JP2017223169A - Multiple revolving chamber type high viscosity fluid pump - Google Patents

Abstract

PROBLEM TO BE SOLVED: To provide a low cost high viscosity fluid pump realizing it by a lesser number of component elements in which occurrence of friction at a pumping action is prevented, complex machine configurations such as an intake valve and a discharging valve are not required, a fluid resistance at an opening part is reduced, and deterioration of fluid is avoided.SOLUTION: Two rotors 20, 30 having convexoconcave curved surfaces 21, 31 at their outer peripheral parts are oppositely rotated while being synchronized in pump chambers 23, 33, an intake region and a discharging region are separated through engagement between the convexoconcave curved surfaces, high viscosity fluid is taken into several chambers dynamically formed by the convexoconcave curved surfaces and a pump inner wall from a suction port 7 through an intake region, the high viscosity fluid is transferred by the turning of the chambers of themselves to the rotating downstream side and discharged out of a discharging port 8 through the discharging region.SELECTED DRAWING: Figure 1

Description

  The present invention relates to a positive displacement pump for transferring a high-viscosity fluid.

  There are two types of pumps, a non-positive type and a positive type pump. In order to pump a high-viscosity fluid, a positive type pump is generally adopted. The positive displacement pump can be further classified into a reciprocating type, a screw type, and a rotary type.

  The reciprocating pump is particularly called a plunger type and is characterized by discharging a fluid flowing from one end through an inlet valve from an outlet valve at the same end in accordance with a reciprocating plunger. Even if it is a highly viscous fluid, it can be pushed out by the plunger, but the volume in one container is changed by the reciprocating motion of the plunger, and the fluid of the volume inserted by the plunger is discharged. In order to use one container, an intake valve and a discharge valve that are linked to this reciprocating motion are required. However, in the pumping of a high viscosity fluid, the valve cannot be operated completely, and a normal plunger pump cannot be used for a high viscosity fluid. A problem arises in the smooth suction and discharge of the high-viscosity liquid through the valve. Even if the fluid can pass through the valve, a shearing force may act on the fluid and adversely affect the properties of the fluid. Furthermore, as the invention described in Japanese Patent Application Laid-Open No. H10-228561 is a problem, the pulsation and instability of the discharge pressure by the plunger may become a problem as the viscosity becomes higher.

  The screw type uses the kinematic viscosity between the screw surface and the pipe inner surface to transfer and discharge the fluid from one end to the other end. Generally, a seal material is disposed on the screw end and the inner wall of the pipe. Durability becomes a problem as the viscosity of the transfer fluid increases. In addition, in the case of a high-viscosity fluid, in some cases, the rotation of the screw itself becomes impossible or unstable. Sometimes a large starting torque is required due to static friction, adhesion and sticking. In addition, since the screw type pump lacks the suction capacity, it is necessary to invent a separate high-viscosity fluid conveyance part to the screw type pump inlet part as described in Patent Document 2, depending on the properties of the individual fluids. The problem of becoming will also arise.

  In addition, there are gear-type pumps, but in high-viscosity fluids, the fluid is often damaged by sliding between the gears, and the properties are often adversely affected.

  As described above, it is considered that the remaining rotary type pump is suitable for the transfer of the high-viscosity fluid by the positive displacement pump. However, even the rotary type pump is the invention described in FIG. In the uniaxial eccentric type rotary pump, there is a possibility that a shearing force is always applied to the transfer fluid while the rotor is rotating due to the rotor rolling in the pump chamber (see Patent Document 3 and FIG. 4), and the properties of the pump fluid may be adversely affected.

  Non-Patent Document 1 also discloses a type using a biaxial rotor for a high-viscosity fluid. The pump disclosed in Non-Patent Document 1 creates a vacuum in the suction port of the pump by two rotating rotors, sucks fluid into the space, and the two rotating rotors are rotated in a non-contact manner by a timing gear. The pump fluid is pushed out “continuously” (where “continuous” is an expression described in the explanation of the principle of operation in non-patent literature) every time the two rotors rotate 180 degrees. Yes (non-patent document 1, operating principle diagram described on the same page). In this configuration, the convex surfaces of the two rotors face each other, and it is difficult to form a sufficient seal, uneven suction is generated, pulsation is not suppressed, and pump fluid discharge is intermittent rather than continuous.

In pumping of high-viscosity fluid, once the rotor has stopped and a certain amount of time has passed, adsorption occurs at the interface between the high-viscosity fluid and the solid, or the difference or change in the properties of the high-viscosity fluid between the stationary state and the pumping state. As a result, the rotor may be adsorbed or fixed to the pump housing. This point is substantially the same as the problem of the screw type pump, and may be a problem unlike a pure plunger type pump. In particular, the adsorption phenomenon has a problem that the generation conditions are complicated, and the generation has a stochastic element and is difficult to predict.

  Thus, it is an object of the present invention to provide a high-viscosity fluid pump at a low cost that eliminates a valve and extrudes a high-viscosity fluid while extruding a high-viscosity fluid and suppresses discharge pulsation. It was recognized.

  That is, the present invention avoids deterioration and damage of a high-viscosity fluid due to kinematic viscosity between the pump drive body and the housing, and does not cause high added static friction, adsorption or adhesion even after restarting after the pump transfer is stopped. This eliminates the need for complicated configurations such as suction valves and discharge valves, reduces fluid resistance during suction and discharge of high-viscosity fluid into the pump chamber, and avoids fluid alteration, thereby reducing the number of parts required for high-viscosity fluid pumps. A low-cost high-viscosity fluid pump realized by

JP 10-174920 A JP 2005-545691 A JP 2009-191717 A

http://www.miuraz.co.jp/product/pump/vrp.html, Miura top page> Product information> Pump / boiler parts> High viscosity liquid transfer pump VRP, June 7, 2016

The main problem of the present invention is to enable the transfer of high viscosity fluid,
1. Creates a vacuum similar to a plunger and allows high-viscosity fluid to be smoothly sucked into the pump chamber.
2. While discharging fluid friction similar to a plunger, high viscosity fluid is extruded and discharged from the pump chamber,
3. Avoiding alteration and damage of high-viscosity fluid due to kinematic viscous friction between the pump driver and housing,
4). Even when restarting after stopping pump transfer, high added static friction does not occur,
5. Eliminates the need for complicated configurations such as intake and discharge valves,
6). Avoiding fluid alteration while reducing fluid resistance at the time of suction and discharge of high viscosity fluid into the pump chamber,
7). Low-cost high-viscosity fluid pump that realizes a high-viscosity fluid pump with fewer parts,
Etc. is to provide.

In the pump of the present invention, two rotors having different cross-sectional arc shapes are engaged. The outer edge of one rotor has a plurality of semicircular arc-shaped convex portions, and the outer edge of the other rotor has a semi-arc-shaped concave portion that is the same shape as the convex portion, and each rotor has the same center. The two rotors are meshed with each other and rotated in two pump arcs with two arcuate portions while being timed by the action of the timing mechanisms such as the gears.
The pump housing is provided with a suction port and a discharge port facing each other.
In this pump, the suction port and the discharge port are determined by the rotation direction of the gear, and the suction port and the discharge port are separated in the pump chamber by the meshing portion of the two rotors that mesh the suction side and the discharge side. One is a portion for sucking a high-viscosity fluid as a suction side space, and the other is a discharge side space. Unlike a plunger pump, a valve (valve) is unnecessary.
The rotor side having a convex arc is a first pump chamber having a larger inner diameter, the rotor side having a concave arc is a second pump chamber having a smaller inner diameter, and the first and second pump chambers are A plurality of rotary chambers are further formed by the arcuate portion constituting the mesh and the inner wall of the housing.

(Function and effect)
The space on the fluid inlet side of the pump increases in volume due to the rotation of the rotor, and the space on the outlet side decreases in volume, and suction / discharge is performed in the same manner as the plunger pump. It is carried to the discharge side by the action of the rotary pump. That is, with the rotation of the arc portion due to the rotation of the rotor, high-viscosity fluid is sucked from the suction port by the expansion of the space on the fluid inlet side, and is surrounded by the space surrounded by the arc portion and the pump chamber inner wall, and the convex arc portion and the housing inner wall. The angled rotary chamber is swiveled around the axis on the first pump chamber side, and the half-moon shaped rotary chamber surrounded by the concave arc and the inner wall of the housing is rotated and transferred to the discharge port side by extrusion. The fluid is discharged out of the discharge port, and suction, transfer, and discharge are completed while avoiding the alteration of the fluid.
Therefore, the present invention
A first rotor having a cross section forming a convex curved surface;
A second rotor having a cross section forming a concave curved surface and arranged axially parallel to said rotor;
A timing mechanism in which each timing control member is concentrically coupled to each rotor capable of rotationally driving the two rotors in opposite directions; and the rotation of each rotor can be synchronized; and
A first pump chamber formed in an axial concentric cylinder with the first rotor, and a second pump formed in an axial concentric cylinder with the second rotor in parallel with the first pump chamber in the axial direction. A housing having a pumping chamber and a bearing portion capable of rotatably supporting the two rotors;
The two rotors include a plurality of concave and convex curved surface portions having the same number of concave and convex surface shapes whose outer edges of the axial cross-sectional shape can mesh with each other, and the housing includes the two A high-viscosity fluid pump comprising a suction port for a high-viscosity fluid on one side perpendicular to the axial direction and a discharge port facing the suction port on the other side at a central portion of the meshing portion of the rotor.
As a modification of the invention, a groove may be dug in the arc surface so that the surfaces facing each other do not adhere to the two arc surfaces.

(Function and effect)
When the groove is carved in this way, the groove provides an effect of increasing the surface distance between the opposing surfaces and reducing the kinematic viscosity resistance.
When the groove is carved in this way, the surface distance between the opposing surfaces is increased by the groove, and the formation of a meniscus at rest can be prevented and the static adhesion resistance can be reduced.
As another modification of the present invention, there may be provided a high-viscosity fluid pump that is the housing connected to the opening and communicating with the opening and the second pump chamber to form a cylindrical cavity in the axial direction. .

(Function and effect)
This cylindrical part reduces the fluid frictional resistance during suction and increases the connection time between the half-moon-shaped rotating chamber and the high-viscosity fluid inlet opening, thereby increasing the suction effect. Can be prevented and the pump efficiency can be improved.
In the present invention, the meshing portion may be composed of four or more.

(Function and effect)
In this way, if the meshing portions are composed of four or more, the meshing portions are formed more densely, and the number of concave and convex curved surface portions is the same. The effect that the gap between the meshing portions can be set to the minimum can be obtained.

As described above, according to the present invention, the following 1. Avoiding alteration and damage of high-viscosity fluid due to kinematic viscous friction between the pump driver and housing,
2. Even when restarting after stopping the pump transfer, high added static friction, adsorption and adhesion do not occur,
3. Eliminates the need for complicated configurations such as intake and discharge valves,
4). Avoiding fluid alteration while reducing fluid resistance at the time of suction and discharge of high viscosity fluid into the pump chamber,
5. It is possible to provide a low-cost high-viscosity fluid pump that realizes a high-viscosity fluid pump with a smaller number of parts.

1 is a schematic perspective view of a high-viscosity fluid pump 1 that is an embodiment of a high-viscosity fluid pump according to the present invention. 1 is an exploded perspective schematic view of a high-viscosity fluid pump 1 that is an embodiment of a high-viscosity fluid pump according to the present invention. 1 is a schematic front view of a high-viscosity fluid pump 1 that is an embodiment of a high-viscosity fluid pump according to the present invention, and is a vertical cross-sectional view of the center of a suction port and a discharge port. The housing 6 is hatched. FIG. 3 is a schematic front view of a deformable high-viscosity fluid pump 1 in which the rotors 20 and 30 that are the housing internal components are not hatched. It is a back surface schematic diagram of high viscosity fluid pump 1 which shows a housing internal configuration at the time of removing a back cover in a back surface schematic diagram of high viscosity fluid pump 1 which is one embodiment of a high viscosity fluid pump concerning the present invention. 1 is a schematic side view of a rotor gear structure in an assembled state of a high-viscosity fluid pump 1 that is an embodiment of a high-viscosity fluid pump according to the present invention. It is a side surface conceptual schematic diagram which sees through the inside of a housing. Transition showing the movement of suction of the high-viscosity fluid near the intake port 7 to the chamber when the shafts 2 and 3 of the high-viscosity fluid pump 1 which is an embodiment of the high-viscosity fluid pump according to the present invention rotate. FIG. Transition showing over time the movement discharged from the chamber of the high-viscosity fluid near the exhaust port 8 when the shafts 2 and 3 of the high-viscosity fluid pump 1 which is an embodiment of the high-viscosity fluid pump according to the present invention rotate. FIG. It is a pump cycle chart figure of the high viscosity fluid pump 1 which is one embodiment of the high viscosity fluid pump concerning the present invention. It is a side surface schematic diagram of high viscosity fluid pump 701 which is other forms of a high viscosity fluid pump concerning the present invention.

Hereinafter, an embodiment of the present invention will be described in detail with reference to the accompanying drawings.
FIG. 1 is a schematic perspective view of a high-viscosity fluid pump 1 that is an embodiment of the high-viscosity fluid pump 1 according to the present invention, and FIG. 2 is an embodiment of the high-viscosity fluid pump 1 according to the present invention. FIG. 3 is a schematic exploded perspective view of the high-viscosity fluid pump 1, and FIG. 3 is a schematic front view of the high-viscosity fluid pump 1, which is an embodiment of the high-viscosity fluid pump 1 according to the present invention. 4 shows the internal configuration of the housing part 5, and FIG. 4 shows the internal configuration of the housing when the back cover is removed in the schematic back view of the high-viscosity fluid pump 1, which is an embodiment of the high-viscosity fluid pump 1 according to the present invention. FIG. 5 conceptually shows the structure of the timing gears 22 and 32 of the timing mechanism 40 that controls the rotation of the rotors 20 and 30 in the assembled state of the high-viscosity fluid pump 1 that is an embodiment of the high-viscosity fluid pump according to the present invention. Aspect concept FIG. 6 is a diagram showing the high-viscosity fluid pump in the vicinity of the inlet 7 when the shafts 2 and 3 of the high-viscosity fluid pump 1 that is an embodiment of the high-viscosity fluid pump according to the present invention rotate. FIG. 7 is a schematic perspective view from the front showing the movement of suction over time, and FIG. 7 shows exhaust when the shafts 2 and 3 of the high-viscosity fluid pump 1 which is an embodiment of the high-viscosity fluid pump according to the present invention rotate. FIG. 8 is a transition diagram showing the movement of the high-viscosity fluid near the mouth 8 discharged from the chamber over time, and FIG. 8 is a pump cycle chart of the high-viscosity fluid pump 1 which is an embodiment of the high-viscosity fluid pump according to the present invention. Among these schematic views, the rotor meshing portion of FIG. 5 including the vertical cross-sectional schematic view is hatched to clearly show the vertical cross-section, and in FIG. 3, the housing portion 5 is hatched to indicate the vertical cross-sectional schematic view. Figure 4, Figure The timing gear illustrates a side conceptual schematic diagram for perspective internal housing.

<One Embodiment of High Viscosity Fluid Pump 1 According to the Present Invention>
The high-viscosity fluid pump 1 according to the present invention includes a first rotor 20 having a cross section that forms a convex curved surface 21; a cross section that forms a concave curved surface 31; and the rotor 20 is disposed parallel to the axial direction AX. A second rotor 30 of;
Timings at which the timing control members 22 and 32 are concentrically coupled to the rotors 20 and 30 capable of rotating the two rotors 20 and 30 in opposite directions to synchronize the rotations of the rotors 20 and 30. Mechanism 40; and
A first pump chamber 23 formed in an axial concentric cylinder with the first rotor, and formed in an axial concentric cylinder with the second rotor 30 in parallel with the first pump chamber 23 in the axial direction AX. A housing 6 having bearings 11 and 13 and a bearings 12 and 14 which can rotatably support shafts 2 and 3 coupled to the two rotors 20 and 30. A housing part 5 including a back cover 9 and a housing front cover 10;
The two rotors 20 and 30 include a plurality of concave and convex curved surface portions 21 and 31 having the same number of concave and convex surface shapes that can engage with each other on the outer edges of the axial cross-sections, and The housing 6 has a suction port 7 for a high-viscosity fluid on one side perpendicular to the axial direction at the center of the meshing portion of the two rotors 20 and 30 and a discharge port 8 facing the suction port 7 on the other side. A high-viscosity fluid pump 1 is provided. The two rotors 20, 30 are fixedly connected to the shafts 2, 3 by keys, and the rotors 20, 30 are meshed and connected, and synchronous rotation control is performed by timing gears 22, 32. Indentations 18 and 19 adjacent to the suction port 7 and connecting the second pump chamber 33 and the suction port 7 are provided in the second pump chamber wall surface 33. Here, the meshing does not necessarily need to be in contact, and may be slightly spaced apart.

<Operational effect of the present invention shown in the same embodiment>
The two pump chambers 23 and 33 cooperate with the high-viscosity fluid pump 1 according to the present invention to pump a high-viscosity fluid. The operational effects of the high-viscosity fluid pump 1 are expressed in terms of the transition of each stage of the pump operation. This will be described with reference to FIG.

In general, the time base of the strokes (1) to (5) is defined as one stroke, with one rotation corresponding to the number of meshing portions provided in the rotor as one cycle, and one cycle is divided into four equal parts for convenience of explanation. FIG. 8 shows a pump cycle chart. Here, the starting point of one pump cycle is determined for convenience of explanation when the outer edge boundary of the rotor is inscribed in the inner surface of the pump and the formation of the chamber is started. One cycle is from the start of the formation of the chamber to the completion of the chamber. In the high-viscosity fluid pump 1 according to the present embodiment, the suction port 7 is formed such that the formation start point of the most upstream chamber 26 on the first pump chamber 23 side coincides with the chamber formation start point on the second pump chamber 33 side. .
(1) First stroke: S10 From the start of chamber formation to ¼ cycle elapse (2) Second stroke: S20 From 1/4 cycle to 1/2 cycle (3) Third stroke: S30 From 1/2 cycle Up to 3/4 cycle (4) Fourth stroke: S40 From 3/4 cycle to chamber completion (5) Repeat of the first stroke From the top of the high viscosity fluid pump 1 in FIG. Repeat cycle. In the following (1) to (5), focusing on one or two of the plurality of chambers, the time course of suction or discharge will be described. Here, the stage refers to a cut point representing a change with time of the pump function based on a high-viscosity fluid, and the stroke described in parentheses refers to a cut point representing a change with time of rotation based on the rotor rotation. The rotors 20 and 30 are fixedly connected to the shafts 2 and 3 by keys, respectively, and further fixedly connected to the drive shaft of a motor drive mechanism (not shown) at the end of the shaft 2 on the timing gear 22 side.

i) Suction of high-viscosity fluid from suction port Pay attention to one or two of the plurality of chambers 26, 27, 28, 29, 37, 38, and 39 for pump suction of high-viscosity fluid near the suction port 7. The classification into the suction stages according to the time course is as follows.
(1) Pre-suction stage (first stroke: S10)
(2) Suction stage (initial stage) (second stroke: S20)
(3) Suction stage (mid-term) (third process: S30)
(4) Suction stage (late stage) (fourth stroke: S40)
(5) Conveying stage (returning to the first stroke S10. This corresponds to the pre-suction stage for the adjacent concavo-convex portion located downstream of the rotor rotation, and thereafter repeats S10 and subsequent steps.)

  The high-viscosity fluid pump 1 according to the present invention is a multi-chamber type pump having six meshing portions in each of the rotors 20 and 30, and the rotor 20 has a cylindrical surface as a convex curved surface 21 outward with respect to the rotation axis. Six equal angles are equally arranged, and the rotor 30 has a cylindrical surface as a concave curved surface 31 and is equally arranged in six equal angles inward with respect to the rotation axis, and a plurality of chambers 26, 27, 28 ( 6) and 29 and 37, 38 and 39 (hereinafter referred to as 37 etc.) can be formed inscribed in the housing 6 by the rotor outer edge portions 21 and 31 and the pump inner wall surfaces 23 and 33, as shown in FIG. In the vicinity of the suction port 7 located at the upper part, a high-viscosity fluid group 201 (hereinafter simply referred to as a high-viscosity fluid 201) is vacuum-sucked from the outside into the housing 6 as the rotors 20 and 30 rotate in opposite directions. In addition, in the vicinity of the discharge port 8 located in the lower part of FIG. 6, the high-viscosity fluids 403 and 303 are released from the chambers 29 and 39 near the discharge port 8 at the rotational speed of the rotor and stay in the vicinity of the discharge port 8 immediately before that. The fluid group 203 (hereinafter simply referred to as the high-viscosity fluid 203) of the high-viscosity fluid that has been combined is compressed and discharged from the discharge port 8.

  The first stroke S10 of (1) corresponds to the shaft rotation state in which the two rotors are most meshed with each other in this embodiment, but the feature of this stage is in the region adjacent to the multi-chambers 26 and 36. In this stage, a new chamber is about to be formed as the shafts 2 and 3 are rotated. The shaft may be continuously rotated and does not need to be stepped. In that sense, it does not mean that there is a static pre-suction stage in this stage, but just before a new chamber is formed. The time slice is captured in the meaning of the stage.

  (5) is a case where the shaft where the next chamber starts to be formed after the next stroke of S10 is sequentially advanced (in this embodiment, six meshing portions are arranged at equiangular angles) is rotated. At this time, the pump cycle is the same as in the first stroke. If (1) → (5) is the total stroke, in this embodiment, the shaft rotates 1/6 during this time.

(2), (3), and (4) are suction stages that equally divide between (1) and (5) on the time axis,
The second stroke S20 is a 1/4 stroke and the shaft rotates 1/24. The third stroke S30 is a 2/4 stroke, and the shaft rotates 1/12 from S10. The stroke S40 is a 3/4 stroke, and the state in which the shaft is rotating by 1/8 from S10 indicates the relationship with the shaft rotation.

(1) In the pre-suction stage (first process: S10), the semi-cylindrical chamber and rotor in which the high-viscosity fluid 201 is to be formed from the convex curved surface 21 and the pump chamber inner surface 23 formed on the outer edge of the rotor 20 This is the stage immediately before the suction of each of the semi-cylindrical chambers to be formed by the concave curved surface 31 and the pump chamber inner surface 33 formed on the outer edge of 30.
(2) In the suction stage (initial stage) (second stroke: S20), after 1/24 rotation of the shaft, the rotation of the rotors 20 and 30 increases the volume in the vicinity of the suction port 7 and the degree of vacuum in this portion increases and the intake port 7. A new high-viscosity fluid group 400 is sucked from the outside, and a new chamber is being formed at the place where the original chambers 26 and 37 existed by the progress of ¼ stroke.
(3) In the suction stage (mid-term) (third stroke: S30), the shaft rotates 1/12, and the rotation of the rotors 20 and 30 advances the formation of about half of the new chamber by a half stroke. The high-viscosity fluid 201 is deformed with the high-viscosity fluid 202 and taken into both chambers while being taken into the new chamber forming part from the vicinity of the suction port 7.
(4) In the suction stage (late stage) (fourth stroke: S40), the shaft rotates 1/8, and the rotation of the rotors 20 and 30 advances the formation of a new chamber to about 3/4. The viscous fluid 201 is in the stage of being taken into the new chamber forming part from the vicinity of the suction port 7. In the present invention, since the high-viscosity fluid is the target pump, in order to promote suction as much as possible, the recessed portions 18 and 19 adjacent to the suction port and connecting the second pump chamber 33 and the suction port 7 are provided in the second pump chamber. It is provided on the pump chamber wall surface 33 and has a configuration that promotes suction into the chamber that is about to be formed by the concave curved surface 31 provided in the rotor 30 and the second pump chamber surface 33 even after the second stroke. The high-viscosity fluid 201 in the vicinity of the suction port 7 can be connected until the fourth stroke is completed, and the suction capacity is increased. The chamber to be formed by the convex curved surface 21 provided in the rotor 20 and the first pump chamber inner surface 23 is provided in the first pump chamber inner surface and the rotor 20 without providing the same depression on the first pump side. The high-viscosity fluid 201 in the chamber and the vicinity of the suction port 7 formed by the convex curved surface 21 and the convex curved surface of the meshing portion adjacent to the rotation downstream side and the pump chamber inner surface 33 can be connected until the completion of the fourth stroke. There is no need to handle the depression separately, but a design that can be provided is also possible.

ii) In the transfer to the discharge port (5) In the transfer stage (returning to the first step S10), the chambers 26 and 37 are newly formed, and the high-viscosity fluid 201 is transferred to the high-viscosity fluids 203 and 303 in the chamber 26, respectively. , 37 is constrained in the space area. At this stage, the new high-viscosity fluid 400 is vacuum-sucked as the meshing portion opens in the vicinity of the suction port 7 like the original high-viscosity fluid 201, and the high-viscosity fluid is sequentially replenished. The high-viscosity fluids 203 and 303 constrained in the chamber as the rotor is rotated are turned toward the discharge port 8.

iii) High-Viscosity Fluid Discharge from Discharge Port Focusing on one or two of the plurality of chambers for pump discharge of high-viscosity fluid in the vicinity of the discharge port 8 and classifying and explaining them according to these aging steps are as follows.
(1) Pre-discharge stage (first stroke: S10)
(2) Discharge stage (initial stage) (second stroke: S20)
(3) Discharge stage (mid-term) (third process: S30)
(4) Discharge stage (late stage) (fourth stroke: S40)
(5) Conveying step (S50, corresponding to S10 for adjacent convex portions, hereinafter repeated from S10)

  In the vicinity of the discharge port 8 located at the lower part in FIG. 7, the high-viscosity fluids 303 and 403 are rotated and discharged from the multi-chambers 29 and 39 as the rotors 20 and 30 rotate, and at the same time, the discharge port 8 located at the lower part in FIG. In the vicinity, the high-viscosity fluids 403 and 303 are combined with the high-viscosity fluid 203 that has stayed in the vicinity of the discharge port 8 immediately before and are compressed and discharged from the discharge port 8. Since the high-viscosity fluid sandwiched between the convex surface 24 and the concave surface 34 facing each other until the meshing portion is completely engaged again is squeezed toward the discharge port 8, there is also an effect that the high-viscosity fluid is not likely to stay in the central portion. obtain.

iii) For the above i) and ii), the steps described in (1) to (5) (), S10, S20, S30, S40 are categories of the rotary machine over time as described above. As described above, S10 → S20 → S30 → S40 → S10 corresponds to one cycle of the pump function. In one embodiment shown in FIG. 1, the rotors 20 and 30 have 6 meshing portions, and the cycle is repeated 6 cycles in one rotation of the rotor. Therefore, it is a new type of multi-turn chamber type high viscosity fluid pump 1 that corresponds to a pump having six plungers as compared with a normal one plunger pump type. The discharge amount per rotation is distributed to 6 discharge cycles during one rotation of the rotor, and is distributed to 6 based on the pump capacity of the discharge amount per rotation, and the pulsation is also distributed to 6 as well as 1 The amount discharged in the cycle is averaged and smoothed in the swirl region constituted by the convex recesses, and if the inner surface arc radius of the first pump chamber is R and the inner surface arc radius of the second pump is r, the rotational frequency F is a discharge amount H per hour per pump length, which is approximately given by the following equation (1).

  The discharge amount H per hour per pump length is leveled to the expression (1), and pulsation is almost eliminated. If the shape parameters of the concave and convex portions of the rotor meshing part become parameters of the discharge amount per hour, and both are in a close complement relationship, the discharge amount H per hour per pump length using the inner radius of both pumps as a parameter Is in the relationship of equation (1). In particular, when the meshing portion is configured with an even number as in this embodiment, the corresponding chamber volumes of the first pump chamber side chamber and the second pump chamber side chamber are always constant, providing a stable discharge amount. To give the effect. It is difficult to form a meshing form that can be sufficiently complemented by two meshing parts, and the number of meshing parts is preferably four or more, more smoothly six meshing parts are more preferable, and this can be increased. However, it should be noted that even if the amount is increased too much, the result is that the depth of the chamber is reduced, and this embodiment discloses the case of 6 as a particularly preferable condition.

  In the case of a curved surface configuration using an arc shape, in the chambers 37, 38, 39 using the concave curved surface 31 or the like, the shearing force hardly flows due to the separation to the bottom surface of the concave portion, and the high viscosity fluid is damaged or altered. Minimize. In the chambers 26, 27, 28, and 29 that use convex curved surfaces sandwiched between adjacent convex portions, the flow toward the high-viscosity fluid is difficult due to the separation toward the bottom formed between the convex curved surfaces 21 and the like. Minimize damage and deterioration of viscous fluid. Particularly in a high-viscosity fluid, the kinematic viscosity coefficient μ is high, and it is an important factor to minimize damage and alteration due to a shearing force proportional to this.

  In the present embodiment, an axial groove 35 is provided in the concave curved surface 31. The groove 35 keeps the separation between the curved surfaces of the meshing portion, minimizes damage and deterioration due to the shearing force of the high-viscosity fluid, prevents sticking of the high-viscosity fluid to the meshing solid surface at the time of stop, and forms meniscus The effect of preventing adsorption is obtained. The groove is preferably about 1 mm, and the direction thereof is not limited to the axial direction, but may be one in the width direction. For example, a groove 36 in the width direction may be added as in the present embodiment. It may be provided in a herringbone shape even in an oblique direction.

  In the present embodiment, the convex curved surface 21 and the concave curved surface 31 mesh with each other in a curved configuration using an arc shape. The meshing portion exhibits sufficient sealing performance, can suppress the pump suction pulsation and discharge pulsation due to the seal breaking, and the addition of the groove 35 enhances the sealing effect even if the meshing portion is separated. Is also possible.

  In the present embodiment, the suction port 7 and the discharge port 8 are relative, and if the pump rotation direction is reversed, the suction port 7 can also be used as a discharge port. 8 is used as a suction port.

FIG. 9 is a schematic side view of a high-viscosity fluid pump 701 that is another embodiment of the high-viscosity fluid pump according to the present invention. A high-viscosity fluid pump 701, which is another form of the high-viscosity fluid pump according to the present invention, includes a first rotor 720 having a cross section forming a convex curved surface 721, and the same number of pairs as the convex curved surface 721. A second rotor 730 having a cross-section forming a concave curved surface 731 and arranged axially parallel to the first rotor 720;
Each timing control member (not shown) is concentrically coupled to each rotor capable of rotating the two rotors 720 and 730 in opposite directions, and the rotation of each rotor can be synchronized (not shown). 740; and
A first pump chamber formed in an axial concentric cylinder with the first rotor 720 and a first pump chamber formed in an axial concentric cylinder with the second rotor in parallel with the first pump chamber in the axial direction. A plurality of chambers 728, 729, and 739 surrounded by the pump chamber inner surface and the convex curved surface 721 or the concave curved surface 731 of the rotor can be formed, and the two rotors 720 and 730 can be formed. A housing portion 705 having a bearing portion (not shown) capable of rotatably supporting
The convex curved surface 721 and the concave curved surface 731 include concave and convex curved surface portions in which the outer edges of the axial sectional shapes of the two rotors 720 and 730 can mesh with each other, and
The housing 705 has a high-viscosity fluid suction port 707 on one side perpendicular to the axial direction at the center of the meshing portion of the two rotors 720 and 730 and a discharge port 708 opposite the suction port 707 on the other side. Prepared,
The chambers 728, 729, and 739 are high-viscosity fluid pumps 705 capable of taking in high-viscosity fluid from the suction port and turning the rotor center toward the discharge port, and are multi-swirl chamber type high-viscosity fluid pumps. The four chamber configuration is the minimum configuration that can level the pumping.

  Although the embodiment according to the present invention has been described above, the embodiment described here is described in considerable detail. However, the applicant does not intend to limit or limit the appended claims to such detailed description in any way. In addition, the present invention is not limited to such an embodiment, and the part of the configuration of the invention expressed in one embodiment can be adopted in other embodiments, and Various modifications can be made without departing from the spirit of the invention. In addition, each effect for solving the problems of the invention taken up here is not limited to appearing in one embodiment at the same time, and it is enough that at least one of them is expressed and the object of the invention is achieved. Yes, those skilled in the art can easily judge. Accordingly, the invention is broadly limited to specific details, each device and method disclosed and described herein, or combinations thereof, examples, and the spirit of Applicant's general inventive concept. It is possible to deviate from these details without departing from the scope.

  The present invention is a multi-swirl chamber type high-viscosity fluid pump that seals and swirls high-viscosity fluid in a multi-chamber and hardly exerts shearing force on the high-viscosity fluid. It can be used to transfer high-viscosity fluids for high-specification applications such as fine chemicals requiring pharmaceuticals, pharmaceutical applications, general-purpose products that require low costs, and public uses such as muddy water.

DESCRIPTION OF SYMBOLS 1 High-viscosity fluid pump 2, 3 Shaft 5 Housing part 6 Housing main body 7 Suction port 8 Discharge port 9 Housing back plate 10 Housing front plate 18, 19 Recessed part 20 First rotor 21, 24 Convex curve 22 Timing gear 23 First Pump chamber 26, 27, 28, 29 chamber 30 second rotor 31, 34 concave surface 32 timing gear 33 second pump chamber 35, 36 groove 37, 38, 39 chamber 40 timing mechanism 11, 12, 13, 14 Bearing parts 201, 202, 203, 303, 403 High viscosity fluid
701 High-viscosity fluid pump 720, 730 Rotor 721, 731 Concave and curved surface 705 Housing 707 Suction port 708 Discharge port 723, 733 Pump chamber 728, 729, 739 Chamber AX Axial direction S1 Pump cycle S10 First stroke S20 Second stroke S30 Second 3rd stroke S40 4th stroke

Claims (11)

A first rotor having a cross section forming a convex curved surface; and a second rotor having a cross section forming a concave curved surface and arranged in parallel to the rotor in the axial direction;
A timing mechanism in which each timing control member is concentrically coupled to each rotor capable of rotationally driving the two rotors in opposite directions; and the rotation of each rotor can be synchronized; and
A first pump chamber formed in an axial concentric cylinder with the first rotor, and a second pump formed in an axial concentric cylinder with the second rotor in parallel with the first pump chamber in the axial direction. A housing portion having a bearing portion that has a pump chamber and can rotatably support the two rotors;
The two rotors include a plurality of concave and convex curved surface portions having the same number of concave and convex surface shapes whose outer edges of the axial cross-sectional shape can mesh with each other, and the housing includes the two A high-viscosity fluid pump comprising a suction port for a high-viscosity fluid on one side perpendicular to the axial direction and a discharge port facing the suction port on the other side at a central portion of the meshing portion of the rotor. A first rotor having a cross section forming a convex curved surface; and a second rotor having a cross section forming the same number of concave curved surfaces paired with the convex curved surface and arranged parallel to the first rotor in the axial direction. A rotor of;
A timing mechanism in which each timing control member is concentrically coupled to each rotor capable of rotationally driving the two rotors in opposite directions; and the rotation of each rotor can be synchronized; and
A first pump chamber formed in an axial concentric cylinder with the first rotor, and a second pump formed in an axial concentric cylinder with the second rotor in parallel with the first pump chamber in the axial direction. A housing having a bearing portion capable of forming a plurality of chambers surrounded by the pump chamber inner surface and the convex curved surface or the concave curved surface of the rotor and capable of rotatably supporting the two rotors. Part;
The convex curved surface and the concave curved surface include an uneven curved surface portion in which outer edges of axial cross-sectional shapes of two rotors can mesh with each other, and
The housing comprises a suction port for high-viscosity fluid on one side perpendicular to the axial direction at the center of the meshing portion of the two rotors, and a discharge port facing the suction port on the other side,
The chamber is capable of taking a high-viscosity fluid from the suction port and turning the rotor center toward the discharge port. When the radius in the cylinder of the first pump chamber is R and the radius in the cylinder of the second pump chamber is r, the pump discharge amount per hour is approximately the following equation (1):

3. The high-viscosity fluid pump according to claim 1, wherein the convex curved surface of the first rotor and the concave curved surface of the second rotor are formed so as to be in close meshing engagement with each other.   3. The high-viscosity fluid pump according to claim 1, wherein the second pump chamber has a hollow portion adjacent to the suction port and connecting the second pump chamber and the suction port.   3. The high-viscosity fluid pump according to claim 1, wherein the second pump chamber has a cylindrical recess adjacent to the suction port and connected to the second pump chamber and the suction port.   The high-viscosity fluid pump according to claim 1, wherein a groove is provided in at least one of the concave curved surface portion and the convex curved surface portion.   The high-viscosity fluid pump according to claim 1, wherein the timing mechanism is a spur gear mechanism.   The curved surface is a part of a cylindrical surface, the convex cross section of the first rotor includes an arc, and the concave cross section of the second rotor includes an arc. A pump for high viscosity fluid according to the above.   The high-viscosity fluid pump according to claim 8, wherein the arc is substantially a semicircle.   3. The high-viscosity fluid pump according to claim 1, wherein the concave curved surface portion and the convex curved surface portion are formed in an even number of four or more in each rotor.   The high-viscosity fluid pump according to claim 1, wherein the concave curved surface portion and the convex curved surface portion are formed in each rotor by six.

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