourth link 19 and the fifth link 20. One end of the left push-pull rod 16 is connected to a pivot 22 that pivotally connects the third link 18 and the sixth link 21.

When the motor 5 drives the crankshaft 13 to rotate, the crankshaft 13 drives the first connecting rod 14 and the second connecting rod 15 to move. No matter where the lower ends of the first and second connecting

rods

14 and 15 move, the parallel four-bar linkage is inevitably deformed, and the at least one push-pull rod 16 is driven to move left and right, so that the at least one piston 4 moves left and right.

However, in order to ensure that both pistons 4 are able to operate during operation, the present embodiment provides a displacement guide 23 in the transmission chamber 17, which is directly or indirectly fixed to the diaphragm pump housing 33. The guide holder 23 is formed with a guide groove 23a extending up and down in parallel with the paper surface in fig. 23, and the pivot shaft 22 pivotally connecting the third link 18 and the fourth link 19 and the pivot shaft 22 pivotally connecting the fifth link 20 and the sixth link 21 are slidably disposed in the guide groove 23 a. This allows the two pivot shafts 22 to move only up and down (toward and away from each other) along the guide grooves 23a, thereby ensuring that the crankshaft 13 rotating during operation simultaneously moves the pistons 4 on both sides to the left and right.

When the electric motor works, the motor 5 drives the crankshaft 13 to rotate through the speed reducer. The crankshaft 13 rotates one end of the first connecting rod 14 and the second connecting rod 15 about a pivot axis of the crankshaft. The other ends of the first link 14 and the second link 15 bring the upper and lower vertex angles of the parallelogram links close and far away periodically in fig. 22. The parallel four-bar linkage is periodically extended and shortened in the horizontal dimension in fig. 22, and the left and right pistons 4 are driven to reciprocate in the left and right directions in fig. 22 by the left and right push-pull rods 16, respectively.

It is understood that, during operation, the direction of the vertical component of the pushing force or pulling force of the fourth connecting rod 19 on the left push-pull rod 16 is always opposite to the direction of the vertical component of the pushing force or pulling force of the fifth connecting rod 20 on the right push-pull rod 16, the direction of the vertical component of the pushing force or pulling force of the third connecting rod 18 on the right push-pull rod 16 is always opposite to the direction of the vertical component of the pushing force or pulling force of the sixth connecting rod 21 on the right push-pull rod 16, and the vertical forces exerted on the two push-pull rods 16 are both small and even zero, so that the radial acting force exerted on the piston 4 by the push-pull rod 16 is reduced, the service lives of the piston 4 and the piston cylinder liners (in the embodiment, the piston cylinder liners are main components for forming the power chamber) shown in fig. 22 but not labeled are prolonged, and the problem of oil leakage at the joint of the piston 4 and the power chamber 2 is reduced.

Further, in order to ensure that the vertical component of the pushing force or the pulling force of the fourth connecting rod 19 on the right push-pull rod 16 and the vertical component of the pushing force or the pulling force of the fifth connecting rod 20 on the right push-pull rod 16 are completely offset to zero all the time during the operation, the vertical component of the pushing force or the pulling force of the third connecting rod 18 on the left push-pull rod 16 and the vertical component of the pushing force or the pulling force of the sixth connecting rod 21 on the left push-pull rod 16 are completely offset to zero all the time, and therefore the driving force applied to the two pistons 4 is always parallel to the inner wall surface of the power chamber 2, the lengths of the third connecting rod 18, the fourth connecting rod 19, the fifth connecting rod 20 and the sixth connecting rod 21 are set to be equal, so that the parallel four connecting rods are in a diamond structure.

Further, the first link 14 and the second link 15 also have the same length, so that the parallelogram linkage structure operates more smoothly.

Obviously, with the design of the diamond-shaped four-bar linkage, it is ensured that the two push-pull rods 16 are always symmetrically far away or symmetrically close during operation, so that the operation steps of the left pump head and the right pump head are consistent.

It will be understood that the structural combination formed by the crankshaft 13, the first connecting rod 14, the third connecting rod 18 and the push-pull rod 16, and the structural combination formed by the crankshaft 13, the first connecting rod 14, the fourth connecting rod 19 and the push-pull rod 16 in the transmission system of the present embodiment are substantially the same as the structural combination in fig. 6 or 9 of the first embodiment, and the motion trajectory during operation is also substantially the same. Therefore, the transmission system in the embodiment also has the same transmission characteristics as the transmission system in the first embodiment: in the rear stage of the left piston 4 moving leftwards to do work and the right piston 4 moving rightwards to do work, the larger the reduction ratio from the motor 5 to the two pistons 4 is, the larger the driving force received by the two pistons 4 is.

In addition, the linear bearing 28 fixed in the housing 33 and sleeved outside the push-pull rod 16 is also provided in the present embodiment, and the linear bearing 28 supports and guides the reciprocating motion of the push-pull rod 16, thereby further prolonging the service life of the piston 4.

Example six:

fig. 24 shows a sixth diaphragm pump, which is similar in structure to the first embodiment except that:

instead of providing a power fluid storage chamber in communication with the power chamber and a valve in the communication path, a clutch 37 is provided in the flywheel 24 to piston 4 transmission system, the clutch 37 being connected in series between the flywheel 24 and piston 4. Obviously, the clutch 37 is arranged in the drive path from the motor 5 to the diaphragm 3, and the clutch 37 also forms part of the drive path from the motor 5 to the diaphragm 3.

The clutch 37 is operatively disengaged and engaged. When the clutch 37 is in the disengaged state, the drive path from the flywheel 24 to the diaphragm 3 is disconnected; with the clutch 37 engaged, the drive path from the flywheel 24 to the diaphragm 3 is engaged. It can be seen that the clutch 37 has the same function as the power fluid storage chamber 10 and valve 11 of the first embodiment.

As shown in fig. 25, in order to enable the clutch 37 to be automatically engaged or disengaged according to the rotation speed of the motor 5, an electrically controlled clutch that can be electrically controlled to be engaged or disengaged is used as the clutch 37, and a motor rotation speed sensor 34 that detects the rotation speed of the motor 5 and a controller 35 that is connected to the motor rotation speed sensor 34 and the clutch 37 in communication are provided. The controller 35 is configured to acquire the rotation speed of the motor 5 from the motor rotation speed sensor 34, and control the engagement and disengagement of the clutch 37 based on the rotation speed, so as to implement the following control method substantially the same as the first embodiment:

the embodiment provides a control method of the diaphragm pump, which comprises the following steps:

s201, during operation of the electric machine 5, the clutch 37 is controlled to be alternately disengaged and engaged at a first frequency.

That is, during operation of the motor 5, the drive path of the flywheel 24 to the diaphragm 3 is controlled to be alternately disconnected and engaged at a first frequency.

Preferably, during operation of the electric motor 5, the drive path of the flywheel 24 to the diaphragm 3 is controlled to be alternately disengaged and engaged at a first frequency if it is determined that the rotational speed of the electric motor 5 is in a set first rotational speed interval.

In other embodiments, motor speed sensor 34 may not be provided, and controller 35 may be caused to control clutch 37 to alternately disengage and engage at a first frequency solely by user instructions applied to controller 35.

S202, in the process of controlling the clutch 37 to be alternately disengaged and engaged at the first frequency in the above S201, if it is detected that the rotation speed of the motor 5 is continuously reduced for the first period of time, controlling the clutch 37 to be alternately disengaged and engaged at the third frequency; wherein the ratio of the engaging duration to the disengaging duration of the clutch 37 in each cycle of the third frequency < the ratio of the engaging duration to the disengaging duration of the clutch 37 in each cycle of the first frequency.

That is, if it is determined that the rotation speed of the motor 5 continuously decreases for the first time period in the process of controlling the driving path of the flywheel 24 to the diaphragm 3 to be alternately opened and engaged at the first frequency, the driving path of the flywheel 24 to the diaphragm 3 is controlled to be alternately opened and engaged at the third frequency. Wherein the ratio of the duration of engagement to the duration of disengagement of the drive path in each cycle of the third frequency (the drive path of the flywheel 24 to the diaphragm 3) is < the ratio of the duration of engagement to the duration of disengagement of the drive path in each cycle of the first frequency.

S203, in the process of controlling the clutch 37 to be alternately disengaged and engaged at the third frequency in the above S202, if it is detected that the rotation speed of the motor 5 is continuously reduced for the second period, the clutch 37 is controlled to be alternately disengaged and engaged at the fourth frequency. Wherein the ratio of the engaging duration to the disengaging duration of the clutch 37 in each cycle of the fourth frequency < the ratio of the engaging duration to the disengaging duration of the clutch 37 in each cycle of the third frequency.

That is, if it is determined that the rotation speed of the motor 5 is continuously reduced for the second period of time in the process of controlling the driving path of the flywheel 24 toward the diaphragm 3 to be alternately disconnected and engaged at the third frequency, the driving path of the flywheel 24 toward the diaphragm 3 is controlled to be alternately disconnected and engaged at the fourth frequency. Wherein the ratio of the engagement duration to the disengagement duration of the drive path in each cycle of the fourth frequency < the ratio of the engagement duration to the disengagement duration of the drive path in each cycle of the third frequency.

S204, in the process of controlling the clutch 37 to be alternately disengaged and engaged at the third frequency in the above S202, if it is detected that the rotation speed of the electric motor 5 is continuously increased for the third period, controlling the clutch 37 to be alternately disengaged and engaged at the fifth frequency; wherein the ratio of the engaging duration to the disengaging duration of the clutch 37 in each cycle of the first frequency > the ratio of the engaging duration to the disengaging duration of the clutch 37 in each cycle of the fifth frequency > the ratio of the engaging duration to the disengaging duration of the clutch 37 in each cycle of the third frequency.

That is, in the process of controlling the driving path of the flywheel 24 toward the diaphragm 3 to be alternately disconnected and engaged at the third frequency, if it is determined that the rotation speed of the motor 5 is continuously increased for the third period of time, the driving path of the flywheel 24 toward the diaphragm 3 is controlled to be alternately disconnected and engaged at the fifth frequency; wherein the ratio of the engagement duration to the disengagement duration of the drive path in each cycle of the first frequency > the ratio of the engagement duration to the disengagement duration of the drive path in each cycle of the fifth frequency > the ratio of the engagement duration to the disengagement duration of the drive path in each cycle of the third frequency.

S205, in the process of controlling the clutch 37 to be alternately disengaged and engaged at the first frequency in S201, if it is detected that the rotation speed of the motor 5 is continuously increased for the fourth time period, controlling the clutch 37 to be alternately disengaged and engaged at the sixth frequency; wherein the ratio of the engaging duration to the disengaging duration of the clutch 37 in each cycle of the sixth frequency > the ratio of the engaging duration to the disengaging duration of the clutch 37 in each cycle of the first frequency.

That is, if it is determined that the rotation speed of the motor 5 continuously increases for the fourth time period in the process of controlling the driving path of the flywheel 24 toward the diaphragm 3 to be alternately disconnected and engaged at the first frequency, the driving path of the flywheel 24 toward the diaphragm 3 is controlled to be alternately disconnected and engaged at the sixth frequency; wherein a ratio of the engagement duration to the disengagement duration of the drive path in each cycle of the sixth frequency > a ratio of the engagement duration to the disengagement duration of the drive path in each cycle of the first frequency.

S206, in the process of controlling the clutch 37 to be alternately disengaged and engaged at the sixth frequency at S205 described above, if it is detected that the rotation speed of the motor 5 is continuously increased for the fifth period of time, the clutch 37 is controlled to be alternately disengaged and engaged at the seventh frequency. Wherein the ratio of the engaging duration to the disengaging duration of the clutch 37 in each cycle of the seventh frequency > the ratio of the engaging duration to the disengaging duration of the clutch 37 in each cycle of the sixth frequency.

That is, in the process of controlling the driving path of the flywheel 24 to the diaphragm 3 to be alternately disconnected and engaged at the sixth frequency, if it is determined that the rotation speed of the motor 5 continuously increases in the fifth period, the driving path of the flywheel 24 to the diaphragm 3 is controlled to be alternately disconnected and engaged at the seventh frequency; wherein a ratio of the engagement duration to the disengagement duration of the drive path in each cycle of the seventh frequency > a ratio of the engagement duration to the disengagement duration of the drive path in each cycle of the sixth frequency.

S207, in the process of controlling the clutch 37 to be alternately disengaged and engaged at the sixth frequency in S205 described above, if it is detected that the rotation speed of the electric motor 5 is continuously decreased in the sixth period, the clutch 37 is controlled to be alternately opened and closed at the eighth frequency. Wherein the ratio of the engaging duration to the disengaging duration of the clutch 37 in each cycle of the sixth frequency > the ratio of the closing duration to the opening duration of the valve in each cycle of the eighth frequency > the ratio of the engaging duration to the disengaging duration of the clutch 37 in each cycle of the first frequency.

That is, in the process of controlling the driving path of the flywheel 24 to the diaphragm 3 to be alternately disconnected and engaged at the sixth frequency, if it is determined that the rotation speed of the motor 5 continuously increases for the sixth period of time, the driving path of the flywheel 24 to the diaphragm 3 is controlled to be alternately disconnected and engaged at the eighth frequency; wherein a ratio of an engagement duration to a disconnection duration of the drive path in each cycle of the sixth frequency > a ratio of an engagement duration to a disconnection duration of the drive path in each cycle of the eighth frequency > a ratio of an engagement duration to a disconnection duration of the drive path in each cycle of the first frequency

S208, if the rotation speed of the motor 5 is detected to be less than the first rotation speed threshold value, controlling the clutch 37 to be continuously disengaged; wherein the first rotation speed threshold is smaller than the lower limit of the first rotation speed interval in S201.

That is, if it is determined that the rotation speed of the motor 5 is less than a relatively small first rotation speed threshold, the driving path of the flywheel 24 to the diaphragm 3 is controlled to be continuously disconnected; wherein the first speed threshold is smaller than the lower limit of the first speed interval. To avoid severe overload of the motor 5.

S209, if it is detected that the rotation speed of the electric machine 5 is greater than the second rotation speed threshold, controlling the clutch 37 to be continuously engaged; wherein the second rotation speed threshold is not less than the first rotation speed threshold in S208.

That is, in the process of controlling the continuous disconnection of the drive path of the flywheel 24 to the diaphragm 3, if it is determined that the rotation speed of the motor 5 is greater than the second rotation speed threshold value, the continuous engagement of the drive path of the flywheel 24 to the diaphragm 3 is controlled; and the second rotating speed threshold value is not less than the first rotating speed threshold value.

Preferably, the second rotation speed threshold is greater than the upper limit of the first rotation speed section in S201.

In other embodiments, the above strategies of S201 to S207 may be abandoned, and only the strategies of S208 and S209 may be used to control the diaphragm pump:

that is, if it is determined that the rotation speed of motor 5 is less than the first rotation speed threshold value, flywheel 24 is controlled to be continuously disconnected from the drive path to diaphragm 3. Controlling the flywheel 24 to continue engaging the drive path of the diaphragm 3 if it is determined that the speed of rotation of the motor 5 is greater than the second speed threshold; and the second rotating speed threshold value is not less than the first rotating speed threshold value. In such a control mode, the second rotational speed threshold may generally be equal to the first rotational speed threshold. The disadvantages are that: the rotation speed of the motor 5 may be unstable.

The controller 35 configured in the diaphragm pump of the present embodiment also includes a memory, a processor connected to the memory, and computer instructions stored in the memory and executable by the processor, wherein the computer instructions, when executed by the processor, implement the control method.

To ensure a long service life of the clutch 37, a flexible clutch may be used for the clutch 37. Also, it is preferable to connect the flexible clutch in series between the flywheel 24 and the reducer 12, not on the downstream side of the reducer 12, to reduce the stress of the flexible clutch.

Example seven:

fig. 26 shows a seventh kind of membrane pump, which is particularly suitable for this case: the fluid pressure at the inlet port 6 is much less than the fluid pressure at the outlet port 7, the extraction force to extract the working fluid from the inlet port 6 into the working chamber 1 is much less than the thrust force to push the working fluid out of the working chamber to the outlet port 7, and the power consumption to extract the working fluid is much less than the power consumption to push the working fluid. For example, a diaphragm pump is arranged at the water source, pushing water from a low location to a high location. This is similar to the operation of a diaphragm compressor and is therefore also particularly suitable for a diaphragm compressor.

The structure of the diaphragm pump is similar to that of the sixth embodiment, except that:

as shown in fig. 26, 27 and 28, the present embodiment does not have a clutch, but instead, an electric control valve 38 is additionally provided in parallel with the suction valve 8 between the inlet port 6 and the working chamber 1, and the electric control valve 38 is in communication with the controller 35, so that the controller 35 can control the operating state of the electric control valve 38.

It can be seen that in addition to the suction valve 8 which is originally present in a conventional diaphragm pump, an electrically controlled valve 38 is additionally provided in this embodiment between the working chamber 1 and the inlet opening 6.

The suction valve 8 in this embodiment is a mechanical check valve, and unlike the suction valve 8 which is automatically opened and closed by sensing pressure, the opening and closing of the electrically controlled valve 38 is controlled by an electric signal independent of pressure. In other embodiments, the suction valve 8 may also be an electrically controlled one-way valve. The differences between the mechanical check valve and the electrically controlled check valve are further described below.

If the electrically controlled valve 38 is in the closed state, the operation of the pump head of the diaphragm pump is the same as that of a conventional diaphragm pump, and at this time, as long as the diaphragm pump has enough energy, the working fluid in the inlet port 6 can be pumped into the working chamber 1 and then pushed into the outlet port 7. However, as described above, since the power consumption of the diaphragm pump for pushing the working fluid is large, the diaphragm pump cannot push the working fluid in the working chamber 1 to the discharge port 7 in a sufficient amount when the rotation speed of the motor 5 is low and the energy stored in the flywheel 24 is insufficient.

If the electrically controlled valve 38 is in the open state, when the piston 4 moves to the left in fig. 26, the working fluid in the inlet port 6 is easily pumped to the working chamber 1 through the open electrically controlled valve 38, and the power consumption of the action is small; when the piston moves to the right in fig. 26, the electric control valve 38 is in the open state, and the discharge valve 9 is kept in the closed state due to the large opening pressure, so that the working fluid in the working chamber 1 is discharged from the opened electric control valve 38 back to the inlet 6, and the working fluid in the working chamber is discharged from the inlet 6, and the power consumption of the action is small. Corresponding to (at least partially) disconnecting the working load of the diaphragm 3. Therefore, in the process, one part of the output power provided by the motor 5 is used for completing the extraction and back-exhaust actions, and the other part of the output power is used for applying work to the flywheel 24, so that the flywheel 24 is accelerated to store energy.

In particular, the "diaphragm off workload" described in the present specification and claims is not limited to zero adjustment of the diaphragm workload, but also includes a "diaphragm only partially off" workload, that is, a "diaphragm off workload" situation.

Thus, the present embodiment provides the following control method of the diaphragm pump:

s301, during operation of the motor 5, the electronically controlled valve 38 is controlled to alternately open and close at a first frequency.

That is, the electronic control valve 38 is alternately opened for a twenty-third period of time, closed for a twenty-fourth period of time, and (8230); during the operation of the motor 5 at the set first frequency. That is, during operation of the motor 5, the working load controlling the diaphragm 3 is alternately switched off and on at the first frequency. Also, the electronically controlled valve 38 has a continuous open duration and a continuous closed duration in each cycle of the first frequency, and the ratio of the open duration to the closed duration can be set as desired. It will be appreciated that the greater the ratio of the open duration to the closed duration of the electronically controlled valve 38, the greater the fraction of energy storage time of the flywheel 24 in each cycle; the smaller the ratio of the open duration to the closed duration of the electronically controlled valve 38, the smaller the energy storage time fraction of the flywheel 24 in each cycle.

For example, during operation of the motor, the electronically controlled valve 38 is alternately opened and closed at a frequency of 10 times per minute, and 2 seconds and 4 seconds of closure each time. Wherein 10 times/minute means that the valve is opened 10 times and the valve is closed 10 times every 1 minute, and the opening and closing are alternately performed. Specifically, opening the electric control valve for 2 seconds, closing the electric control valve for 4 seconds, 8230, and the like.

During operation of the electric motor 5, the electronically controlled valve 38 is controlled to open and close alternately according to a set first frequency, so as to cause the alternate disconnection and connection of the working load of the diaphragm 3. Thereby causing flywheel 24 and diaphragm 3 to perform work intermittently during each cycle of the first frequency. Motor 5 periodically charges flywheel 24 with energy. If the energy supplied by the motor 5 during continuous operation (e.g. 2 seconds as described above) is balanced with the energy consumed by the diaphragm 3 during normal work only for a part of the period (e.g. 4 seconds as described above) during each cycle, the diaphragm pump can continue to operate stably.

It is understood that when the electrically controlled valve 38 is closed, the working load of the diaphragm 3 is switched on, and the closing time of the electrically controlled valve 38 = the switching-on time of the diaphragm working load. When the electric control valve 38 is opened, the working load of the diaphragm 3 is turned off, and the opening period of the electric control valve 38 = the turning-off period of the diaphragm working load. For convenience of description, in the present embodiment, the on-period of the diaphragm work load is simply referred to as "on-period of the work load", and the off-period of the diaphragm work load is simply referred to as "off-period of the work load".

It is not appropriate to adopt the control strategy of S301 if the rotation speed of the motor 5 is low (e.g., just started). Therefore, the control strategy of S301 may be adopted only when the rotation speed of the motor 5 is in the set first rotation speed interval. That is, during operation of motor 5, if it is determined that the rotational speed of motor 5 is in the first rotational speed interval, the operational load of diaphragm 3 is controlled to be alternately switched off and on at a first frequency. It is understood that the first speed range is preferably a range around the rated speed of the motor 5. For example, if the nominal rotational speed of the electric machine 5 is 10000 rpm, the first rotational speed interval can be selected to be an interval of 9000-11000 rpm.

Of course, the switching frequency of the electronically controlled valve 38 can also be adjusted when the electric motor 5 is in different speed ranges. For example, if it is determined that the speed of the electric machine 5 is in a second speed interval, different from and not intersecting the first speed interval and smaller than the first speed interval, the electronically controlled valve 38 is controlled to open and close alternately at a second frequency, different from the first frequency. I.e. if it is determined that the rotational speed of the motor 5 is in the second rotational speed interval, the operational load of the diaphragm 3 is controlled to be alternately switched off and on at the second frequency.

In other embodiments, motor speed sensor 34 may not be provided, and the user commands applied to controller 35 by the user to control electronically controlled valve 38 to alternately disengage and engage at the first frequency.

S302, in the process of controlling the electronic control valve 38 to alternately open and close at the first frequency in S301, if it is detected that the rotation speed of the motor 5 continuously decreases for the first time period, controlling the electronic control valve 38 to alternately open and close at the third frequency; wherein the ratio of the closed duration to the open duration of the electronically controlled valve 38 in each cycle of the third frequency < the ratio of the closed duration to the open duration of the electronically controlled valve 38 in each cycle of the first frequency.

That is, if it is determined that the rotational speed of the motor 5 is continuously reduced for a first period of time, for example, one minute, during the control of the operation load of the diaphragm 3 to be alternately turned off and on at the first frequency, the operation load of the diaphragm 3 is controlled to be alternately turned off and on at the third frequency; and the ratio of the access duration to the disconnection duration of the working load in each period of the third frequency is less than the ratio of the access duration to the disconnection duration of the working load in each period of the first frequency.

The rotational speed of the motor 5 is continuously reduced during a set first period of time, for example, two minutes, which means that the energy supplied by the motor 5 is less than the power consumption of the diaphragm 3 during this first period of time. Therefore, it is necessary to reduce the duty ratio of the working time of the diaphragm 3 or increase the duty ratio of the dead time of the flywheel 24. Thus, the electronically controlled valve 38 is controlled to alternately open and close at a third frequency different from the first frequency when it is detected that the rotational speed of the electric motor 5 continuously decreases for a first period of time. And the ratio of the access duration to the disconnection duration of the working load in each period of the third frequency is less than the ratio of the access duration to the disconnection duration in each period of the first frequency.

Illustratively, the third frequency may be: opening the electric control valve for 4 seconds, closing the electric control valve for 2 seconds, 8230, and circularly opening and closing the electric control valve for 10 times every minute. Of course, the third frequency can be adjusted to cycle on and off 3, 6, or 20 times per minute, etc.

And S303, in the process of controlling the electronic control valve 38 to be alternately opened and closed at the third frequency in the above S302, if it is detected that the rotation speed of the motor 5 is continuously decreased within the second period, controlling the electronic control valve 38 to be alternately opened and closed at the fourth frequency. Wherein the ratio of the closing duration to the opening duration of the electronically controlled valve 38 in each cycle of the fourth frequency < the ratio of the closing duration to the opening duration of the electronically controlled valve 38 in each cycle of the third frequency.

That is, if it is determined that the rotational speed of the motor 5 is continuously reduced for the second period of time in controlling the operational load of the diaphragm 3 to be alternately switched off and on at the third frequency, the operational load of the diaphragm 3 is controlled to be alternately switched off and on at the fourth frequency. And the ratio of the access duration to the disconnection duration of the working load in each period of the fourth frequency is less than the ratio of the access duration to the disconnection duration of the working load in each period of the third frequency.

The rotational speed of the motor 5 is continuously reduced during a second period of time, which means that the energy supplied by the motor 5 is still less than the energy consumed by the diaphragm 3 to do work. Therefore, it is necessary to further reduce the duty ratio of the normal operation of the diaphragm 3, or to further increase the duty ratio of the dead time of the flywheel 24. Thus, when it is detected that the rotation speed of the motor 5 continuously decreases for the second period of time, the electronic control valve 38 is controlled to alternately open and close at the above-described fourth frequency.

Illustratively, at the fourth frequency: opening the electric control valve for 5 seconds, closing the electric control valve for 1 second, 8230, and still circulating for 10 times every minute.

And S304, in the process of controlling the electronic control valve 38 to be alternately opened and closed at the third frequency in the step S302, if the rotation speed of the motor 5 is detected to be continuously increased in the third period, controlling the electronic control valve 38 to be alternately opened and closed at the fifth frequency. Wherein, the ratio of the closing duration to the opening duration of the electronic control valve 38 in each period of the first frequency > the ratio of the closing duration to the opening duration of the electronic control valve 38 in each period of the fifth frequency > the ratio of the closing duration to the opening duration of the electronic control valve 38 in each period of the third frequency.

That is, in the process of controlling the operational load of the diaphragm 3 to alternately turn off and on the operational load of the diaphragm 3 at the third frequency, if it is determined that the rotational speed of the motor 5 is continuously increased for the third period of time, the operational load of the diaphragm 3 is controlled to alternately turn off and on the operational load of the diaphragm 3 at the fifth frequency; and the ratio of the access duration to the disconnection duration in each period of the first frequency is greater than the ratio of the access duration to the disconnection duration in each period of the fifth frequency is greater than the ratio of the access duration to the disconnection duration in each period of the third frequency.

The rotational speed of the motor 5 is continuously increased during a third period of time, which means that the energy supplied by the motor 5 is greater than the energy consumed by the diaphragm 3. Therefore, the normal duty ratio of the diaphragm 3 can be increased appropriately, or the dead time ratio of the flywheel 24 can be decreased appropriately. Thus, when it is detected that the rotation speed of the motor 5 is continuously increased for the third period, the electronic control valve 38 is controlled to be alternately opened and closed at the above-described fifth frequency.

Illustratively, at this fifth frequency: opening the electric control valve for 3.5 seconds, closing the electric control valve for 2.5 seconds, 8230, 8230and the like.

S305, in the process of controlling the electronic control valve 38 to be opened and closed alternately at the first frequency in the above S301, if it is detected that the rotation speed of the motor 5 is continuously increased for the fourth time period, controlling the electronic control valve 38 to be opened and closed alternately at the sixth frequency; wherein the ratio of the closing duration to the opening duration of the electronically controlled valve 38 in each cycle of the sixth frequency > the ratio of the closing duration to the opening duration of the electronically controlled valve 38 in each cycle of the first frequency.

That is, in the process of controlling the working load of diaphragm 3 to alternately turn off and on the working load of diaphragm 3 at the first frequency, if it is determined that the rotation speed of motor 5 continuously increases for the fourth time period, the working load of diaphragm 3 is controlled to alternately turn off and on the working load of diaphragm 3 at the sixth frequency; wherein, the ratio of the access duration to the disconnection duration of the working load in each period of the sixth frequency is greater than the ratio of the access duration to the disconnection duration of the working load in each period of the first frequency.

The rotational speed of the motor 5 is continuously reduced during a fourth time period, which means that the energy supplied by the motor 5 is greater than the energy consumed by the diaphragm 3 during this fourth time period. Therefore, the time ratio of the diaphragm 3 to normally apply work can be increased, or the idle energy storage time ratio of the flywheel 24 can be shortened. Thus, when it is detected that the rotation speed of the motor 5 is continuously reduced for the fourth period, the electronically controlled valve 38 is controlled to alternately open and close at the sixth frequency.

Illustratively, the sixth frequency may be: opening the electric control valve for 4 seconds, closing the electric control valve for 11 seconds, 8230, and circularly opening and closing the electric control valve for 4 times per minute.

And S306, in the process of controlling the electronic control valve 38 to be alternately opened and closed at the sixth frequency in S305, if it is detected that the rotation speed of the motor 5 is continuously increased in the fifth period, controlling the electronic control valve 38 to be alternately opened and closed at the seventh frequency. Wherein the ratio of the closing duration to the opening duration of the electronically controlled valve 38 in each cycle of the seventh frequency > the ratio of the closing duration to the opening duration of the electronically controlled valve 38 in each cycle of the sixth frequency.

That is, in controlling the work load of the diaphragm 3 to alternately turn off and on the work load of the diaphragm 3 at the sixth frequency, if it is determined that the rotation speed of the motor 5 continuously increases in the fifth period, the work load of the diaphragm 3 is controlled to alternately turn off and on the work load of the diaphragm 3 at the seventh frequency; wherein the ratio of the on-duration to the off-duration of the workload in each period of the seventh frequency is greater than the ratio of the on-duration to the off-duration of the workload in each period of the sixth frequency.

The rotational speed of the electric motor 5 is continuously increased during a fifth time period, which means that the energy provided by the electric motor 5 is still greater than the work energy consumption of the diaphragm 3 during this fifth time period. Therefore, the proportion of time that diaphragm 3 normally works can be further increased, or the proportion of dead time of flywheel 24 can be further decreased. Thus, when it is detected that the rotation speed of the motor 5 continuously decreases for the fifth period, the electronic control valve 38 is controlled to alternately open and close at the above-described seventh frequency.

Illustratively, at the seventh frequency: opening the electric control valve for 4 seconds, closing the electric control valve for 12 seconds, 8230, 8230and 8230.

S307, in the process of controlling the electronic control valve 38 to be alternately opened and closed at the sixth frequency in the above S305, if it is detected that the rotation speed of the motor 5 is continuously decreased in the sixth period, the electronic control valve 38 is controlled to be alternately opened and closed at the eighth frequency. Wherein, the ratio of the closing duration to the opening duration of the electronic control valve 38 in each cycle of the sixth frequency > the ratio of the closing duration to the opening duration of the electronic control valve 38 in each cycle of the eighth frequency > the ratio of the closing duration to the opening duration of the electronic control valve 38 in each cycle of the first frequency.

That is, in controlling the working load of the diaphragm 3 to alternately break and make the working load of the diaphragm 3 at the sixth frequency, if it is determined that the rotation speed of the motor 5 is continuously decreased for the sixth period of time, the working load of the diaphragm 3 is controlled to alternately break and make the working load of the diaphragm 3 at the eighth frequency; and the ratio of the access duration to the disconnection duration of the working load in each period of the sixth frequency is greater than the ratio of the access duration to the disconnection duration of the working load in each period of the eighth frequency is greater than the ratio of the access duration to the disconnection duration of the working load in each period of the first frequency.

The rotational speed of the motor 5 is continuously reduced during a sixth time period, which means that the energy supplied by the motor 5 is less than the energy consumed by the diaphragm 3 during this sixth time period. Therefore, the time ratio of the diaphragm 3 to normally do work can be appropriately reduced, or the dead energy storage time ratio of the flywheel 24 can be appropriately increased. Thus, when it is detected that the rotation speed of the motor 5 is continuously increased in the sixth period, the electronic control valve 38 is controlled to be alternately opened and closed at the above-described eighth frequency.

Illustratively, at this eighth frequency: opening the electric control valve for 4 seconds, closing the electric control valve for 10 seconds, 8230, 8230and 8230.

S308, if the rotation speed of the motor 5 is detected to be less than the first rotation speed threshold value, the electronic control valve 38 is controlled to be continuously opened; wherein the first rotation speed threshold is smaller than the lower limit of the first rotation speed interval in S301.

I.e. to control the continuous switching off of the working load of diaphragm 3 if it is determined that the rotational speed of motor 5 is less than a relatively small first rotational speed threshold.

The first rotation speed threshold value is a relatively small value which is smaller than the lower limit of the above-described first rotation speed section in the present embodiment. When the speed of rotation of the motor 5 is less than this very small first speed threshold, indicating that the energy of the motor 5 and the flywheel 24 has been severely insufficient, the electronically controlled valve 38 can be kept open so that the work load of the diaphragm 3 remains in the disconnected state, in order to avoid a severe overload of the motor 5.

S309, if the rotation speed of the motor 5 is detected to be greater than the second rotation speed threshold value, controlling the electric control valve 38 to be continuously closed; wherein, the second rotation speed threshold is not less than the first rotation speed threshold in S308.

That is, if it is determined that the rotation speed of the motor 5 is greater than the second rotation speed threshold value during the continuous disconnection of the working load of the diaphragm 3, the working load of the diaphragm 3 is continuously connected.

It can be understood that during the process of S308 of continuously opening the electrically controlled valve 38, the flywheel 24 is always kept in the idle energy storage state, and the energy provided by the motor 5 is completely converted into the kinetic energy of the flywheel 24. When the rotational speed of motor 5 and flywheel 24 is high enough and the kinetic energy is large enough, if the electrically controlled valve 38 is still kept open, the whole diaphragm pump runs idle, and energy is wasted. Therefore, in the present embodiment, when it is detected that the rotation speed of the motor 5 is greater than the second rotation speed threshold, the electronic control valve 38 is switched from the stuck state to the closed state, and the working load of the diaphragm 3 is switched on, so that the diaphragm 3 normally applies work.

The second rotation speed threshold value should not be smaller than the first rotation speed threshold value in S301, and is preferably a value larger than the upper limit of the first rotation speed section.

Obviously, we can also abandon the above strategies S301-S307, and use only the strategies S308 and S309 to control the diaphragm pump:

i.e. if it is determined that the rotational speed of the motor 5 is less than the first rotational speed threshold, the operational load of the diaphragm 3 is controlled to be continuously switched off. If the rotating speed of the motor 5 is determined to be greater than the second rotating speed threshold value, controlling the working load of the diaphragm 3 to be continuously connected; and the second rotating speed threshold value is not less than the first rotating speed threshold value. In such a control manner, the second rotational speed threshold may generally be equal to the first rotational speed threshold. The disadvantages are that: the rotation speed of the motor 5 may be unstable.

The controller 35 configured in the diaphragm pump also includes a memory, a processor coupled to the memory, and computer instructions stored in the memory and executable by the processor, which when executed by the processor implement the control method.

Example eight:

fig. 29 shows an eighth kind of membrane pump, which is particularly suitable for this case: the extraction force to extract the working fluid from the inlet port 6 into the working chamber 1 is much greater than the thrust to push the working fluid out of the working chamber to the outlet port 7, with the power consumption to extract the working fluid being much greater than the power consumption to push the working fluid. For example, the diaphragm pump is arranged at a high place, to which water at a low place is pumped.

The structure of the diaphragm pump is similar to that of the seventh embodiment, except that:

in this embodiment, an electrically controlled valve 38, which is in communication with the controller 35, is provided between the working chamber 1 and the outlet port 7, in parallel with the outlet valve 9, rather than between the working chamber 1 and the inlet port 6.

It can be seen that in addition to the discharge valve 9 which is originally present in conventional membrane pumps, an electrically controlled valve 38 is additionally provided in this embodiment between the working chamber 1 and the discharge opening 7.

The discharge valve 9 in this embodiment is a mechanical one-way valve, and unlike the discharge valve 9 which is automatically opened and closed by sensing pressure, the opening and closing of the electrically controlled valve 38 can be controlled by an electric signal independent of pressure. In other embodiments, the discharge valve 9 may also be an electrically controlled one-way valve.

If the electrically controlled valve 38 is in the closed state, the operation of the pump head of the diaphragm pump is the same as that of a conventional pump head, and at this time, as long as the diaphragm pump has enough energy, the working fluid in the inlet port 6 can be pumped to the working chamber 1 and then pushed to the outlet port 7. However, as described above, the power consumption of the diaphragm pump for pumping the working fluid is very large, so that the diaphragm pump cannot pump the working fluid in the inlet port 6 to the working chamber 1 in a sufficient amount when the flywheel 24 is insufficiently charged with energy due to the low rotation speed of the motor 5. The working fluid or air in the outlet 7 is drawn into the working chamber 1 with less power consumption, so that the electrically controlled valve 38 is now opened, reducing the load on the diaphragm 3 that is deformed to the left in fig. 29.

If the electrically controlled valve 38 is in the open state, when the piston moves to the right in fig. 29, the working fluid in the working chamber 1 is easily pushed to the outlet 7 through the electrically controlled valve 38, and the power consumption of the pushing action is small; when the piston moves to the left in fig. 29, the electric control valve 38 is in the open state, and the suction valve 8 is kept in the closed state due to the larger opening pressure, so the working fluid (or air) in the discharge port 7 can be easily pumped from the opened electric control valve 38 to the working chamber 1, and the power consumption of the pumping action is also smaller. Corresponding to at least partially disconnecting the working load of the diaphragm 3. Therefore, in the process, a part of the output power provided by the motor 5 is used for completing the pushing and extracting actions, and the other part of the output power is used for applying work to the flywheel 24, so that the flywheel 24 is accelerated to store energy.

Therefore, the present embodiment provides the following control method which is basically the same as the seventh embodiment and is briefly introduced, and the detailed control method can refer to the contents of the seventh embodiment.

S401, during the operation of the electric motor 5, the electronically controlled valve 38 is controlled to open and close alternately at a first frequency.

Preferably, in the case of determining that the rotation speed of the electric motor 5 is in the set first rotation speed interval, the electronically controlled valve 38 is controlled to open and close alternately at a first frequency.

S402, in the process of controlling the electric control valve 38 to be opened and closed alternately at the first frequency in S401, if the rotation speed of the motor 5 is detected to be continuously reduced within the first time period, the electric control valve 38 is controlled to be opened and closed alternately at the third frequency; wherein the ratio of the closing duration to the opening duration of the electrically controlled valve 38 in each cycle of the third frequency < the ratio of the closing duration to the opening duration of the electrically controlled valve 38 in each cycle of the first frequency.

And S403, in the process of controlling the electronic control valve 38 to alternately open and close at the third frequency in S402, if it is detected that the rotation speed of the motor 5 is continuously decreased for the second period of time, controlling the electronic control valve 38 to alternately open and close at the fourth frequency. Wherein the ratio of the closing duration to the opening duration of the electronically controlled valve 38 in each cycle of the fourth frequency < the ratio of the closing duration to the opening duration of the electronically controlled valve 38 in each cycle of the third frequency.

S404, in the process of controlling the electronic control valve 38 to alternately open and close at the third frequency in S402, if it is detected that the rotation speed of the motor 5 continuously increases for the third period of time, the electronic control valve 38 is controlled to alternately open and close at the fifth frequency. Wherein, the ratio of the closing duration to the opening duration of the electronic control valve 38 in each period of the first frequency > the ratio of the closing duration to the opening duration of the electronic control valve 38 in each period of the fifth frequency > the ratio of the closing duration to the opening duration of the electronic control valve 38 in each period of the third frequency.

S405, in the process of S401 controlling the electronic control valve 38 to be alternately opened and closed at the first frequency, if it is detected that the rotation speed of the motor 5 continuously increases for the fourth time period, controlling the electronic control valve 38 to be alternately opened and closed at a sixth frequency; wherein the ratio of the closing duration to the opening duration of the electronically controlled valve 38 in each cycle of the sixth frequency > the ratio of the closing duration to the opening duration of the electronically controlled valve 38 in each cycle of the first frequency.

S406, in the process of controlling the electronic control valve 38 to alternately open and close at the sixth frequency at S405, if it is detected that the rotation speed of the motor 5 continuously increases in the fifth period, the electronic control valve 38 is controlled to alternately open and close at the seventh frequency. Wherein the ratio of the closing period to the opening period of the electronically controlled valve 38 in each cycle at the seventh frequency > the ratio of the closing period to the opening period of the electronically controlled valve 38 in each cycle at the sixth frequency.

S407, in the process of controlling the electronic control valve 38 to be alternately opened and closed at the sixth frequency in S405, if it is detected that the rotation speed of the motor 5 is continuously decreased for the sixth period, the electronic control valve 38 is controlled to be alternately opened and closed at the eighth frequency. Wherein the ratio of the closing duration to the opening duration of the electronically controlled valve 38 in each cycle at the sixth frequency > the ratio of the closing duration to the opening duration of the electronically controlled valve 38 in each cycle at the eighth frequency > the ratio of the closing duration to the opening duration of the electronically controlled valve 38 in each cycle at the first frequency.

And S408, if the rotation speed of the motor 5 is detected to be less than a first smaller rotation speed threshold value, controlling the electronic control valve 38 to be continuously opened.

S409, if the rotating speed of the motor 5 is detected to be greater than the second rotating speed threshold value, controlling the electronic control valve 38 to be continuously closed; wherein the second rotation speed threshold is not less than the first rotation speed threshold in S408. Preferably, the second rotation speed threshold is greater than the upper limit of the first rotation speed section in S401.

Example nine:

fig. 32 shows a ninth diaphragm pump which is also applicable to the case described in embodiment eight: the extraction force to extract the working fluid from the inlet port 6 into the working chamber 1 is much greater than the thrust to push the working fluid out of the working chamber to the outlet port 7, with the power consumption to extract the working fluid being much greater than the power consumption to push the working fluid. For example, the diaphragm pump is arranged at a high place to which water at a low place is pumped.

The structure of the diaphragm pump is similar to that of the eighth embodiment, except that: in this embodiment, instead of additionally adding an electrically controlled valve between the working chamber 1 and the discharge opening 7, the discharge valve 9 is provided as an electrically controlled one-way valve in communication with the controller 35. As in fig. 33.

As known, the electrically controlled check valve mainly differs from a common mechanical check valve in that: the common mechanical one-way valve is directly opened or closed by the pressure, and the reverse flow of the fluid cannot be realized. The electric control one-way valve has more functions and application modes, and mainly comprises two types: i, some electrically-controlled one-way valves can be opened (or closed) in response to an electric control signal on the basis of completely reserving the functions of a common mechanical one-way valve; and ii, some electric control one-way valves need to convert the fluid pressure at the valve into an electric control signal, and then the opening (or closing) of the valve is controlled by the electric control signal. Therefore, the reverse flow of the fluid can be realized only by applying the intervention of the control command to the electric control one-way valve. For example, chinese patent application publication No. CN108825828A discloses an electrically controlled check valve which can actively open a check valve in an electrically controlled manner, so as to realize reverse flow of fluid.

For the same purpose as that of the eighth embodiment, this embodiment mainly implements, by a computer instruction written into the controller 35, the following control method for the diaphragm pump:

and S501, controlling the discharge valve 9 to be opened for an eighth time period every seventh time period in the running process of the motor 5.

That is, during the operation of the motor 5, the discharge valve 9 is alternately opened for an eighth period-at an interval of a seventh period-the discharge valve 9 is opened for an eighth period of 8230; \8230;. 8230;. The discharge valve 9 is opened. In effect, this corresponds to the embodiment seven and the embodiment eight: during operation of the motor 5, the working load of the diaphragm 3 is alternately switched off and on at a first frequency.

The above-mentioned "eighth period of opening the discharge valve 9" means that the discharge valve 9 is kept in the open state for the eighth period. The term "interval of the seventh period" means that the controller 35 does not actively intervene in the operation of the discharge valve 9 during the seventh period, and allows the discharge valve 9 to operate according to its original characteristics. Such as: the switch is turned on or off according to physical pressure or according to an original electric control strategy.

The above-mentioned "letting the discharge valve 9 operate in its own original characteristic" generally includes two cases:

1) The discharge valve 9 is opened or closed according to the physical pressure. In this case, the controller 35 completely removes the intervention on the operating state of the discharge valve 9, allowing the discharge valve 9 to be automatically opened or closed by directly sensing the pressures on both sides thereof. That is, the controller 35 does not operate at all on the discharge valve 9, allowing the discharge valve 9 to open or close by only non-electrical mechanical force. This is suitable for application to an electrically controlled one-way valve of the type "i" described above.

2) The discharge valve 9 is opened or closed according to an original electrical control strategy. In this case, the controller need only remove the above-mentioned active intervention on the discharge valve and use a conventional strategy to control the opening and closing of the discharge valve 9. "the opening and closing of the discharge valve 9 is controlled using a conventional strategy", which is typically: the controller 35 controls the discharge valve 9 to open or close mainly according to the pressure at the discharge valve 9. This is suitable for application to the above-mentioned electrically controlled check valve of the type "ii".

For example, during motor operation, the controller 35 intermittently actively opens the discharge valve 9 once every 4 seconds, and every 2 seconds. I.e., open the discharge valve and hold for 2 seconds-4 seconds apart-open the discharge valve and hold for 2 seconds \8230;.

During operation of the electric motor 5, the controller 35 actively and intermittently opens the outlet valve 9 in a set rhythm, so that the working load of the diaphragm 3 is alternately switched off and on at a set first frequency. Thereby making flywheel 24 and diaphragm 3 intermittently perform work in each cycle time of the first frequency, and motor 5 periodically charges flywheel 24 with energy. Generally, in each cycle time (e.g. 4+2=6 seconds in this embodiment), the energy supplied by the motor 5 in continuous operation is balanced with the energy consumed by the diaphragm 3 in normal work only in a partial time (e.g. 4 seconds in this embodiment), and then the diaphragm pump can operate continuously and stably.

It will be appreciated that the controller 35 actively controls the discharge valve 9 to open with the diaphragm 3 work load disconnected, the length of time the discharge valve 9 is actively opened = the length of time the diaphragm work load is disconnected. When the controller 35 stops active intervention on the discharge valve 9, the discharge valve 9 operates normally, the working load of the diaphragm 3 is switched on, and the interval duration during which the discharge valve 9 is opened = the switching on duration of the diaphragm working load, is actively controlled by the controller 35. For convenience of description, in the present embodiment, the on-period of the diaphragm work load, that is, the period of time between the active control of the controller 35 and the opening of the discharge valve 9, is simply referred to as "the on-period of the work load", and the off-period of the diaphragm work load is simply referred to as "the off-period of the work load".

It is not appropriate to adopt the control strategy of S501 if the motor 5 is rotating at a low speed (e.g., just started). Therefore, the control strategy of S501 may be adopted only when the rotation speed of the motor 5 is in the set first rotation speed range. That is, during the operation of the motor 5, if it is determined that the rotation speed of the motor 5 is in the first rotation speed section, the discharge valve 9 is controlled to be opened for the eighth period every seventh period in response to the determination, such that the work load of the diaphragm 3 is alternately switched off and on at the first frequency. It will be appreciated that the first speed range is preferably a range around the rated speed of the motor 5. For example, if the rated rotational speed of the electric motor 5 is 10000 rpm, the first rotational speed interval may be selected to be an interval of 9000-11000 rpm.

Of course, it is also possible to adjust the rhythm of the active opening of the outlet valve 9 when the electric motor 5 is in different speed ranges. For example, if it is determined that the rotation speed of the electric motor 5 is in a second rotation speed interval which is different from and does not intersect with the first rotation speed interval and which is smaller than the first rotation speed interval, the discharge valve 9 is controlled to be opened for the tenth period every ninth period. I.e. if it is determined that the rotational speed of the motor 5 is in the second rotational speed interval, the working load of the diaphragm 3 is controlled to be alternately switched off and on at the second frequency.

S502, in the process of controlling the discharge valve 9 to be opened for the eighth time period every seventh time period in the S501, if the rotation speed of the motor 5 is detected to be continuously reduced in the first time period, for example, three minutes, the discharge valve 9 is controlled to be opened for the twelfth time period every eleventh time period; wherein the ratio of the eleventh time period to the twelfth time period is less than the ratio of the seventh time period to the eighth time period.

That is, if it is determined that the rotation speed of the motor 5 is continuously reduced for the first time period during the control of the diaphragm 3 to alternately turn off and on the diaphragm 3 at the first frequency, the control of the diaphragm 3 to alternately turn off and on the diaphragm 3 at the third frequency. And the ratio of the access duration to the disconnection duration of the working load in each period of the third frequency is less than the ratio of the access duration to the disconnection duration of the working load in each period of the first frequency.

S503, in the process that the discharge valve 9 is controlled to be opened for the twelfth period every interval of the eleventh period in the S502, if the rotation speed of the motor 5 is detected to be continuously reduced in the second period, the discharge valve 9 is controlled to be opened for the fourteenth period every interval of the thirteenth period; wherein a ratio of the thirteenth time period to the fourteenth time period is less than a ratio of the eleventh time period to the twelfth time period.

That is, in controlling the operational load of the diaphragm 3 to be alternately turned off and on at the third frequency, if it is determined that the rotational speed of the motor 5 is continuously decreased for the second period of time, the operational load of the diaphragm 3 is controlled to be alternately turned off and on at the fourth frequency; and the ratio of the access duration to the disconnection duration of the working load in each period of the fourth frequency is less than the ratio of the access duration to the disconnection duration of the working load in each period of the third frequency.

S504, in the process of controlling the discharge valve 9 to be opened for the twelfth time interval by the eleventh time interval in the S502, if the rotation speed of the motor 5 is detected to be continuously increased in the third time interval, controlling the discharge valve 9 to be opened for the sixteenth time interval by the fifteenth time interval; wherein a ratio of the seventh time period to the eighth time period > a ratio of the fifteenth time period to the sixteenth time period > a ratio of the eleventh time period to the twelfth time period.

That is, in controlling the operational load of the diaphragm 3 to be alternately turned off and on at the third frequency, if it is determined that the rotational speed of the motor 5 is continuously increased for the third period of time, the operational load of the diaphragm 3 is controlled to be alternately turned off and on at the fifth frequency; and the ratio of the access duration to the disconnection duration in each period of the first frequency is greater than the ratio of the access duration to the disconnection duration in each period of the fifth frequency is greater than the ratio of the access duration to the disconnection duration in each period of the third frequency.

S505, in the process of controlling the discharge valve 9 to be opened for the eighth time interval at the seventh time interval in the S501, if the rotation speed of the motor 5 is continuously increased within the fourth time interval, controlling the discharge valve 9 to be opened for the eighteenth time interval at the seventeenth time interval; wherein a ratio of the seventeenth time period to the eighteenth time period is greater than a ratio of the seventh time period to the eighth time period.

That is, if it is determined that the rotation speed of the motor 5 is continuously increased for the fourth time period during the control of the alternately opening and closing of the working load of the diaphragm 3 at the first frequency, the control of the alternately opening and closing of the working load of the diaphragm 3 at the sixth frequency; wherein, the ratio of the access duration to the disconnection duration of the working load in each period of the sixth frequency is greater than the ratio of the access duration to the disconnection duration of the working load in each period of the first frequency.

And S506, in the process that the discharge valve 9 is controlled to be opened for the eighteenth time period every seventeenth time period in the above S505, if it is detected that the rotation speed of the motor 5 is continuously increased in the fifth time period, the discharge valve 9 is controlled to be opened for the twentieth time period every nineteenth time period. Wherein a ratio of the nineteenth time period to the twentieth time period > a ratio of the seventeenth time period to the eighteenth time period.

That is, in controlling the operation load of the diaphragm 3 to be alternately turned off and on at the sixth frequency, if it is determined that the rotation speed of the motor 5 is continuously increased for the fifth period of time, the operation load of the diaphragm 3 is controlled to be alternately turned off and on at the seventh frequency; and the ratio of the access duration to the disconnection duration of the working load in each period of the seventh frequency is greater than the ratio of the access duration to the disconnection duration of the working load in each period of the sixth frequency.

And S507, in the process that the discharge valve 9 is controlled to be opened for the eighteenth time period every seventeenth time period in the above S505, if it is detected that the rotation speed of the motor 5 is continuously reduced in the sixth time period, the discharge valve 9 is controlled to be opened for the twenty second time period every twenty first time period. Wherein, the ratio of the seventeenth duration to the eighteenth duration is greater than the ratio of the twenty-first duration to the twenty-second duration is greater than the ratio of the seventh duration to the eighth duration.

That is, in controlling the operation load of the diaphragm 3 to be alternately turned off and on at the sixth frequency, if it is determined that the rotation speed of the motor 5 is continuously increased for the sixth period of time, the operation load of the diaphragm 3 is controlled to be alternately turned off and on at the eighth frequency; and the ratio of the access duration to the disconnection duration of the working load in each period of the sixth frequency is greater than the ratio of the access duration to the disconnection duration of the working load in each period of the eighth frequency is greater than the ratio of the access duration to the disconnection duration of the working load in each period of the first frequency.

S508, if the rotation speed of the motor 5 is detected to be less than a first smaller rotation speed threshold value, controlling the discharge valve 9 to be continuously opened; wherein the first rotation speed threshold is smaller than the lower limit of the first rotation speed interval in S501.

S509, if it is detected that the rotation speed of the electric motor 5 is greater than the second rotation speed threshold, removing the above-mentioned active intervention of the controller 35 on the discharge valve 9; wherein the second rotation speed threshold is not less than the first rotation speed threshold in S508, and the second rotation speed threshold is preferably a value greater than the upper limit of the first rotation speed section in S501.

In other embodiments, the above strategies of S501-S507 may be abandoned, and only the strategies of S508 and S509 are used to control the diaphragm pump:

that is, if it is determined that the rotation speed of motor 5 is less than the first rotation speed threshold value, the operating load of diaphragm 3 is controlled to be continuously turned off; if the rotating speed of the motor 5 is determined to be greater than the second rotating speed threshold value, controlling the working load of the diaphragm 3 to be continuously connected; and the second rotating speed threshold value is not less than the first rotating speed threshold value. In such a control mode, the second rotational speed threshold may generally be equal to the first rotational speed threshold.

The controller 35 includes a memory, a processor coupled to the memory, and computer instructions stored in the memory and executable by the processor, which when executed by the processor implement the control method.

Example ten:

fig. 34 shows a tenth diaphragm pump which is also applicable to the case described in embodiment seven: the extraction force to extract the working fluid from the inlet port 6 to the working chamber 1 is much less than the thrust force to push the working fluid out of the working chamber to the outlet port 7, with the power consumption to extract the working fluid being much less than the power consumption to push the working fluid. For example, a diaphragm pump is arranged at the water source, pushing water from low to high. This is similar to the operation of a diaphragm compressor and is therefore also applicable to diaphragm compressors.

The structure of the diaphragm pump is similar to that of the seventh embodiment, except that: in this embodiment, instead of additionally providing an electrically controlled valve between the working chamber 1 and the inlet port 6, the suction valve 8 is provided as an electrically controlled one-way valve in communication with the controller 35.

For the same purpose as that of the seventh embodiment, the present embodiment mainly realizes the following control method similar to that of the ninth embodiment for the diaphragm pump by the computer instructions (codes) written into the controller 35, and the detailed control method can refer to the contents of the ninth embodiment.

And S601, controlling the suction valve 8 to be opened for an eighth time period every seventh time period in the running process of the motor 5.

That is, during the operation of the motor 5, the suction valve 8 is alternately opened for an eighth length of time-at an interval of a seventh length of time-the suction valve 8 is opened for an eighth length of time \8230;. In effect, this corresponds to the seventh embodiment, the eighth embodiment, and the ninth embodiment: during operation of the motor 5, the working load of the diaphragm 3 is alternately switched off and on at the first frequency.

Preferably, in the case where it is determined that the rotation speed of the motor 5 is in the set first rotation speed section, the suction valve 8 is controlled to be opened for the eighth period every seventh period.

S602, in the process of controlling the suction valve 8 to be opened for the eighth time interval by the seventh time interval in the S601, if the rotation speed of the motor 5 is detected to be continuously reduced in the first time interval, controlling the suction valve 8 to be opened for the twelfth time interval by the eleventh time interval; wherein a ratio of the eleventh time period to the twelfth time period is less than a ratio of the seventh time period to the eighth time period.

S603, in the process of controlling the suction valve 8 to be opened for the twelfth period every eleventh period in S602, if it is detected that the rotation speed of the motor 5 is continuously decreased in the second period, controlling the suction valve 8 to be opened for the fourteenth period every thirteenth period. Wherein a ratio of the thirteenth time period to the fourteenth time period is less than a ratio of the eleventh time period to the twelfth time period.

S604, in the process of controlling the suction valve 8 to be opened for the twelfth period every eleventh period in S602, if it is detected that the rotation speed of the motor 5 is continuously increased in the third period, the suction valve 8 is controlled to be opened for the sixteenth period every fifteenth period. Wherein, the ratio of the seventh time length to the eighth time length is greater than the ratio of the fifteenth time length to the sixteenth time length is greater than the ratio of the eleventh time length to the twelfth time length.

S605, in the process that the suction valve 8 is controlled to be opened for the eighth time period every seventh time period in the S601, if the rotation speed of the motor 5 is detected to be continuously increased in the fourth time period, the suction valve 8 is controlled to be opened for the eighteenth time period every seventeenth time period; wherein a ratio of the seventeenth time period to the eighteenth time period is greater than a ratio of the seventh time period to the eighth time period.

And S606, in the process of controlling the suction valve 8 to be opened for the eighteenth time period every seventeenth time period in the above S605, if the rotation speed of the motor 5 is detected to be continuously increased in the fifth time period, controlling the suction valve 8 to be opened for the twentieth time period every nineteenth time period. Wherein a ratio of the nineteenth duration to the twentieth duration is greater than a ratio of the seventeenth duration to the eighteenth duration.

And S607, in the process of controlling the suction valve 8 to be opened for the eighteenth time period every the seventeenth time period in the above S605, if it is detected that the rotation speed of the motor 5 is continuously decreased in the sixth time period, controlling the suction valve 8 to be opened for the twenty second time period every the twenty first time period. Wherein a ratio of the seventeenth time period to the eighteenth time period > a ratio of the twenty first time period to the twenty second time period > a ratio of the seventh time period to the eighth time period.

S608, if it is detected that the rotation speed of the motor 5 is less than a first, relatively small rotation speed threshold, the suction valve 8 is controlled to be continuously opened.

S609, if it is detected that the rotation speed of the electric motor 5 is greater than the second rotation speed threshold, removing the above active intervention of the controller 35 on the suction valve 8; wherein the second rotation speed threshold is not less than the first rotation speed threshold in S608.

In other embodiments, the strategies of S601-S607 may be discarded and only the strategies of S608 and S609 may be used to control the diaphragm pump.

Example eleven:

fig. 36 shows an eleventh diaphragm pump, which is similar in structure to the first embodiment, and mainly differs therefrom in that:

in this embodiment, a piston is not provided, but a bellows 26 of axially telescopically deformable and rotational body structure is provided. The power fluid in the power chamber 2 is pushed by the telescopic deformation of the leather bag 26 to drive the diaphragm 3 to deform, and then the working fluid in the working chamber 1 is squeezed to do work. The axis of the bladder 26 extends linearly in the left-right direction in fig. 38.

As shown in fig. 37 and with reference to fig. 36, a portion of the power chamber 2 is formed inside the bladder 26, with the remainder located outside the bladder 26. In operation, the power chamber 2 inside and outside the bladder 26 is filled with power fluid. The motor 5 is connected to the left end of the bladder 26 through a transmission system to drive the bladder to deform in an axial direction (left-right direction in fig. 37). The right end of the bladder 26 is fixed to the housing 33 of the diaphragm pump.

As shown in fig. 39 with reference to fig. 38 and 37, the drive train of this embodiment is identical in construction to the drive train of the sixth embodiment except that the push-pull rod of the sixth embodiment is connected to the piston, and the push-pull rod 16 of this embodiment is connected to the bladder 26. The transmission system is also provided with a flywheel 24 connected in series between the motor 5 and the reducer 12. In operation, the push-pull rod 16 moves the left end of the leather bag 26 to the left and right in fig. 36, so that the leather bag 26 is axially stretched and deformed. When the leather bag 26 is driven by the flywheel 24 to axially contract, if the valve 11 is in an open state, a part of hydraulic oil in the power chamber 2 enters the power fluid storage chamber 10; if the valve 11 is in a closed state, the hydraulic oil in the power chamber 2 extrudes the diaphragm 3 to deform rightwards, and works on the working fluid.

It is obvious that the transmission system in this embodiment may also adopt the structure implementing the second embodiment or the third embodiment.

The bladder 26 is made of rubber, has a certain thickness, can bear strong radial pressure without deformation (no radial deformation) and has basically the same structure as that of an air spring shock absorber used in the automobile field.

The leather bag 26 is integrally provided with a plurality of fold rings which are closely arranged along the axis direction of the leather bag, and each fold ring surrounds the periphery of the axis of the leather bag so as to improve the axial deformation capability of the leather bag 26.

For the sake of illustration, the power chamber 2 is now divided into two parts, the power chamber 2 inside the bladder 26 being referred to as the first half-chamber 2a, and the power chamber 2 outside the bladder 26 being referred to as the second half-chamber 2b, as shown in fig. 37.

The left end and the right end of the leather bag 26 are both of an open structure, and the right end of the push-pull rod 16 plugs the opening at the left end of the leather bag. The opening at the right end of the bladder 26 is used for communicating with the second half-chamber 2b, which is a power chamber outside the bladder, so that the power fluid b can flow between the power chambers inside and outside the bladder, namely between the first half-chamber 2a and the second half-chamber 2 b.

If the opening at the right end of the bellows 26 is not specially treated, the diaphragm 3 is deformed to the left, and the diaphragm is excessively deformed at the opening, thereby shortening the service life thereof. In this respect, in this embodiment, a barrier net 27 is fixedly disposed at the opening at the right end of the leather bag 26 to prevent excessive deformation of the diaphragm 3. The first half chamber 2a and the second half chamber 2b are respectively located at the left and right sides of the barrier net 27, and the second half chamber 2b is formed between the diaphragm 3 and the barrier net 27.

Further, the second half cavity 2b is a conical cavity with the large end facing the diaphragm 3, and the barrier net 27 is arranged at the small end of the conical cavity to better adapt to the leftward deformation of the diaphragm 3, and can be integrally attached to the cavity wall of the second half cavity 2b and the right side surface of the diaphragm 3 when the diaphragm is deformed leftward. Similarly, the working chamber 1 is also arranged with a large end facing the conical cavity of the diaphragm 3, which can also be pressed against the wall of the working chamber 1 over a large area when the diaphragm is deformed to the right. Obviously, similar designs are also adopted in the first to seventh embodiments.

When the bellows 26 is stretched to a certain length by the push-pull rod 16, the diaphragm 3 is deformed to the left and is placed against the wall surface of the second chamber half 2b and the side surface of the barrier net 27 facing the second chamber half 2 b. When the bladder 26 is compressed to a certain length by the push-pull rod 16, the diaphragm 3 deforms to the right and is arranged against the wall surface of the working chamber 1.

The push-pull rod 16, the bladder 26 and the diaphragm 3 are coaxially arranged, and the barrier net 27 is arranged in parallel with the diaphragm 3. The axis of the bladder 26 is perpendicular to the diaphragm 3 and the extension of the axis of the bladder 26 passes through the centre of the diaphragm 3.

It has been mentioned above that the main purpose of the operation of the motor 5 is to provide a driving force to the diaphragm 3 to drive the movement of the diaphragm 3 to squeeze and draw the working fluid. The leather bag 26 and the transmission system connecting the motor and the leather bag are all arranged on the driving path of the motor 5 for transmitting the driving force to the diaphragm 3, and the leather bag 26 and the transmission system connecting the motor and the leather bag are all part of the driving path of the motor 5 for transmitting the driving force to the diaphragm 3.

The motive fluid b filled in the motive force chamber 2 is also provided in a drive path through which the motor 5 transmits a driving force to the diaphragm 3, and has a function of transmitting the driving force to the diaphragm 3, so the motive fluid b filled in the motive force chamber 2 is also a component of the drive path through which the motor 5 transmits the driving force to the diaphragm 3.

Example twelve:

fig. 40 shows a twelfth diaphragm pump that adds a pump head to the eleventh embodiment to perform work on two portions of working fluid simultaneously. The method comprises the following specific steps:

in fig. 40, the diaphragm pump is provided with a total of two bladders 26. The motor 5 simultaneously drives the two leather bags 26 to stretch and deform in the left-right direction in fig. 40 through a set of transmission system, so as to respectively drive the left diaphragm 3 and the right diaphragm 3 to do work on the working fluid a in the corresponding working chambers 1. The structure of the transmission system is the same as that of the fourth embodiment, except that in the fourth embodiment, two push-pull rods are respectively connected with the left and right pistons, and in the fourth embodiment, two push-pull rods are respectively connected with the left and right bladders 26.

The structure of the transmission system in this embodiment is the same as that in the fifth embodiment, except that in the fifth embodiment, the push-pull rod 16 is connected to the bladder 26, and the piston is connected to the push-pull rod.

Obviously, the transmission system in the present embodiment may also adopt the structure of the sixth embodiment.

Example thirteen:

fig. 41 and 42 show a thirteenth type of diaphragm pump, which has substantially the same structure as the embodiment twelve, and mainly differs therefrom in that:

in this embodiment, the power chamber 2 is formed entirely inside the bladder 26, and the diaphragm 3 is provided at the right end portion of the bladder 26, and an oil path for communicating the power chamber 2 and the power fluid storage chamber 10 is led from the push-pull rod 16 on the left side of the bladder to the inside of the bladder 26.

In order to improve the sealing and isolating capability of the diaphragm 3 to the power chamber 2 and the working chamber 1 and facilitate the manufacture and installation of related parts, the diaphragm 3 and the leather bag 26 are made into an integral structure and integrally formed.

Example fourteen:

fig. 43 shows a fourteenth kind of diaphragm pump, which has a structure substantially the same as that of the thirteenth embodiment, except for:

the diaphragm 3 is arranged inside the leather bag 26, so that the inner cavity of the leather bag 26 is divided into a power chamber 2 and a working chamber 1, and the power chamber 2 and the working chamber 1 are both formed in the leather bag 26. During operation, the push-pull rod 16 pushes the leather bag 26 to contract axially rightward, on one hand, the hydraulic oil in the power chamber 2 pushes the diaphragm 3 to squeeze the working fluid in the working chamber 1 rightward, and on the other hand, the working chamber 1 itself also generates contraction deformation to squeeze the working fluid therein to do work. Compared with the twelfth embodiment, the deformation amount of the diaphragm 3 is smaller in the present embodiment when the same volume of the working fluid is squeezed, which is beneficial to prolonging the service life of the diaphragm pump, especially the diaphragm.

In order to ensure the sealing isolation of the diaphragm 3 to the power chamber 2 and the working chamber 1 and facilitate the manufacture and installation of related parts, the present embodiment integrates the diaphragm 3 and the bladder 26 into a whole structure, and the two are integrally formed.

Example fifteen:

fig. 45 and 46 show a fifteenth diaphragm pump, which is similar in structure to the fourteenth embodiment, and mainly differs therefrom in that:

as shown in Figs. 46 and 47, a left thin right thick generally trumpet shaped rigid collar 30 is attached to the right side of the bladder 26, the rigid collar 30 having a small opening at the left end and a large opening at the right end. The right opening of the leather bag 26 is directly communicated with the left opening of the rigid ring sleeve 30, and the diaphragm 3 is sealed at the right opening of the rigid ring sleeve 30. To the right side of the diaphragm 3 is attached an annular deformable flexible ring plate 31. One part of the power chamber 2 is formed within the rigid cuff 30 and the other part is formed within the bladder 26.

When the diaphragm 3 and the flexible ring 31 are in their natural states as shown in figures 46 and 47, they are both of substantially planar configuration and are in abutment, the volume of the working chamber being zero. As the push-pull rod 16 moves the left end of the bladder 26 to the left in fig. 47. On one hand, the negative pressure formed in the power chamber 2 makes the diaphragm 3 deform leftwards, on the other hand, the rigid ring sleeve 30 moves leftwards along with the leather bag 26, and further drives the outer edge of the flexible ring piece 31 to deform leftwards, so that the flexible ring piece 31 is roughly in a conical structure with the left thick and the right thin. A working chamber 1 for sucking the working fluid is formed between the diaphragm 3 and the flexible ring plate 31, as shown in fig. 48. And the volume of the working chamber is then positively correlated with the amount of deformation of the diaphragm 3 and the flexible ring 31.

It can be seen that in operation the diaphragm 3 and the flexible ring 31 deform together to change the volume of the working chamber and thereby draw working fluid into the working chamber or push the working fluid out of the working chamber entirely. Compared with the first to ninth embodiments, the deformation amount of the diaphragm 3 in the present embodiment is smaller when the same volume of working fluid is squeezed, which is beneficial to prolonging the service life of the diaphragm.

In order to improve the deformation adaptability of the diaphragm 3 and the flexible ring plate 31 and further improve the service life of the diaphragm 3 and the flexible ring plate 31, a circle of deformation wrinkles 3a with a shaft protruding to the right is integrally formed on the diaphragm 3, and a circle of deformation wrinkles 31a with a shaft protruding to the right is integrally formed on the flexible ring plate 31. The pressure bearing seat 32 fixed with the housing 33 is arranged on the right side of the flexible ring sheet 31, the pressure bearing seat 32 has a bearing plane facing the flexible ring sheet, and the bearing plane is provided with an annular groove 32a which is concave inwards and is matched with the deformation wrinkles 3a and the second deformation wrinkles 31a, so as to accommodate the deformation wrinkles 3a and the second deformation wrinkles 31a in the state of fig. 46. When the membrane sheet 3 and the flexible ring sheet 31 are in the natural state of fig. 46 and 47, the parts except the deformed wrinkles are in a planar structure, that is, the non-deformed wrinkle area of the membrane sheet 3 and the flexible ring sheet 31 in the natural state is in a planar structure.

Furthermore, an oil-feeding chamber is provided around the bladder 26, and an oil passage for communicating the power chamber 2 and the power fluid storage chamber 10 passes through the oil-feeding chamber, and the valve 11 is provided on the rigid collar 30.

Example sixteen:

fig. 50 shows a sixteenth diaphragm pump which is similar in structure to the eleventh embodiment except that the present embodiment is not provided with a motive fluid storage chamber communicating with the motive chamber 2.

Example seventeen:

fig. 51 shows a seventeenth diaphragm pump of a construction similar to the twelfth embodiment except that the present embodiment is not provided with a motive fluid storage chamber communicating with the motive chamber 2.

Example eighteen:

fig. 52 shows an eighteenth diaphragm pump, which is similar in structure to the thirteenth embodiment except that the present embodiment is not provided with a motive fluid storage chamber communicating with the motive chamber 2.

Example nineteenth:

fig. 53 shows a nineteenth diaphragm pump which is similar in structure to the fourteenth embodiment except that the present embodiment is not provided with a motive fluid storage chamber communicating with the motive chamber 2.

Example twenty:

fig. 54 shows a twentieth diaphragm pump which is similar in structure to the fifteenth embodiment except that the present embodiment is not provided with a motive fluid storage chamber communicating with the motive chamber 2.

It is understood that the structures of the above embodiments are all applicable to a diaphragm compressor for compressing a working fluid. Such as compressing low pressure refrigerant to a high pressure state or even a liquid state, and is particularly suitable for use as an air conditioning compressor.

Example twenty one: air conditioning system

Inspired by the seventh and tenth embodiments, the present embodiment provides an air conditioning system capable of intermittently performing high-power work. As shown in fig. 55, the air conditioning system includes a compressor 100, a condenser 200, a throttle valve 300, and an evaporator 400, which are fluidly connected in sequence and constitute a closed circuit. The air conditioning system is charged with a refrigerant. When the air-conditioning system works, a refrigerant sequentially flows through the compressor, the condenser, the throttle valve and the evaporator, so that the air-conditioning system can refrigerate or heat outwards.

The main improvement of the air conditioning system is that the compressor 100 is a diaphragm compressor, and the structure of the diaphragm compressor is basically the same as that of the diaphragm pump in the sixth embodiment, and the diaphragm compressor also includes a motor speed sensor 34 and a controller 35 connected in communication with the motor speed sensor, except that the diaphragm compressor is not provided with the clutch in the sixth embodiment, and refer to fig. 24.

As shown in fig. 56 and with reference to fig. 55, throttle valve 300 is an electronically controlled throttle valve that is communicatively coupled to controller 35.

As is known, the opening and closing action of an electronically controlled throttle valve can be controlled by an electronically controlled signal, and in conventional air conditioning systems the electronically controlled throttle valve typically controls the on-off state based primarily on the pressure at the throttle valve. Conventional mechanical throttle valves are directly pressure-responsive to open (including degree of opening) or close. Like the electrically controlled check valve, the electrically controlled throttle valve mainly includes two types: i, some electronic control throttle valves can be opened and closed in response to an electronic control signal on the basis of completely retaining the functions of a common mechanical throttle valve; and ii, some electrically controlled throttle valves are completely controlled to be opened and closed by an electrically controlled signal.

For the same purposes as those of the seventh embodiment and the tenth embodiment, the present embodiment mainly implements a control method of the air conditioning system, which is briefly described below, by a computer instruction (code) written in the controller 35, and the detailed control method can refer to the contents of the ninth embodiment and the tenth embodiment.

And S701, if the rotating speed of the motor is determined to be in the set first rotating speed interval in the process of running the motor 5 of the diaphragm compressor, controlling the throttle valve 300 to open for an eighth time period at intervals of a seventh time period.

S702, in the process of controlling the throttle valve 300 to be opened for the eighth period every seventh period in S701, if it is detected that the rotation speed of the motor is continuously decreased for the first period, controlling the throttle valve 300 to be opened for the twelfth period every eleventh period; wherein the ratio of the eleventh time period to the twelfth time period is less than the ratio of the seventh time period to the eighth time period.

S703, in the process of S702 controlling the throttle valve 300 to be opened for the twelfth period at intervals of the eleventh period, if it is detected that the rotation speed of the motor is continuously decreased in the second period, controlling the throttle valve 300 to be opened for the fourteenth period at intervals of the thirteenth period; wherein a ratio of the thirteenth time period to the fourteenth time period is less than a ratio of the eleventh time period to the twelfth time period.

S704, in the process of controlling the throttle valve 300 to open for the twelfth period at intervals of the eleventh period in S702, if it is detected that the rotation speed of the motor is continuously increased for the third period, the throttle valve 300 is controlled to open for the sixteenth period at intervals of the fifteenth period. Wherein a ratio of the seventh time period to the eighth time period > a ratio of the fifteenth time period to the sixteenth time period > a ratio of the eleventh time period to the twelfth time period.

S705, in the process of controlling the throttle valve 300 to be opened for the eighth time period every seventh time period in S701, if the rotation speed of the motor is detected to be continuously increased in the fourth time period, controlling the throttle valve 300 to be opened for the eighteenth time period every seventeenth time period; wherein a ratio of the seventeenth time period to the eighteenth time period is greater than a ratio of the seventh time period to the eighth time period.

S706, in the process of S705 controlling the throttle valve 300 to be opened for the eighteenth period every seventeenth period, if it is detected that the rotation speed of the motor is continuously increased in the fifth period, the throttle valve 300 is controlled to be opened for the twentieth period every nineteenth period. Wherein a ratio of the nineteenth time period to the twentieth time period > a ratio of the seventeenth time period to the eighteenth time period.

S707, in the step of S705 controlling the throttle valve 300 to be opened for the eighteenth period every seventeenth period, if it is detected that the rotation speed of the motor is continuously decreased for the sixth period, the throttle valve 300 is controlled to be opened for the twenty second period every twenty first period. Wherein, the ratio of the seventeenth duration to the eighteenth duration is greater than the ratio of the twenty-first duration to the twenty-second duration is greater than the ratio of the seventh duration to the eighth duration.

S708, if the detected rotation speed of the motor is less than a first smaller rotation speed threshold, the throttle valve 300 is opened continuously.

S709, if it is detected that the rotation speed of the motor 5 is greater than the second rotation speed threshold, removing the active intervention of the controller 35 on the throttle valve 300, and allowing the discharge valve 9 to operate according to its original characteristic; wherein the second rotation speed threshold is not less than the first rotation speed threshold in S708. "letting the discharge valve 9 operate in its own original characteristic" generally includes two cases:

1) The throttle valve 300 is opened or closed according to the physical pressure. In this case, the controller 35 completely removes the intervention on the operating state of the throttle valve 300, and allows the throttle valve 300 to be automatically opened or closed by directly sensing the pressures on both sides thereof. That is, controller 35 does not act at all on throttle valve 300, leaving throttle valve 300 to open or close by means of only non-electrical mechanical force. This is suitable for application to the above-described "i" type of electronically controlled throttle valve.

2) Throttle valve 300 opens or closes according to an otherwise electrical control strategy. In this case, the controller 35 need only remove the active intervention described above with respect to the throttle valve 300 and employ a conventional strategy to control the opening and closing of the throttle valve 300. "controlling the opening and closing of throttle valve 300 using conventional strategies" is typically: controller 35 controls throttle valve 300 to open or close based primarily on the fluid pressure at throttle valve 300. This is suitably applied to the above-described "ii" type of electronically controlled throttle valve.

In other embodiments, the above-mentioned policies of S701-S707 may be omitted, and the air conditioning system is simply controlled by using the policies of S708 and S709, which are as follows:

that is, if it is determined that the rotation speed of the motor 5 is less than the first rotation speed threshold, the throttle valve 300 is controlled to be continuously opened to continuously cut off the work load of the diaphragm. Removing the active intervention of the controller 35 on the throttle valve 300 to continue to switch in the working load of the diaphragm 3 if it is determined that the speed of rotation of the motor is greater than the second speed threshold; and the second rotating speed threshold value is not less than the first rotating speed threshold value. In such a control mode, the second rotational speed threshold may generally be equal to the first rotational speed threshold.

In the simplified control strategy, when the motor has a low rotation speed and insufficient output power, the throttle valve 300 is kept in an open state to reduce the load of the compressor, increase the rotation speed of the motor, and store energy for the flywheel. Under the condition that the rotating speed of the motor is high enough and the energy of the flywheel is large enough, the throttle valve 300 is restored to the original state, and the air conditioning system works normally. The disadvantages are that: the rotation speed of the motor in the compressor 100 may be very unstable.

Those skilled in the art will understand that: the obtaining of the rotation speed information of the motor 5 in the diaphragm compressor is one of the conditions that the above-mentioned S701-S709 control method can be smoothly implemented, for example, the rotation speed of the motor 5 can be obtained in real time during the operation of the motor 5, and once the rotation speed of the motor is determined to satisfy a certain preset condition, the throttle valve 300 is controlled to perform a corresponding response action, such as alternately opening and closing the throttle valve 300 at a first frequency when the rotation speed of the motor is determined to be in a set first rotation speed interval.

Example twenty two: air conditioning system

Inspired by the eighth embodiment and the ninth embodiment, the present embodiment provides another air conditioning system capable of intermittently performing high-power work. As shown in fig. 57 and with reference to fig. 58, the air conditioning system is provided with an electrically controlled valve 38 connected between the condenser 200 and the evaporator 400 in parallel with the throttle valve 300. The electrically controlled valve 38 is communicatively connected to the controller 35 which is communicatively connected to the motor speed sensor 34, so that the operating state of the electrically controlled valve 38 can be controlled by the controller 35 in accordance with the motor speed. The compressor 100 has the same structure as that of the twenty-one embodiment.

If the electrically controlled valve 38 is kept closed, the air conditioning system operates in the same manner as a conventional air conditioning system. At this time, as long as the diaphragm compressor 100 has sufficient energy, the high-pressure fluid on the upstream side of the throttle valve 300 can be pressure-fed to the downstream side of the throttle valve 300. However, in some cases, the power consumed by the compressor 100 to compress the working fluid is significant, such as when carbon dioxide is used as the refrigerant. Therefore, when the rotation speed of the motor 5 is low and the energy stored in the flywheel 24 is insufficient, the compressor 100 cannot work normally.

If the electronic control valve 38 is kept in the open state, which corresponds to "short-circuiting" the throttle valve 300 and removing it from the circuit, the electronic control valve 38 having no throttle expansion function allows the working fluid (refrigerant) to easily flow between the condenser 200 and the evaporator 400, and the working load of the compressor 100 is small. In this case, of course, the air conditioning system has no cooling and heating effects.

Thus, the present embodiment provides the following control method of the air conditioning system of this modification, and the detailed control method thereof can be referred to embodiment seven and embodiment eight.

S801, during the operation of the motor of the diaphragm compressor 100, if the rotation speed of the motor is detected to be in the first rotation speed interval, controlling the electronically controlled valve 38 to open and close alternately at the first frequency.

In general, the rated rotation speed of the driving motor in the compressor 100 is in the first rotation speed range.

Alternatively, if it is detected that the speed of the electric motor is in a second speed interval, which does not intersect the first speed interval and is smaller than the first speed interval, the electrically controlled valve 38 is alternately opened and closed at a second frequency different from the first frequency. The ratio of the opening duration to the closing duration of the electrically controlled valve 38 in each cycle of the second frequency ≠ the ratio of the opening duration to the closing duration of the electrically controlled valve 38 in each cycle of the first frequency.

S802, in the process of S801 controlling the electronically controlled valve 38 to open and close alternately at the first frequency, if it is detected that the rotation speed of the motor is continuously reduced for the first time period, controlling the electronically controlled valve 38 to open and close alternately at the third frequency; wherein the ratio of the closing duration to the opening duration of the electrically controlled valve 38 in each cycle of the third frequency < the ratio of the closing duration to the opening duration of the electrically controlled valve 38 in each cycle of the first frequency.

And S803, in the process of controlling the electronic control valve 38 to be opened and closed alternately at the third frequency in S802, if the rotation speed of the motor is detected to be continuously reduced in the second time period, controlling the electronic control valve 38 to be opened and closed alternately at the fourth frequency. Wherein the ratio of the closing duration to the opening duration of the electronically controlled valve 38 in each cycle of the fourth frequency < the ratio of the closing duration to the opening duration of the electronically controlled valve 38 in each cycle of the third frequency.

S804, in the process of controlling the electronic control valve 38 to alternately open and close at the third frequency in S802, if it is detected that the rotation speed of the motor 5 continuously increases in the third period, the electronic control valve 38 is controlled to alternately open and close at the fifth frequency. Wherein the ratio of the closing duration to the opening duration of the electronically controlled valve 38 in each cycle of the first frequency > the ratio of the closing duration to the opening duration of the electronically controlled valve 38 in each cycle of the fifth frequency > the ratio of the closing duration to the opening duration of the electronically controlled valve 38 in each cycle of the third frequency.

S805, in the process of controlling the electronic control valve 38 to alternately open and close at the first frequency at S801, if it is detected that the rotation speed of the motor continuously increases for a fourth time period, controlling the electronic control valve 38 to alternately open and close at a sixth frequency; wherein the ratio of the closing duration to the opening duration of the electronically controlled valve 38 in each cycle of the sixth frequency > the ratio of the closing duration to the opening duration of the electronically controlled valve 38 in each cycle of the first frequency.

S806, in the process of controlling the electronic control valve 38 to be alternately opened and closed at the sixth frequency in S805, if it is detected that the rotation speed of the motor is continuously increased for the fifth period of time, controlling the electronic control valve 38 to be alternately opened and closed at the seventh frequency. Wherein the ratio of the closing period to the opening period of the electronically controlled valve 38 in each cycle at the seventh frequency > the ratio of the closing period to the opening period of the electronically controlled valve 38 in each cycle at the sixth frequency.

S807, in the process of controlling the electronic control valve 38 to be alternately opened and closed at the sixth frequency in S805, if it is detected that the rotation speed of the motor is continuously decreased for the sixth period, the electronic control valve 38 is controlled to be alternately opened and closed at the eighth frequency. Wherein, the ratio of the closing duration to the opening duration of the electronic control valve 38 in each cycle of the sixth frequency > the ratio of the closing duration to the opening duration of the electronic control valve 38 in each cycle of the eighth frequency > the ratio of the closing duration to the opening duration of the electronic control valve 38 in each cycle of the first frequency.

S808, if the rotating speed of the motor 5 is detected to be less than a first smaller rotating speed threshold value, controlling the electronic control valve 38 to be continuously opened; wherein, the first rotating speed threshold value is smaller than the lower limit of the first rotating speed interval in S801.

And S809, if the rotation speed of the motor 5 is detected to be greater than the second rotation speed threshold value, controlling the electronic control valve 38 to be continuously closed. The second rotation speed threshold value is not less than the first rotation speed threshold value in S808, and is generally greater than the upper limit value of the first rotation speed section in S801.

The electrically controlled valve 38 is preferably a normally closed valve or a normally open valve for simplicity of control.

The controller 35 in fig. 57 and fig. 58 respectively includes a memory, a processor connected to the memory, and computer instructions stored in the memory and executable by the processor, and when the computer instructions are executed by the processor, the above control method in the present embodiment can be respectively implemented.

Example twenty three: air conditioning system

As shown in fig. 59 and 60, the air conditioning system of the present embodiment also includes a compressor 100, a condenser 200, a throttle valve 300, and an evaporator 400, which are fluidly connected in this order and constitute a closed circuit. The pressure sensor 39 is used to detect the internal pressure of the condenser 200, referred to simply as the condenser pressure.

In this embodiment, the compressor 100 is a diaphragm compressor, and the structure thereof is substantially the same as that of the first embodiment, and can be seen from fig. 2, and the difference between the two embodiments is only: the compressor of the present embodiment is not provided with a motor rotation speed sensor, and the controller 35 communicatively connected to the valve 11 is also communicatively connected to the above-described pressure sensor 39, thereby enabling the valve 11 to be opened or closed according to the pressure of the condenser 200.

The embodiment proposes a control method for the air conditioning system, which comprises the following steps: during operation of the motor of the diaphragm compressor 100, if it is detected that the pressure of the condenser 200 is in the first pressure interval, the valve 11 in the diaphragm compressor is alternately opened and closed at the first frequency, i.e. the drive path of the flywheel 24 in the compressor 100 to the diaphragm 3 in the compressor 100 is alternately disconnected and engaged at the first frequency.

The greater the pressure of the condenser 200, the greater the opening pressure of the discharge valve 9 in the compressor 100, and the greater the load force that the diaphragm 3 needs to overcome. The smaller the condenser 200 pressure, the smaller the opening pressure of the discharge valve 9 in the compressor 100, and the smaller the load force that the diaphragm 3 needs to overcome. Therefore, the upper limit of the first pressure interval should not be too large, otherwise the rotational speed of the motor 5 and the flywheel 24 may drop suddenly due to insufficient output power of the compressor motor 5, and the compressor 100 is overloaded severely. The lower limit of the first pressure interval is not required to be small, otherwise, the energy waste is increased, and the refrigerating or heating efficiency of the air conditioner is reduced. When the pressure of the condenser 200 is in the first pressure interval, which is neither too large nor too small, the valve 11 of the diaphragm compressor 100 connected between the power chamber 2 and the power fluid storage chamber 10 is controlled to alternately open and close at a set first frequency, and if the energy supplied by the compressor motor 5, which is continuously operated, is balanced with the energy consumption of the compressor diaphragm 3, which is operated only for a part of the time period, during each cycle time of the first frequency, the diaphragm compressor 100 can be continuously and stably operated and can intermittently perform high-power work.

In further embodiments, it is also possible to open and close the valve 11 on the diaphragm compressor alternately at a second frequency, when it is detected that the pressure of the condenser 200 is in a second pressure interval that does not intersect the above-mentioned first pressure interval; wherein, the lower limit of the second pressure interval is greater than the upper limit of the first pressure interval, the ratio of the closing time length to the opening time length of the valve 11 in each period of the second frequency is less than the ratio of the closing time length to the opening time length of the valve 11 in each period of the first frequency, namely, the ratio of the engaging time length to the disengaging time length of the driving path (the driving path from the flywheel to the diaphragm in the diaphragm compressor) in each period of the second frequency is less than the ratio of the engaging time length to the disengaging time length of the driving path in each period of the first frequency.

In other embodiments, if it is detected that the pressure of condenser 200 is greater than the first pressure threshold, valve 11 in the diaphragm compressor is continuously opened, thereby maintaining the drive path of flywheel 24 to diaphragm 3 in the disconnected state; wherein the first rotational speed threshold is greater than an upper limit of the first pressure interval.

When the pressure of the condenser 200 is greater than a value greater than the upper limit of the first pressure interval, it indicates that the load of the compressor is too high, and if the compressor 100 is made to perform intermittent work, the output power of the compressor motor 5 may be insufficient, which may result in a sudden drop in the rotation speeds of the motor 5 and the flywheel 24. Thus, at this time, the valve 11 is continuously opened to keep the drive path of the flywheel 24 to the diaphragm 3 in the off state, and the air conditioning system stops cooling or heating. If the rotational speed of the electric motor has not yet reached the setpoint rotational speed, flywheel 24 can be charged continuously during the period in which valve 11 is continuously open.

In other embodiments, if it is detected that the pressure of the condenser 200 is less than the second pressure threshold, the valve 11 in the diaphragm compressor is continuously closed, thus maintaining the drive path of the flywheel 24 towards the diaphragm 3 in the engaged state; wherein the second rotational speed threshold is smaller than the lower limit of the first pressure interval.

When the pressure of the condenser 200 is smaller than a value smaller than the lower limit of the first pressure interval, it means that the load of the compressor is small, and if the compressor 100 is also intermittently operated, energy is wasted. Thus, at this time, the valve 11 is continuously closed to maintain the drive path of the flywheel 24 to the diaphragm 3 in the engaged state, and the air conditioning system can continue to perform cooling or heating.

Those skilled in the art will understand that: the obtaining of the information about the internal pressure of the condenser 200 is one of the conditions for implementing the above control method, for example, the pressure of the condenser 200 may be obtained in real time during the operation of the compressor motor, and once the condenser pressure is determined to satisfy a certain preset condition, the control valve 11 may perform corresponding response actions, such as alternately opening and closing the valve 11 at a first frequency when the condenser pressure is determined to be in a set first pressure interval, and continuously opening the valve 11 when the condenser pressure is determined to be greater than a set first pressure threshold.

It is also understood that if the diaphragm compressor 100 of the present embodiment is replaced with the structure of the sixth, seventh, tenth or eleventh embodiment, the air conditioning system can be controlled by a method similar to the aforementioned control method. Such as engagement or disengagement of the clutch 37 based on pressure control of the condenser 200, such as opening or closing an electronically controlled valve in parallel with the suction valve based on pressure control of the condenser 200, or actively opening continuously or intermittently, such as opening the suction valve in an electronically controlled one-way valve configuration based on pressure control of the condenser 200. The specific schemes can refer to the sixth embodiment, the seventh embodiment and the tenth embodiment and combine with twenty-third embodiment, which are not repeated herein.

The above are exemplary embodiments of the present application only, and are not intended to limit the scope of the present application, which is defined by the appended claims.

Claims

1. A diaphragm pump or a diaphragm compressor comprising:

a membrane sheet (3), and

a motor (5) for providing a driving force to the diaphragm;

characterized in that the drive path of the motor (5) to the diaphragm (3) comprises:

a flywheel (24), and

and a clutch (37) provided on the downstream side of the flywheel in transmission.

2. The diaphragm pump or diaphragm compressor according to claim 1, wherein the clutch (37) is an electronically controlled clutch in communicative connection with a controller (35), the controller (35) being configured to: -controlling the clutch (37) to be disengaged or engaged.

3. A diaphragm pump or a diaphragm compressor according to claim 2, further comprising a motor speed sensor (34) for detecting the speed of the motor (5) and being in communication with the controller (35), the controller (35) being configured to: the rotational speed of the motor (5) is acquired from the motor rotational speed sensor (34), and the clutch (37) is controlled to be disengaged or engaged based on the rotational speed.

4. A diaphragm pump or a diaphragm compressor according to claim 1, characterized in that the drive path of the motor (5) to the diaphragm (3) further comprises a speed reducer (12) provided on the drive downstream side of the flywheel (24).

5. A control method to be applied to a diaphragm pump or a diaphragm compressor according to any of claims 1 to 4, characterized in that the control method comprises:

-controlling the clutch (37) to alternately disengage and engage at a first frequency during operation of the electric machine (5).

6. The control method according to claim 5, characterized in that, before said controlling said clutch (37) to alternately disengage and engage at a first frequency, said control method further comprises:

determining that the rotating speed of the motor (5) is in a first rotating speed interval; wherein the rated rotating speed of the motor (5) is in the first rotating speed interval.

7. The control method according to claim 5, characterized in that, in said controlling the clutch (37) to alternately disengage and engage at a first frequency, the control method further comprises:

if it is determined that the rotational speed of the electric machine (5) is continuously reduced for the first period of time, alternately disengaging and engaging the clutch (37) at a third frequency; wherein the ratio of the engagement duration to the disengagement duration of the clutch (37) in each cycle of the third frequency < the ratio of the engagement duration to the disengagement duration of the clutch (37) in each cycle of the first frequency.

8. The control method according to claim 6, characterized by further comprising:

controlling the clutch (37) to be continuously disengaged if it is determined that the rotational speed of the electric machine (5) is less than a first rotational speed threshold; wherein the first rotation speed threshold is smaller than a lower limit of the first rotation speed interval.

9. The control method according to claim 5 or 8, characterized by further comprising:

-controlling the clutch (37) to continue to engage if it is determined that the speed of the electric machine (5) is greater than a second speed threshold; wherein the second rotation speed threshold is greater than an upper limit of the first rotation speed interval.

10. A control method to be applied to a diaphragm pump or a diaphragm compressor according to any of claims 1 to 4, characterized in that the control method comprises:

acquiring the rotating speed of the motor (5) in real time;

-controlling the clutch (37) to be continuously disengaged if it is determined that the rotation speed is less than a first rotation speed threshold;

controlling the clutch (37) to continue to engage if it is determined that the rotational speed is greater than a second rotational speed threshold; wherein the second rotational speed threshold is not less than the first rotational speed threshold.