CN114623111B - Pressure and flow controllable hydraulic system of garbage compression station and control method thereof - Google Patents
Pressure and flow controllable hydraulic system of garbage compression station and control method thereof Download PDFInfo
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- CN114623111B CN114623111B CN202210294966.5A CN202210294966A CN114623111B CN 114623111 B CN114623111 B CN 114623111B CN 202210294966 A CN202210294966 A CN 202210294966A CN 114623111 B CN114623111 B CN 114623111B
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- 230000006835 compression Effects 0.000 title claims abstract description 42
- 238000007906 compression Methods 0.000 title claims abstract description 42
- 238000000034 method Methods 0.000 title claims abstract description 27
- 239000010720 hydraulic oil Substances 0.000 claims abstract description 34
- 239000003921 oil Substances 0.000 claims description 154
- 230000009699 differential effect Effects 0.000 claims description 4
- 239000002699 waste material Substances 0.000 claims 1
- 230000007246 mechanism Effects 0.000 description 17
- 238000010586 diagram Methods 0.000 description 2
- 230000005611 electricity Effects 0.000 description 2
- 238000012986 modification Methods 0.000 description 2
- 230000004048 modification Effects 0.000 description 2
- 230000007935 neutral effect Effects 0.000 description 2
- 230000002159 abnormal effect Effects 0.000 description 1
- 230000009286 beneficial effect Effects 0.000 description 1
- 125000004122 cyclic group Chemical group 0.000 description 1
- 230000007547 defect Effects 0.000 description 1
- 230000010354 integration Effects 0.000 description 1
Classifications
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
- F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
- F15B11/00—Servomotor systems without provision for follow-up action; Circuits therefor
- F15B11/02—Systems essentially incorporating special features for controlling the speed or actuating force of an output member
- F15B11/022—Systems essentially incorporating special features for controlling the speed or actuating force of an output member in which a rapid approach stroke is followed by a slower, high-force working stroke
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
- F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
- F15B11/00—Servomotor systems without provision for follow-up action; Circuits therefor
- F15B11/02—Systems essentially incorporating special features for controlling the speed or actuating force of an output member
- F15B11/028—Systems essentially incorporating special features for controlling the speed or actuating force of an output member for controlling the actuating force
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
- F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
- F15B11/00—Servomotor systems without provision for follow-up action; Circuits therefor
- F15B11/02—Systems essentially incorporating special features for controlling the speed or actuating force of an output member
- F15B11/04—Systems essentially incorporating special features for controlling the speed or actuating force of an output member for controlling the speed
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
- F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
- F15B11/00—Servomotor systems without provision for follow-up action; Circuits therefor
- F15B11/08—Servomotor systems without provision for follow-up action; Circuits therefor with only one servomotor
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
- F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
- F15B13/00—Details of servomotor systems ; Valves for servomotor systems
- F15B13/02—Fluid distribution or supply devices characterised by their adaptation to the control of servomotors
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
- F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
- F15B13/00—Details of servomotor systems ; Valves for servomotor systems
- F15B2013/002—Modular valves, i.e. consisting of an assembly of interchangeable components
- F15B2013/004—Cartridge valves
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
- F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
- F15B13/00—Details of servomotor systems ; Valves for servomotor systems
- F15B13/02—Fluid distribution or supply devices characterised by their adaptation to the control of servomotors
- F15B13/04—Fluid distribution or supply devices characterised by their adaptation to the control of servomotors for use with a single servomotor
- F15B13/044—Fluid distribution or supply devices characterised by their adaptation to the control of servomotors for use with a single servomotor operated by electrically-controlled means, e.g. solenoids, torque-motors
- F15B2013/0448—Actuation by solenoid and permanent magnet
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
- F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
- F15B2211/00—Circuits for servomotor systems
- F15B2211/20—Fluid pressure source, e.g. accumulator or variable axial piston pump
- F15B2211/205—Systems with pumps
- F15B2211/20576—Systems with pumps with multiple pumps
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
- F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
- F15B2211/00—Circuits for servomotor systems
- F15B2211/30—Directional control
- F15B2211/315—Directional control characterised by the connections of the valve or valves in the circuit
- F15B2211/3157—Directional control characterised by the connections of the valve or valves in the circuit being connected to a pressure source, an output member and a return line
- F15B2211/31582—Directional control characterised by the connections of the valve or valves in the circuit being connected to a pressure source, an output member and a return line having multiple pressure sources and a single output member
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
- F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
- F15B2211/00—Circuits for servomotor systems
- F15B2211/40—Flow control
- F15B2211/415—Flow control characterised by the connections of the flow control means in the circuit
- F15B2211/4159—Flow control characterised by the connections of the flow control means in the circuit being connected to a pressure source, an output member and a return line
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- Engineering & Computer Science (AREA)
- Physics & Mathematics (AREA)
- Fluid Mechanics (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Fluid-Pressure Circuits (AREA)
Abstract
The invention discloses a hydraulic system of a garbage compression station with controllable pressure and flow and a control method thereof, wherein the hydraulic system comprises a main valve group, a control valve group, an auxiliary action valve group, a first hydraulic pump, a second hydraulic pump, a hydraulic oil tank and a hydraulic oil cylinder; the outlet pressure of the first hydraulic pump acts on each logic valve in the main valve group after being reduced by the reducing valve, so as to control the switching of the working positions of each hydraulic control reversing valve in the main valve group, and the hydraulic oil cylinder is controlled in an action mode; the electromagnetic reversing valve in the auxiliary action valve group is used for controlling the output flow of the second hydraulic pump to be switched in between the main valve group system and the auxiliary action hydraulic system through power supply and power failure, so as to control the action speed of the hydraulic cylinder; the first hydraulic pump selects overflow valves with different set pressures to be combined into the system through control switching of working positions of the electromagnetic directional valves in the control valve group so as to limit the highest working pressure of the system, and multistage pressure switching is realized. The invention can improve the system universality and reduce the variety and the number of valve groups.
Description
Technical Field
The invention relates to a hydraulic system of a garbage compression station with controllable pressure and flow and a control method thereof, belonging to the technical field of hydraulic control.
Background
At present, garbage compression stations are widely used in garbage collection and transportation processes. The hydraulic system is realized in a form of a hydraulic pump station, the control valve group is an integrated valve group, and different valve groups are matched for realizing different pressure speed control of the compression mechanism, so that the variety and the number of the valve groups are various, and the unified shape of products is not facilitated; meanwhile, matched systems are generally required to be respectively designed on different series of garbage compression stations, and the universality of the system is not high.
Disclosure of Invention
The invention aims to overcome the defects in the prior art, and provides a hydraulic system of a garbage compression station with controllable pressure and flow and a control method thereof, which meet the pressure and speed control requirements of compression mechanisms of different series of garbage compression stations, improve the universality of the system and reduce the types and the number of valve groups.
In order to achieve the above purpose, the invention adopts the following technical scheme:
The invention provides a hydraulic system of a garbage compression station with controllable pressure and flow, which comprises a main valve group, a control valve group, an auxiliary action valve group, a first hydraulic pump, a second hydraulic pump, a hydraulic oil tank and a hydraulic oil cylinder; the outlet pressure of the first hydraulic pump acts on each logic valve in the main valve group after being reduced by the reducing valve, so as to control the switching of the working positions of each hydraulic control reversing valve in the main valve group, and the hydraulic oil cylinder is controlled in an action mode; the electromagnetic reversing valve in the auxiliary action valve group is used for controlling the output flow of the second hydraulic pump to be switched in between the main valve group system and the auxiliary action hydraulic system through power supply and power failure, so as to control the action speed of the hydraulic cylinder; the first hydraulic pump selects overflow valves with different set pressures to be combined into the system through control switching of working positions of the electromagnetic directional valves in the control valve group so as to limit the highest working pressure of the system, and multistage pressure switching is realized.
Further, the main valve group: the oil inlet is communicated with a first hydraulic pump, the first working oil port I and the first working oil port II are communicated with a rodless cavity of the hydraulic oil cylinder, the second working oil port is communicated with a rod cavity of the hydraulic oil cylinder, and the oil return port I and the oil return port II are communicated with the hydraulic oil tank; and the oil inlet of the auxiliary action valve group is communicated with the second hydraulic pump.
Further, the main valve group includes first hydraulically controlled reversing valve, second hydraulically controlled reversing valve, first logic valve, third logic valve, second logic valve and two-way cartridge valve, wherein:
the first pilot-operated directional valve is a three-position four-way directional valve, the middle slide valve can be O-shaped, and the first pilot-operated directional valve is as follows: the oil inlet is communicated with the first hydraulic pump, the oil return port is communicated with the hydraulic oil tank, and the first working oil port and the second working oil port are respectively communicated with the oil inlet and the oil return port of the second hydraulic control reversing valve;
The first logic valve, the second logic valve and the third logic valve are two-position three-way reversing valves, a second oil port of the first logic valve is communicated with the right end of the first hydraulic reversing valve, a second oil port of the third logic valve is communicated with the left end of the first hydraulic reversing valve, a second oil port of the second logic valve is communicated with the right end of the second hydraulic reversing valve, the first logic valve and the third logic valve control reversing actions of the first hydraulic reversing valve, the second logic valve control reversing actions of the second hydraulic reversing valve, the second hydraulic reversing valve is a two-position four-way reversing valve, a normal-position slide valve can be P-shaped, a first working oil port of the second hydraulic reversing valve is communicated with a rodless cavity of a hydraulic cylinder, a second working oil port of the second hydraulic reversing valve is communicated with the rod cavity of the hydraulic cylinder, and the second hydraulic reversing valve controls differential actions of the hydraulic cylinder.
Further, the control valve group comprises a first electromagnetic directional valve, a first overflow valve, a second overflow valve and a pressure reducing valve, wherein:
The first electromagnetic reversing valve is a three-position four-way reversing valve, the middle-position slide valve can be H-shaped, the oil return port of the first electromagnetic reversing valve is communicated with the oil return ports of the first overflow valve, the oil return port of the second overflow valve and the oil drain port of the pressure reducing valve, and is communicated with the first oil port of the first logic valve, the second logic valve and the third logic valve, and the right end of the second hydraulic reversing valve, and the second working oil port is plugged;
the oil inlet of the pressure reducing valve is communicated with the first hydraulic pump, and the oil outlet of the pressure reducing valve is communicated with the third oil ports of the first logic valve, the second logic valve and the third logic valve;
The oil return port of the first overflow valve, the oil return port of the second overflow valve and the oil drain port of the pressure reducing valve are communicated with the first oil port of the first logic valve, the first oil port of the third logic valve and the first oil port of the second logic valve.
Further, the two-way cartridge valve: the first oil port is communicated with the first hydraulic pump and the oil inlet of the pressure reducing valve, and the control oil port is communicated with the second overflow valve oil inlet and the first electromagnetic directional valve oil inlet.
Further, the auxiliary action valve group comprises a second electromagnetic reversing valve, a third overflow valve and a one-way valve, wherein:
the second electromagnetic reversing valve is a three-position four-way reversing valve, the middle slide valve can be H-shaped, the oil inlet of the second electromagnetic reversing valve is communicated with the oil outlet of the second hydraulic pump, and the oil return port is communicated with the hydraulic oil tank; the second electromagnetic reversing valve is connected with the third overflow valve in parallel; the second working oil port of the second electromagnetic directional valve is connected with an auxiliary action system, and the first working oil port is communicated with the oil inlet of the one-way valve; and the oil outlet of the one-way valve is communicated with the oil inlet of the first hydraulic control reversing valve.
Further, the set pressure of the first overflow valve is lower than the set pressure of the second overflow valve, the set pressure of the third overflow valve is lower than the set pressure of the first overflow valve, and the set pressure of the pressure reducing valve is set according to reversing requirements of the first hydraulic control reversing valve and the second hydraulic control reversing valve.
The invention provides a control method of a hydraulic system of a garbage compression station with controllable pressure and flow, which is used for controlling the hydraulic system of the garbage compression station with controllable pressure and flow, and comprises a hydraulic cylinder action control method, a hydraulic cylinder action speed control method and a multistage pressure switching control method, wherein:
the hydraulic cylinder action control method comprises the following steps:
the outlet pressure of the first hydraulic pump is reduced by the pressure reducing valve and then acts on the first logic valve, the second logic valve and the third logic valve; the first logic valve, the second logic valve and the third logic valve working positions are switched by controlling the electromagnet of the first logic valve, the electromagnet of the second logic valve and the electromagnet of the third logic valve to be powered on and powered off, so that the switching of the first hydraulic control reversing valve and the working positions of the second hydraulic control reversing valve is controlled, and the extending, retracting and differential actions of the hydraulic oil cylinder are realized;
the hydraulic cylinder action speed control method comprises the following steps:
The differential motion of the hydraulic oil cylinder is realized by controlling the switching of the working position of the second hydraulic control valve; controlling the output flow of the second hydraulic pump to be connected to a main valve group system or an auxiliary action hydraulic system by controlling the electromagnet of the second electromagnetic directional valve to be powered on and powered off, so as to control the action speed of the hydraulic cylinder;
The multistage pressure switching control method comprises the following steps:
The first hydraulic pump output oil is communicated with the oil inlet of the first electromagnetic directional valve through the control oil port of the two-way cartridge valve, the electromagnet of the first electromagnetic directional valve is controlled to be electrified and de-electrified, the working position of the first electromagnetic directional valve is controlled to switch, the first overflow valve and the second overflow valve are selected to be integrated into the system, the highest working pressure of the system is limited, and multistage pressure switching is realized.
Compared with the prior art, the invention has the beneficial effects that:
The hydraulic system provided by the invention can be applied to corresponding hydraulic systems as a whole, and can be also used for configuring different valve groups according to different working condition demands; in addition, the hydraulic system provided by the invention can realize multi-stage pressure control and meet the working conditions of different pressure demands; secondly, the hydraulic system provided by the invention can realize the speed switching of the actuating mechanism, and meet the speed requirements of different working conditions; finally, the invention can match single and double pump systems according to the requirements of the host.
Drawings
Fig. 1 is a schematic diagram of a hydraulic system according to a first embodiment of the present invention.
In the figure: 1. the hydraulic oil tank, 2, a first hydraulic pump, 3, a first electromagnetic directional valve, 4, a first overflow valve, 5, a second overflow valve, 6, a two-way cartridge valve, 7, a first hydraulic directional valve, 8, a first logic valve, 9, a second logic valve, 10, a second hydraulic directional valve, 11, a hydraulic cylinder, 12, a third logic valve, 13, a one-way valve, 14, a second electromagnetic directional valve, 15, a third overflow valve, 16, a pressure reducing valve, 17 and a second hydraulic pump.
Detailed Description
The invention is further described below with reference to the accompanying drawings. The following examples are only for more clearly illustrating the technical aspects of the present invention, and are not intended to limit the scope of the present invention.
Embodiment one:
A hydraulic system of a garbage compression station with controllable pressure and flow,
The principle schematic diagram of the hydraulic system of the invention is combined, only the preferred embodiment of the invention is described in detail, and the protection scope of the invention is not limited by the detailed description.
As shown in fig. 1, the invention provides a hydraulic system of a garbage compression station with controllable pressure and flow, which comprises a hydraulic oil tank 1, a first hydraulic pump 2, a first electromagnetic directional valve 3, a first overflow valve 4, a second overflow valve 5, a two-way cartridge valve 6, a first hydraulic directional valve 8, a first logic valve 7, a second logic valve 9, a second hydraulic directional valve 10, a hydraulic oil cylinder 11, a third logic valve 12, a second electromagnetic directional valve 14, a third overflow valve 15, a pressure reducing valve 16 and a second hydraulic pump 17.
The first hydraulic control reversing valve 7 is a three-position four-way reversing valve, and the middle slide valve can be O-shaped; the second hydraulic control reversing valve 10 is a two-position four-way reversing valve, and the normal-position slide valve can be a P-type valve; the first electromagnetic directional valve 3 is a three-position four-way directional valve, and the middle slide valve function is H-shaped; the second electromagnetic directional valve 14 is a three-position four-way directional valve, and the normal-position slide valve can be H-shaped; the first logic valve 8, the second logic valve 9 and the third logic valve 12 are two-position three-way reversing valves. The first logic valve 8 and the third logic valve 12 control the reversing of the first hydraulic control reversing valve 7, the second logic valve 9 controls the reversing of the second hydraulic control reversing valve 10, and the second hydraulic control reversing valve 10 controls the differential motion of the hydraulic cylinder 11.
An oil inlet P7 of the first pilot operated directional valve 7 is communicated with the first hydraulic pump 2, an oil return port T7 of the first pilot operated directional valve 7 is communicated with the hydraulic oil tank 1, a first working oil port A7 of the first pilot operated directional valve 7 is communicated with an oil inlet P10 of the second pilot operated directional valve 10, and a second working oil port B7 of the first pilot operated directional valve 7 is communicated with an oil return port T10 of the second pilot operated directional valve 10; the first working oil port A10 of the second hydraulic control reversing valve 10 is communicated with a rodless cavity of the hydraulic cylinder 11, and the second working oil port B10 of the second hydraulic control reversing valve 10 is communicated with a rod cavity of the hydraulic cylinder 11; the second oil port 82 of the first logic valve 8 is communicated with the right end of the first hydraulic control reversing valve 7; the second oil port 122 of the third logic valve 12 is communicated with the left end of the first hydraulic control reversing valve 7; the second oil port 92 of the second logic valve 9 is communicated with the right end of the second hydraulic control reversing valve 10.
The first oil port 61 of the two-way cartridge valve 6 is communicated with the first hydraulic pump 2 and the oil inlet 161 of the pressure reducing valve 16, the second oil port 62 of the two-way cartridge valve 6 is communicated with the hydraulic oil tank 1, and the control oil port X of the two-way cartridge valve 6 is communicated with the oil inlet P3 of the first electromagnetic directional valve 3 and the oil inlet 51 of the second overflow valve 5; the first working oil port A3 and the oil return port T3 of the first electromagnetic directional valve 3 are communicated with the oil inlet 41 of the first overflow valve 4, the oil return port T3 of the first electromagnetic directional valve 3 is communicated with the oil return port 52 of the second overflow valve 5 and the oil discharge port 163 of the pressure reducing valve 16, and is communicated with the right ends of the first oil port of the first logic valve 8, the second logic valve 9 and the third logic valve 12 and the right end of the second hydraulic directional valve 10, and the second working oil port B3 of the first electromagnetic directional valve 3 is blocked; the oil inlet 161 of the pressure reducing valve 16 is communicated with the first hydraulic pump 2; the oil return port 42 of the first overflow valve 4, the oil return port 52 of the second overflow valve 5 and the oil drain port 163 of the pressure reducing valve 16 are communicated with the first oil port 81 of the first logic valve 8, the first oil port 121 of the third logic valve 12 and the first oil port 91 of the second logic valve 9, and the oil outlet 162 of the pressure reducing valve 16 is communicated with the third oil port 123 of the third logic valve 12, the third oil port 83 of the first logic valve 8, the third oil port 93 of the second logic valve 9 and the left end of the second hydraulic control reversing valve 10.
An oil inlet P14 of the second electromagnetic directional valve 14 is communicated with the second hydraulic pump 17, an oil return port T41 of the second electromagnetic directional valve 14 is communicated with the hydraulic oil tank 1, the second electromagnetic directional valve 14 is connected with the third overflow valve 15 in parallel, a first working oil port A14 of the second electromagnetic directional valve 14 is communicated with an oil inlet 131 of the one-way valve 13, and a second working oil port B14 of the second electromagnetic directional valve 14 is communicated with an auxiliary action loop; the oil outlet 132 of the one-way valve 13 is communicated with the oil inlet P7 of the first hydraulic control reversing valve 7.
The set pressure of the first relief valve 4 is lower than the set pressure of the second relief valve 5, and the set pressure of the third relief valve 15 is lower than the set pressure of the first relief valve 4; the set pressure of the pressure reducing valve 16 is set according to the reversing demands of the first hydraulic control reversing valve 7 and the second hydraulic control reversing valve 10.
In the embodiment, the working process of the hydraulic system comprises the following steps:
Cyclic compression stage:
Fast forward of the compression mechanism: the first hydraulic pump 2 and the second hydraulic pump 17 work, the electromagnet YV5 of the first logic valve 8 and the electromagnet YV7 of the second logic valve 9 are powered, part of oil output by the first hydraulic pump 2 enters the right end of the first hydraulic control reversing valve 7 and the right end of the second hydraulic control reversing valve 10 respectively through the pressure reducing valve 16, the working position of the first logic valve 8 and the working position of the second logic valve 9, and the first hydraulic control reversing valve 7 and the second hydraulic control reversing valve 10 are reversed to the right position; the first electromagnet YV3 of the second electromagnetic directional valve 14 is electrified, and the second electromagnetic directional valve 14 is switched to the lower position; the output flow of the second hydraulic pump 17 is converged with the output oil of the first hydraulic pump 2 through the lower position of the second electromagnetic directional valve 14 and the one-way valve 13, and enters the rodless cavity of the hydraulic cylinder 11 through the right position of the first hydraulic directional valve 7 and the right position of the second hydraulic directional valve 10, the oil in the rod cavity of the hydraulic cylinder 11 enters the rodless cavity of the hydraulic cylinder 11 through the right position of the second hydraulic directional valve 10, and the hydraulic cylinder 11 differentially extends to realize the fast forward of the compression mechanism; meanwhile, the second electromagnet YV2 of the first electromagnetic directional valve 3 is powered, the first electromagnetic directional valve 3 is changed to the left position, and control oil enters the left position of the first electromagnetic directional valve 3 through the first oil port 61 and the control oil port X of the two-way cartridge valve 6 and returns to the hydraulic oil tank 1 through the first overflow valve 4; at this time, the system maximum pressure is set by the first relief valve 4, and the second hydraulic pump 17 working circuit pressure is set by the third relief valve 15;
A first compression stage: when the compression mechanism contacts garbage, the second electromagnet YV2 of the first electromagnetic directional valve 3 is continuously powered on, the electromagnet YV7 of the second logic valve 9 and the first electromagnet YV3 of the second electromagnetic directional valve 14 are powered off, the second hydraulic directional valve 10 is changed to a normal position, the second electromagnetic directional valve 14 is switched to a neutral position, the output flow of the first hydraulic pump 2 enters a rodless cavity of the hydraulic cylinder 11 through the right position of the first hydraulic directional valve 7 and the normal position of the second hydraulic directional valve 10, the oil in the rod cavity of the hydraulic cylinder 11 returns to the hydraulic oil tank 1 through the normal position of the second hydraulic directional valve 10 and the right position of the first hydraulic directional valve 7, and the output oil of the second hydraulic pump 17 returns to the hydraulic oil tank 1 through the neutral position of the second electromagnetic directional valve 14; the system pressure is set by the second relief valve 5;
Compressing in place, continuously powering on the first electromagnet YV3 of the second electromagnetic directional valve 14, powering on the electromagnet YV5 of the first logic valve 8 and the second electromagnet YV2 of the first electromagnetic directional valve 3, powering off the electromagnet YV7 of the second logic valve 9, reversing the first hydraulic directional valve 7 to the right, enabling the output oil of the second hydraulic pump 17 to flow into the output oil of the first hydraulic pump 2 through the lower position of the second electromagnetic directional valve 14, enabling the output oil of the one-way valve 13 to enter a rod cavity of the hydraulic cylinder 11 through the right position of the first hydraulic directional valve 7 and the left position of the second hydraulic directional valve 10, and enabling the oil without the rod cavity of the hydraulic cylinder 11 to flow back into the hydraulic tank 1 through the left position of the second hydraulic directional valve 10 and the right position of the first hydraulic directional valve 7; the system pressure is set by the first relief valve 4;
the compression mechanism circularly acts until the set circulation times are reached, the first compression stage is completed, and the compression mechanism is reset.
And (3) a strong pressure stage:
The electromagnet YV6 of the third logic valve 12 and the first electromagnet YV1 of the first electromagnetic directional valve 3 are electrified, the first hydraulic directional valve 7 is switched to the left position, the output flow of the first hydraulic pump 2 enters a rodless cavity of the hydraulic cylinder 11 through the left position of the first hydraulic directional valve 7 and the left position of the second hydraulic directional valve 10, and the oil in the rod cavity of the hydraulic cylinder 11 returns to the oil tank through the left position of the second hydraulic directional valve 10 and the right position of the first hydraulic directional valve 7; the hydraulic cylinder 11 stretches out to carry out strong pressure; at this time, the system maximum pressure is set by the second relief valve 5;
compressing in place, wherein the electromagnet YV6 of the third logic valve 12 and the first electromagnet YV1 of the first electromagnetic directional valve 3 lose electricity, the electromagnet YV5 of the first logic valve 8 and the second electromagnet YV2 of the first electromagnetic directional valve 3 get electricity, the first hydraulic directional valve 7 commutates to the right, the oil output by the first hydraulic pump 2 enters a rodless cavity of the hydraulic cylinder 11 from the left of the second hydraulic directional valve 10, the oil in the rod cavity of the hydraulic cylinder 11 returns to the hydraulic oil tank 1 from the left of the second hydraulic directional valve 10 and the right of the first hydraulic directional valve 7, the hydraulic cylinder 11 returns, and the compression mechanism resets; at this time, the system maximum pressure is set by the first relief valve 4;
The compression mechanism completes the circulation action until reaching the set circulation times, the second compression stage is completed, and the compression mechanism is reset.
The compression mechanism is forced to retreat:
If the equipment is in an abnormal shutdown condition and the compression mechanism is in an extending state, when the compression mechanism needs to be reset, the electromagnet YV5 of the first logic valve 8 and the first electromagnet YV1 of the first electromagnetic directional valve 3 are electrified, the oil output by the first hydraulic pump 2 enters a rod cavity of the hydraulic cylinder 11 through the right position of the first hydraulic directional valve 7 and the left position of the second hydraulic directional valve 10, and the oil in the rodless cavity of the hydraulic cylinder 11 returns to the hydraulic oil tank 1 through the left position of the second hydraulic directional valve 10 and the right position of the first hydraulic directional valve 7; the hydraulic cylinder 11 is retracted, and the compression mechanism is reset; at this point, the system maximum pressure is defined by the first relief valve 4.
According to the hydraulic system of the garbage compression station with controllable pressure and flow and the control method thereof, provided by the invention, as a preferred embodiment, the loop of the second hydraulic pump 17 can be used for controlling an auxiliary action loop, the second electromagnetic directional valve 14 is powered by the second electromagnet YV4, the second electromagnetic directional valve 14 is switched to an upper position, the output oil of the second hydraulic pump 17 enters the auxiliary action loop through the upper position of the second electromagnetic directional valve 14, and the pressure of the auxiliary action loop is limited by the third overflow valve 15.
According to the hydraulic system and the control method of the garbage compression station with controllable pressure and flow, when the speed of the compression mechanism is switched, a flow valve is not required to be added, and only the working position of the reversing valve is required to be controlled to switch, so that differential or double-pump confluence is realized, the energy loss of the system caused by throttling and overflow is reduced, and the energy utilization rate of the system is improved. The hydraulic system solves the problems of various types and quantity of valve groups and low system universality of the existing garbage compression station body; the hydraulic system can meet the pressure and speed control requirements of compression mechanisms of different series of stations and improve the integration level of the hydraulic system.
In the description of the present invention, it should be understood that the directions or positional relationships indicated by the terms "upper", "lower", "left", "right", etc. are based on directions or positional relationships shown in the drawings or in actual use engineering, are merely for convenience in describing the present invention and simplifying the description, and do not indicate or imply that the specific directions or orientations that the device or element referred to must have, be constructed and operated in the specific directions, and are not to be construed as limiting the present invention. Furthermore, the terms "first," "second," "third," and the like are used for descriptive purposes only and are not to be construed as indicating or implying a relative importance or implying a number of technical features being indicated.
Terms used in any of the technical aspects of the present disclosure for expressing positional relationships or shapes include states or shapes similar, analogous or approaching thereto unless otherwise stated. Any part provided by the invention can be assembled by a plurality of independent parts, or can be manufactured by an integral forming process.
The foregoing specific examples are provided to illustrate the principles and embodiments of the present invention and to aid in understanding the methods and core concepts of the present invention. Although the invention has been described in detail with reference to preferred embodiments, those skilled in the art will understand that modifications and equivalents may be made to the specific embodiments of the invention or to some of the features of the invention without departing from the spirit and principles of the invention, and such modifications and variations are within the scope of the appended claims.
Claims (5)
1. The hydraulic system of the garbage compression station with controllable pressure and flow is characterized by comprising a main valve group, a control valve group, an auxiliary action valve group, a first hydraulic pump, a second hydraulic pump, a hydraulic oil tank and a hydraulic oil cylinder; the outlet pressure of the first hydraulic pump acts on each logic valve in the main valve group after being reduced by the reducing valve, so as to control the switching of the working positions of each hydraulic control reversing valve in the main valve group, and the hydraulic oil cylinder is controlled in an action mode; the electromagnetic reversing valve in the auxiliary action valve group is used for controlling the output flow of the second hydraulic pump to be switched in between the main valve group system and the auxiliary action hydraulic system through power supply and power failure, so as to control the action speed of the hydraulic cylinder; the first hydraulic pump selects overflow valves with different set pressures to be combined into a system through control switching of working positions of electromagnetic directional valves in a control valve group so as to limit the highest working pressure of the system and realize multistage pressure switching;
The main valve group comprises a first hydraulic control reversing valve, a second hydraulic control reversing valve, a first logic valve, a third logic valve, a second logic valve and a two-way cartridge valve, wherein:
the first pilot-operated directional valve is a three-position four-way directional valve, the middle slide valve can be O-shaped, and the first pilot-operated directional valve is as follows: the oil inlet is communicated with the first hydraulic pump, the oil return port is communicated with the hydraulic oil tank, and the first working oil port and the second working oil port are respectively communicated with the oil inlet and the oil return port of the second hydraulic control reversing valve;
The first logic valve, the second logic valve and the third logic valve are two-position three-way reversing valves, a second oil port of the first logic valve is communicated with the right end of the first hydraulic reversing valve, a second oil port of the third logic valve is communicated with the left end of the first hydraulic reversing valve, a second oil port of the second logic valve is communicated with the right end of the second hydraulic reversing valve, the first logic valve and the third logic valve control reversing actions of the first hydraulic reversing valve, the second logic valve control reversing actions of the second hydraulic reversing valve, the second hydraulic reversing valve is a two-position four-way reversing valve, a normal-position slide valve can be P-shaped, a first working oil port of the second hydraulic reversing valve is communicated with a rodless cavity of a hydraulic cylinder, a second working oil port of the second hydraulic reversing valve is communicated with the rod cavity of the hydraulic cylinder, and the second hydraulic reversing valve controls differential actions of the hydraulic cylinder;
the control valve group comprises a first electromagnetic reversing valve, a first overflow valve, a second overflow valve and a pressure reducing valve, wherein:
the first electromagnetic reversing valve is a three-position four-way reversing valve, the middle-position slide valve can be H-shaped, and an oil return port of the first electromagnetic reversing valve is communicated with an oil return port of the first overflow valve, an oil return port of the second overflow valve and an oil drain port of the pressure reducing valve, and is communicated with a first oil port of the first logic valve, a second logic valve and a third logic valve, and a left end of the second hydraulic reversing valve, and a second working oil port is plugged;
the oil inlet of the pressure reducing valve is communicated with the first hydraulic pump, and the oil outlet of the pressure reducing valve is communicated with the third oil ports of the first logic valve, the second logic valve and the third logic valve;
the auxiliary action valve group comprises a second electromagnetic reversing valve, a third overflow valve and a one-way valve, wherein:
the second electromagnetic reversing valve is a three-position four-way reversing valve, the middle slide valve can be H-shaped, the oil inlet of the second electromagnetic reversing valve is communicated with the oil outlet of the second hydraulic pump, and the oil return port is communicated with the hydraulic oil tank; the second electromagnetic reversing valve is connected with the third overflow valve in parallel; the second working oil port of the second electromagnetic directional valve is connected with an auxiliary action system, and the first working oil port is communicated with the oil inlet of the one-way valve; and the oil outlet of the one-way valve is communicated with the oil inlet of the first hydraulic control reversing valve.
2. The hydraulic system of a refuse compression station with controllable pressure and flow according to claim 1, characterized in that said main valve set: the oil inlet is communicated with a first hydraulic pump, the first working oil port I and the first working oil port II are communicated with a rodless cavity of the hydraulic oil cylinder, the second working oil port is communicated with a rod cavity of the hydraulic oil cylinder, and the oil return port I and the oil return port II are communicated with the hydraulic oil tank; and the oil inlet of the auxiliary action valve group is communicated with the second hydraulic pump.
3. The hydraulic system of a waste compression station with controllable pressure and flow as claimed in claim 2, wherein the two-way cartridge valve: the first oil port is communicated with the first hydraulic pump and the oil inlet of the pressure reducing valve, and the control oil port is communicated with the second overflow valve oil inlet and the first electromagnetic directional valve oil inlet.
4. The hydraulic system of the garbage compression station with controllable pressure and flow according to claim 2, wherein the set pressure of the first overflow valve is lower than the set pressure of the second overflow valve, the set pressure of the third overflow valve is lower than the set pressure of the first overflow valve, and the set pressure of the pressure reducing valve is set according to the reversing demands of the first hydraulic control reversing valve and the second hydraulic control reversing valve.
5. The control method of the hydraulic system of the garbage compression station with controllable pressure and flow is characterized by comprising a hydraulic cylinder action control method, a hydraulic cylinder action speed control method and a multistage pressure switching control method, wherein the control method is used for controlling the hydraulic system of the garbage compression station with controllable pressure and flow, and the control method is characterized in that:
the hydraulic cylinder action control method comprises the following steps:
the outlet pressure of the first hydraulic pump is reduced by the pressure reducing valve and then acts on the first logic valve, the second logic valve and the third logic valve; the first logic valve, the second logic valve and the third logic valve working positions are switched by controlling the electromagnet of the first logic valve, the electromagnet of the second logic valve and the electromagnet of the third logic valve to be powered on and powered off, so that the switching of the first hydraulic control reversing valve and the working positions of the second hydraulic control reversing valve is controlled, and the extending, retracting and differential actions of the hydraulic oil cylinder are realized;
the hydraulic cylinder action speed control method comprises the following steps:
The differential motion of the hydraulic oil cylinder is realized by controlling the switching of the working position of the second hydraulic control reversing valve; controlling the output flow of the second hydraulic pump to be connected to a main valve group system or an auxiliary action hydraulic system by controlling the electromagnet of the second electromagnetic directional valve to be powered on and powered off, so as to control the action speed of the hydraulic cylinder;
The multistage pressure switching control method comprises the following steps:
The first hydraulic pump output oil is communicated with the oil inlet of the first electromagnetic directional valve through the control oil port of the two-way cartridge valve, the electromagnet of the first electromagnetic directional valve is controlled to be electrified and de-electrified, the working position of the first electromagnetic directional valve is controlled to switch, the first overflow valve and the second overflow valve are selected to be integrated into the system, the highest working pressure of the system is limited, and multistage pressure switching is realized.
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| CN104314907A (en) * | 2014-10-12 | 2015-01-28 | 郑州大学 | Hydraulic system for jacking pipe |
| CN106089827A (en) * | 2016-07-18 | 2016-11-09 | 福建龙马环卫装备股份有限公司 | A kind of hydraulic system of sunk garbage compression station |
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| Publication number | Priority date | Publication date | Assignee | Title |
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| CN107355435B (en) * | 2017-08-28 | 2023-07-25 | 福龙马集团股份有限公司 | A dual-power hydraulic pump station system for garbage compression equipment |
| CN114151398A (en) * | 2021-12-15 | 2022-03-08 | 天水锻压机床(集团)有限公司 | Hydraulic control system of vertical garbage compression station |
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Patent Citations (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN104314907A (en) * | 2014-10-12 | 2015-01-28 | 郑州大学 | Hydraulic system for jacking pipe |
| CN106089827A (en) * | 2016-07-18 | 2016-11-09 | 福建龙马环卫装备股份有限公司 | A kind of hydraulic system of sunk garbage compression station |
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