JP2015148206A - rotary pump - Google Patents

Abstract

PROBLEM TO BE SOLVED: To provide a rotary pump which realizes high pressure discharge while maintaining the sealability.SOLUTION: A seal member 80 disposed at an outer periphery of an outer rotor 51 is formed by a seal function part 81 and an elastic pressing part 82 and a deformation inhibition part 81b is provided at the seal function part 81. The structure inhibits a resin part 81a from deforming and entering into the low pressure portion side of an outer peripheral clearance S. Therefore, the structure inhibits damage of the resin part 81a, secures the sealability, and realizes high pressure discharge of a rotary pump 11.

Description

  The present invention relates to a rotary pump that performs fluid suction and discharge, and is particularly suitable when applied to a rotary pump for a brake device that performs brake fluid pressure control by performing suction and discharge of brake fluid.

  Conventionally, it has been proposed to use an internal gear type rotary pump such as a trochoid pump as a pump for a brake device (for example, see Patent Document 1). This rotary pump includes an inner rotor having outer teeth on the outer periphery, an outer rotor having inner teeth on the inner periphery, a casing for housing these outer rotor and inner rotor, and the like. The inner rotor and the outer rotor are disposed in the casing in a state where the inner teeth and the outer teeth are engaged with each other and a plurality of gaps are formed by these teeth. Further, assuming that a line passing through both central axes of the inner rotor and the outer rotor is a center line of the pump, suction ports and discharge ports communicating with the plurality of gaps are provided on both sides of the center line. .

  In the pump configured as described above, when driven, the inner rotor is driven by the drive shaft to rotate, and accordingly, the outer rotor is also rotated in the same direction by the meshing of the outer teeth and the inner teeth. At this time, the volume of each gap portion changes in size while the outer rotor and the inner rotor rotate once, sucks fluid from the suction port, and discharges fluid from the discharge port.

  In addition, since a low pressure part and a high pressure part are generated in the gap between the outer periphery of the outer rotor and the casing during the pump drive, a seal member is provided on the outer periphery of the outer rotor to seal the low pressure part and the high pressure part. Is arranged. Specifically, a recess is formed at a position corresponding to the outer periphery of the outer rotor in the casing, and a seal member composed of a resin member and a rubber member is disposed in the recess. The rubber member is disposed on the bottom surface side of the recess, and the resin member is disposed on the outer peripheral surface side of the outer rotor. Thereby, the resin member is pressed by the rubber member, and the resin member is brought into contact with the outer peripheral surface of the outer rotor, so that the low pressure portion and the high pressure portion on the outer periphery of the outer rotor can be sealed.

JP 2002-295376 A

  In recent years, there has been an increasing demand for enabling high-pressure discharge of brake fluid. However, the above-described conventional seal member requires a wide clearance between the casing and the outer rotor with respect to the required pressure due to design limitations that take into account manufacturing errors, etc. However, sufficient durability could not be obtained. Specifically, the resin member may be deformed and entered into the gap between the casing and the outer rotor, and the resin member may be damaged to prevent sealing performance. In particular, under high temperature and high pressure, the resin member is easily deformed and easily enters the gap between the casing and the outer rotor. For this reason, the durability of the seal member cannot be ensured, and it has been difficult to realize high-pressure discharge of the rotary pump.

  An object of this invention is to provide the rotary pump which can implement | achieve high-pressure discharge, keeping a sealing performance in view of the said point.

  In order to achieve the above object, in the first aspect of the present invention, the suction pressure of the outer peripheral gap (S) is introduced into the inner wall surface of the casing (50) facing the outer peripheral surface of the outer rotor (51). A recess (50e, 50f) is formed between the part and the part into which the discharge pressure is introduced, and a seal member (80, 90) is provided in the recess to hold the differential pressure between the suction pressure and the discharge pressure. . The seal member is in contact with the suction pressure side surface in the outer circumferential clearance of the inner wall surfaces of the outer rotor and the recess, and holds the differential pressure, and the bottom side of the recess with respect to the seal function portion. And an elastic pressing portion (82) that presses the seal function portion to the outer peripheral surface side of the outer rotor, and the seal function portion contacts the suction pressure side surface in the outer peripheral clearance of the inner wall surfaces of the outer rotor and the recess. It is made of a material harder than the resin part (81a) that holds the differential pressure by contact with the resin part, and is disposed on the suction pressure side of the outer peripheral gap, and the boundary position with the resin part is a recess than the outer peripheral gap. It has the deformation | transformation suppression part (81b) made into the inner wall surface side.

  Thus, the seal member is disposed between the low pressure portion and the high pressure portion of the outer circumferential gap. For this reason, the sealing function part is pressed to the low pressure part side of the outer peripheral gap by the elastic reaction force of the elastic pressing part and the high-pressure fluid of the outer peripheral gap. As a result, the resin part can contact the inner wall surface of the recess in addition to the outer circumferential surface of the outer rotor and the inner wall surface of the casing, and can seal between the high-pressure part and the low-pressure part of the outer circumferential gap. Brake fluid can be prevented from leaking.

  At this time, although the resin portion is pressed by the high-pressure brake fluid, since the seal function portion includes the deformation suppressing portion, it is possible to suppress the resin portion from being deformed and entering the low-pressure portion side of the outer circumferential gap. . Therefore, the breakage of the resin portion can be suppressed, sealing performance can be ensured, and high-pressure discharge of the rotary pump can be realized.

  In addition, the code | symbol in the bracket | parenthesis of each said means shows an example of a corresponding relationship with the specific means as described in embodiment mentioned later.

It is the figure which showed the hydraulic circuit structure of the brake device with which the rotary pump concerning 1st Embodiment of this invention is applied. It is sectional drawing which showed the detailed structure of the rotary pump. It is an enlarged view of the vicinity of the seal member 80 in FIG. FIG. 6 is a view showing a state where a seal function part 81 provided in a seal member 80 is viewed from the axial direction of a drive shaft 54. FIG. 4 is a view showing a state when the seal function part 81 shown in FIG. 3B is viewed in the radial direction from the drive shaft 54. FIG. 6 is a view showing a state when the arrangement location of the seal member 80 is viewed in the radial direction from the drive shaft 54. FIG. 10 is a view showing a modification of the seal function unit 81 described in another embodiment, and is a view showing a state in which the seal function unit 81 is viewed from the axial direction of the drive shaft. FIG. 10 is a view showing a modification of the seal function unit 81 described in another embodiment, and is a view showing a state in which the seal function unit 81 is viewed from the axial direction of the drive shaft. FIG. 10 is a view showing a modification of the seal function unit 81 described in another embodiment, and is a view showing a state in which the seal function unit 81 is viewed from the axial direction of the drive shaft. FIG. 10 is a view showing a modification of the seal function unit 81 described in another embodiment, and is a view showing a state in which the seal function unit 81 is viewed from the axial direction of the drive shaft. It is the figure which showed the mode when the sealing function part 81 shown to Fig.8 (a) was seen from the drive shaft 54 to radial direction. FIG. 10 is a view showing a modification of the seal function unit 81 described in another embodiment, and is a view showing a state in which the seal function unit 81 is viewed from the axial direction of the drive shaft. It is the figure which showed the mode when the seal function part 81 shown to Fig.9 (a) was seen from the drive shaft 54 to radial direction. FIG. 10 is a view showing a modification of the seal function unit 81 described in another embodiment, and is a view showing a state in which the seal function unit 81 is viewed from the axial direction of the drive shaft. It is the figure which showed the mode when the seal function part 81 shown to Fig.10 (a) was seen from the drive shaft 54 to radial direction. FIG. 10 is a view showing a modification of the seal function unit 81 described in another embodiment, and is a view showing a state in which the seal function unit 81 is viewed from the axial direction of the drive shaft.

  Hereinafter, embodiments of the present invention will be described with reference to the drawings. In the following embodiments, parts that are the same or equivalent to each other will be described with the same reference numerals.

(First embodiment)
An embodiment of the present invention will be described. The rotary pump described in this embodiment is provided as a component of the hydraulic circuit of the brake device shown in FIG. Here, a brake device that constitutes a hydraulic circuit of an X pipe including the right front wheel-left rear wheel and the left front wheel-right rear wheel piping system will be described as an example.

  As shown in FIG. 1, a brake pedal 1 that is depressed by an occupant when a braking force is applied to a vehicle is connected to a booster device 2, and the brake pedal force and the like are boosted by this booster device 2.

  The booster 2 has a push rod or the like that transmits the boosted pedaling force to a master cylinder (hereinafter referred to as M / C) 3, and this push rod is connected to a master piston disposed on the M / C 3. M / C pressure is generated by pressing.

  Note that a master reservoir 3a for supplying brake fluid into M / C3 and storing excess brake fluid in M / C3 is connected to M / C3.

  The M / C pressure is transmitted as a W / C pressure to the wheel cylinder (hereinafter referred to as W / C) 4 for the right front wheel FR and the W / C 5 for the left rear wheel RL. The brake fluid pressure control actuator 6 disposed between the W / Cs 4 and 5 controls the W / C pressure.

  Hereinafter, the first piping system corresponding to the right front wheel FR and the left rear wheel RL will be described. However, since the second piping system corresponding to the left front wheel FL and the right rear wheel RR is exactly the same, Description is omitted.

  The brake device is provided with a pipe line (main pipe line) A connected to the M / C 3, and the pipe line A is provided with a differential pressure control valve 7. The pipe A is divided into two parts by the differential pressure control valve 7. That is, the pipe A is connected to the pipe A1 that receives the M / C pressure between M / C3 and the differential pressure control valve 7, and to the pipe A2 between the differential pressure control valve 7 and each of the W / Cs 4 and 5. Divided.

  The differential pressure control valve 7 controls the communication state and the differential pressure state. The differential pressure control valve 7 is normally in a communication state. However, by setting the differential pressure state, the W / C 4, 5 side can be maintained at a pressure higher than the M / C 3 side by a predetermined differential pressure.

  In the pipeline A2, the pipeline A is branched into two, one of which is provided with a pressure increase control valve 8a for controlling the increase of the brake fluid pressure to the W / C 4, and the other is connected to the W / C 5. There is provided a pressure increase control valve 8b for controlling the increase in the brake fluid pressure.

  These pressure-increasing control valves 8a and 8b are configured as two-position valves that can control the communication / blocking state by an electronic control device (hereinafter referred to as ECU) for controlling brake fluid pressure (not shown). When the two-position valve is controlled to be in a communicating state, a brake fluid pressure based on the M / C pressure or the like can be applied to each W / C 4 and 5. These pressure-increasing control valves 8a and 8b are always controlled in a normal communication state when a brake brake pressure control such as an anti-lock brake (hereinafter referred to as ABS) control is not executed.

  Further, the pipeline A between the pressure increase control valves 8 a and 8 b and the respective W / Cs 4 and 5 is connected to the pressure regulating reservoir 9 via the pipeline B. The brake fluid is allowed to escape to the pressure regulating reservoir 9 through the conduit B, whereby the W / C pressure applied to the W / Cs 4 and 5 is controlled to prevent the wheels from becoming locked.

  Further, pressure reducing control valves 10a and 10b that can control the communication / blocking state by the ECU are provided in the pipeline B, respectively. These pressure reduction control valves 10a and 10b are always cut off in the normal brake state (when brake fluid pressure control is not controlled), and are appropriately brought into communication when the brake fluid is released to the pressure regulating reservoir 9 described above. .

  A pump 11 driven by a motor 12 is provided together with check valves 11a and 11b in a pipe C connecting the pipe A and the pressure regulating reservoir 9 between the differential pressure control valve 7 and the pressure increase control valves 8a and 8b. Has been.

  In order to reduce the pulsation of the brake fluid discharged from the pump 11, an accumulator 13 is disposed on the downstream side of the pump 11 in the pipe C. A pipe D is provided so as to connect the pressure regulating reservoir 9 and the M / C 3, and the pump 11 sucks the brake fluid in the pipe A 1 through the pipe D and the pressure regulating reservoir 9, The W / C pressure is increased by discharging to the pipe line A2.

  A second piping system having the same configuration as the first piping system as described above is provided. In addition to the various control valves 7, 8 a, 8 b, 10 a, 10 b, the rotary pump 11, and the pressure regulating reservoir 9 that are provided in each of these piping systems, the motor 12 is assembled in a housing in which various piping is formed by drilling. A hydraulic control actuator 6 is configured. The brake fluid pressure control actuator 6 is provided between the M / C 3 and the W / C 4, 5, whereby the brake device shown in FIG. 1 is configured.

  Brake fluid pressure control such as ABS control, brake assist control, adaptive cruise control, regenerative brake control, and the like is performed by using the brake device configured as described above, and the rotary pump 11 is driven to suck in brake fluid. A discharge operation is performed. In recent years, of the brake fluid pressure control, when executing the control (brake assist control, adaptive cruise control, etc.) for increasing the brake fluid pressure by the suction / discharge operation of the rotary pump 11, the response is higher with higher responsiveness. It is required to generate a W / C pressure. For this reason, realization of high-pressure discharge of the rotary pump 11 is desired.

  On the other hand, in this embodiment, the rotary pump 11 is comprised as follows. The detailed structure of the rotary pump 11 will be described with reference to FIG. 2, FIG. 3, and FIG.

  The rotary pump 11 is accommodated in the rotor chamber 50 a of the casing 50. Specifically, in the rotor chamber 50a, the outer rotor 51 and the inner rotor 52 constituting the rotating part in the rotary pump 11 are assembled with their respective central axes (point X and point Y in the figure) being eccentric. It is attached and stored.

  The outer rotor 51 includes an inner tooth portion 51a on the inner periphery, and the inner rotor 52 includes an outer tooth portion 52a on the outer periphery. The outer rotor 51 and the inner rotor 52 form a plurality of gaps 53 by mutual tooth portions, and mesh with the contact surfaces of the inner tooth portions 51a and the outer tooth portions 52a as meshing surfaces. The outer rotor 51 and the inner rotor 52 are rotated by a drive shaft 54 disposed at the center of the inner rotor 52.

  The rotary pump 11 configured as described above is a multi-tooth trochoid type without a partition plate (crescent) in which a gap 53 is formed by the inner teeth 51a of the outer rotor 51 and the outer teeth 52a of the inner rotor 52. It is a pump. In the rotary pump 11, the inner rotor 52 and the outer rotor 51 have a plurality of contact points on the meshing surfaces in order to transmit the rotational torque of the inner rotor 52.

  The casing 50 has side plates 50c and 50d (see FIG. 4) so as to sandwich both end faces of the rotors 51 and 52 in the rotational axis direction and the central plate 50b with the portion surrounding the outer periphery of the rotors 51 and 52 as the central plate 50b. Is configured. In addition, a rotor chamber 50a is configured by a space formed by the central plate 50b and the side plates 50c and 50d, and the drive shaft 54 is fitted into a center hole (not shown) formed at the center of the side plates 50c and 50d. ing. The outer rotor 51 and the inner rotor 52 are rotatably arranged in the rotor chamber 50a. In other words, the rotating part constituted by the outer rotor 51 and the inner rotor 52 is rotatably incorporated in the rotor chamber 50a of the casing 50, the outer rotor 51 rotates about the point X, and the inner rotor 52 sets the point Y. It will rotate as an axis.

  Furthermore, when the line passing through the point X and the point Y, which are the respective rotation axes of the outer rotor 51 and the inner rotor 52, is the center line Z of the rotary pump 11, the side plate 50c A suction port 60 and a discharge port 61 communicating with the rotor chamber 50a are formed. The suction port 60 and the discharge port 61 are disposed at positions that communicate with the plurality of gaps 53. The brake fluid from the outside can be sucked into the gap 53 through the suction port 60 and the brake fluid in the gap 53 can be discharged to the outside through the discharge port 61.

  Of the plurality of gaps 53, the closed portion 53a having the maximum volume does not communicate with either the suction port 60 or the discharge port 61, and the suction pressure at the suction port 60 is reduced by the closed portion 53a. And the pressure difference between the discharge pressure at the discharge port 61 is maintained. One of the side plates has an outer peripheral clearance S of the outer rotor 51, that is, a conduction path that connects the suction port 60 with the outer peripheral clearance of the outer rotor 51 and the casing, and the outer peripheral clearance S and the discharge port. A conduction path communicating with 61 is provided. Thereby, a portion corresponding to the suction port 60 in the outer circumferential clearance S is set to a low suction pressure, and at least a portion corresponding to the discharge port 61 in the outer peripheral clearance S is set to a high discharge pressure.

  And in the inner wall surface of the part which comprises the center plate 50b in the casing 50 shown in FIG. Are formed with recesses 50e and 50f having recessed inner wall surfaces. Seal members 80 and 90 for suppressing the flow of the brake fluid in the outer circumferential clearance S of the outer rotor 51 are provided in the recesses 50e and 50f. That is, the seal members 80 and 90 are formed so as to be located on both sides of the outer circumferential gap S with a position corresponding to the suction port 60 interposed therebetween.

  These sealing members 80 and 90 seal the low-pressure part and the high-pressure part in the outer circumferential gap S, and the brake fluid in the high-pressure part is prevented from flowing to the low-pressure part. In addition, the position corresponding to the suction port 60 in the outer circumferential gap S can be held at a low suction pressure, and the position corresponding to the discharge port 61 in the outer circumferential gap S can be held at a high discharge pressure. The pressure can be balanced inside and outside. For this reason, it is possible to suppress the outer rotor 51 from being pressed against a specific portion of the inner rotor 52 or the casing 50 based on the imbalance of the brake fluid pressure, and the deviation of the outer periphery of the both tooth portions 51a and 52a and the outer rotor 51 based on this Wear can be suppressed.

  3A to 3C and FIG. 4 show the detailed structure of the seal member 80. FIG. Here, the seal member 80 is illustrated, and the details of the seal member 80 will be described below, but the same applies to the seal member 90.

  As shown in FIGS. 3A to 3C, the seal member 80 includes a seal function part 81 and an elastic pressing part 82.

  The seal function part 81 is a part that exhibits a function of sealing the low-pressure part and the high-pressure part in the outer peripheral clearance S by being pressed by the outer peripheral surface of the outer rotor 51 and the side plates 50c and 50d. The seal function part 81 has a resin part 81a and a deformation suppressing part 81b. In the case of the present embodiment, the sealing function part 81 is formed in a substantially rectangular parallelepiped shape, and basically the sealing function part 81 is configured by the resin part 81a. A deformation suppressing portion 81b is arranged for one side and both corners. That is, a portion of the sealing function portion 81 that contacts the outer peripheral clearance S on the low-pressure site side is configured by the deformation suppressing portion 81b, and a portion that does not contact the outer peripheral clearance S is the resin portion 81a.

  The resin portion 81a is made of a soft resin material such as Teflon (registered trademark). In addition to the outer peripheral surface of the outer rotor 51 (see FIG. 3A) and the side plates 50c and 50d (see FIG. 4), the resin portion 81a is the inner wall surface of the recess 50e, specifically, the low pressure portion of the outer peripheral clearance S. It is set as the structure which has the contact surface which contact | abuts to the side wall surface of a side, respectively. Each of the contact surfaces surrounds the deformation suppressing portion 81b by one. For this reason, between the low pressure site | part and the high voltage | pressure site | part of the outer periphery clearance gap S is sealed by the contact surface of the resin part 81a, and the differential pressure | voltage between these can be hold | maintained. The dimension of the resin portion 81a in the same direction as the rotation axis direction of the outer rotor 51 is longer than the dimension of the rotor chamber 50a in the same direction, that is, the distance between the side plates 50c and 50d. Thereby, as shown with the broken line in FIG. 4, the resin part 81a is crushed by both side plates 50c and 50d, and a sealing performance is improved.

  In the case of the present embodiment, the pressing surface 81aa is configured by cutting out a side having a diagonal relationship with the side where the deformation suppressing portion 81b is arranged in the resin portion 81a. The elastic pressing portion 82 comes into contact with the pressing surface 81aa.

  The deformation suppressing portion 81b is made of a resin or metal that is harder than the resin portion 81a, and functions to suppress the deformation of the resin portion 81a toward the outer peripheral clearance S. Specifically, the deformation suppressing portion 81b is disposed at a position corresponding to the low pressure portion of the outer peripheral clearance S in the seal function portion 81 so that the resin portion 81a does not contact the low pressure portion of the outer peripheral clearance S. .

  In the case of the present embodiment, deformation is suppressed by a substantially triangular prism shape with one surface of the deformation suppressing portion 81b on the side plate 50c, 50d side as a bottom surface, the bottom surface as a substantial triangle, and each surface extending in the rotation axis direction of the outer rotor 51 as a side surface. Part 81b is configured. And the dimension design of the deformation | transformation suppression part 81b is performed so that one surface is turned to the outer periphery clearance gap S side, and the boundary position of the one surface and the resin part 81a is located in the recessed part 50e. Further, the dimension of the deformation suppressing portion 81b in the same direction as the rotation axis direction of the outer rotor 51 is made shorter than the dimension of the rotor chamber 50a in the same direction, that is, the distance between the side plates 50c and 50d.

  The resin portion 81a and the deformation suppressing portion 81b may be an integral structure or a separate structure, but in this embodiment, they are an integral structure. Specifically, as shown in FIG. 3C, the engagement recess 81ab that is recessed from the low pressure site side to the high pressure site side of the outer circumferential clearance S on the surface of the resin portion 81a on the outer rotor 51 side. Is formed. In addition, an engagement protrusion 81ba is formed on the surface of the deformation suppressing portion 81b on the outer rotor 51 side so as to protrude toward the high-pressure portion side of the outer circumferential clearance S. The engaging recess 81ab and the engaging protrusion 81ba engage with each other, so that the resin portion 81a and the deformation suppressing portion 81b are integrated.

  Thus, the sealing function part 81 which has the resin part 81a and the deformation | transformation suppression part 81b is comprised.

  On the other hand, the elastic pressing portion 82 is made of an elastically deformable material such as rubber, and is disposed on the bottom side of the concave portion 50e with respect to the sealing function portion 81. The resin portion 81a in the sealing function portion 81 is pressed against the outer peripheral surface of the outer rotor 51 and the inner wall surface of the recess 50e by the reaction force due to the elastic deformation of the elastic pressing portion 82. That is, the elastic pressing portion 82 is elastically deformed between the inner wall surface of the recess 50e and the pressing surface 81aa of the resin portion 81a in the sealing function portion 81, and presses the pressing surface 81aa side to press the resin portion 81a. Yes. Thereby, the space between the low pressure portion and the high pressure portion of the outer peripheral gap S by the resin portion 81a is sealed.

  Next, the operation of the brake device configured as described above and the rotary pump 11 will be described. For example, when the brake fluid pressure control is executed, various control valves 7 and 30 to 33 are controlled according to the control mode, and the motor 12 is driven, and the pump 11 performs a brake fluid suction and discharge operation.

  Specifically, in the rotary pump 11, the inner rotor 52 rotates in accordance with the rotation of the drive shaft 54 by driving the motor 12, and accordingly, the outer rotor 51 is engaged by the engagement between the inner tooth portion 51 a and the outer tooth portion 52 a. Also rotate in the same direction. At this time, since the volume of each gap 53 changes in size while the outer rotor 51 and the inner rotor 52 make one rotation, the brake fluid is sucked from the suction port 60 and is directed from the discharge port 61 toward the pipeline A2. Exhale brake fluid. The discharged brake fluid can increase the W / C pressure.

  As described above, the rotary pump 11 performs a basic pumping operation in which the brake fluid is sucked from the suction port 60 and the brake fluid is discharged from the discharge port 61 as the rotors 51 and 52 rotate. During this pumping operation, the position corresponding to the suction port 60 in the outer circumferential gap S of the outer rotor 51 is set as the suction pressure, and the position corresponding to the discharge port 61 in the outer circumferential gap S is set as the discharge pressure. For this reason, a low pressure portion and a high pressure portion are generated on the outer periphery of the outer rotor 51.

  However, as described above, the seal members 80 and 90 are disposed between the low pressure portion and the high pressure portion of the outer circumferential gap S. For this reason, the sealing function part 81 is pressed to the low pressure site | part side of the outer periphery clearance S by the elastic reaction force of the elastic pressing part 82 and the high-pressure brake fluid of the outer periphery clearance S. Accordingly, the resin portion 81a can contact the inner wall surface of the recess 50e in addition to the outer peripheral surface of the outer rotor 51 and the side plates 50c and 50d, and can seal between the high pressure portion and the low pressure portion of the outer peripheral clearance S. The brake fluid can be prevented from leaking from the side to the low pressure part side.

  At this time, the resin portion 81a is pressed by the high-pressure brake fluid. However, since the seal function portion 81 includes the deformation suppressing portion 81b, the resin portion 81a is deformed to the low pressure portion side of the outer peripheral clearance S. Intrusion can be suppressed. Therefore, damage to the resin part 81a can be suppressed, sealing performance can be secured, and high-pressure discharge of the rotary pump 11 can be realized.

(Other embodiments)
The present invention is not limited to the embodiment described above, and can be appropriately changed within the scope described in the claims.

  For example, the structure of the seal members 80 and 90 can be changed as appropriate. For example, a structure in which the resin portion 81a and the deformation suppressing portion 81b in the seal function portion 81 are separated can be employed. In that case, at least the boundary position between the surface on the low pressure site side of the outer peripheral clearance S on the inner wall surface of the recess 50e and the resin portion 81a in the deformation suppressing portion 81b may be located in the recess 50e.

  For example, as shown in FIG. 5, as in the first embodiment, each surface of the deformation suppressing portion 81 b that has one surface on the side plates 50 c, 50 d side as a bottom surface, the bottom surface is substantially triangular, and extends in the rotational axis direction of the outer rotor 51. The deformation suppressing portion 81b may be configured by a substantially triangular prism shape having a side surface.

  Further, as shown in FIG. 6, deformation suppression is achieved by a columnar shape in which one surface of the deformation suppressing portion 81 b on the side plates 50 c and 50 d side is a bottom surface, the bottom surface is circular, and a surface extending in the rotation axis direction of the outer rotor 51 is a side surface. The part 81b may be configured. When the deformation suppressing portion 81b has a cylindrical shape, when the rotary pump 11 is not in operation, the space between the resin portion 81a and the deformation suppressing portion 81b on the low pressure site side of the outer peripheral clearance S on the inner wall surface of the recess 50e is widened. It becomes. However, if the radius of the deformation suppressing portion 81b is made larger than the radial dimension of the outer peripheral clearance S, even if the resin portion 81a is deformed, the deformed portion can be prevented from entering the outer peripheral clearance S side. Therefore, as long as the boundary position between the resin portion 81a and the deformation suppression portion 81b when the resin portion 81a is deformed to the maximum is positioned in the recess 50e, the deformation suppression portion 81b may be cylindrical. Of course, the same can be said for other shapes in addition to the case where the deformation suppressing portion 81b is cylindrical. That is, in the radial direction of the drive shaft 54, the deformation suppressing portion 81b has a size larger than the outer peripheral clearance S, and the deformation suppressing portion 81b comes into contact with the inner wall surface of the recess 50e. The deformed portion of the portion 81a can be prevented from entering the outer peripheral clearance S.

  Further, as shown in FIG. 7, a substantially rectangular column shape in which one surface of the deformation suppressing portion 81 b on the side plates 50 c and 50 d side is a bottom surface, the bottom surface is a substantially square shape, and each surface extending in the rotation axis direction of the outer rotor 51 is a side surface. The deformation suppressing unit 81b may be configured as described above.

  Moreover, the engagement method when the resin part 81a and the deformation | transformation suppression part 81b in the sealing function part 81 are made into an integral structure can also be changed. In the following description, as shown in FIG. 7, a case where the deformation suppressing portion 81 b has a substantially quadrangular prism shape is taken as an example. However, a substantially triangular prism shape as shown in FIG. 5 and a cylindrical shape as shown in FIG. A similar structure can be applied.

  Specifically, as shown in FIGS. 8A and 8B, an engagement protrusion 81ac protruding to the low pressure region side of the outer peripheral clearance S is formed on the resin portion 81a, and the outer peripheral clearance S of the deformation suppressing portion 81b is formed. It is good also as a structure which formed the engagement recessed part 81bb dented from the high voltage | pressure site | part side to the low voltage | pressure site | part side. By adopting such a structure and engaging the engaging protrusion 81ac in the engaging recess 81bb, the resin portion 81a and the deformation suppressing portion 81b can be physically integrated.

  Further, as shown in FIGS. 9A and 9B, on the contact surface between the deformation suppressing portion 81b and the resin portion 81a, the outer rotor 51 side to the outer peripheral clearance S on the inner wall surface of the recess 50e are located on the low pressure site side. An engagement protrusion 81ba is formed so as to reach the surface. Then, an engagement recess 81ab corresponding to the engagement protrusion 81ba is formed in the resin portion 81a. Even with such a structure, the resin portion 81a and the deformation suppressing portion 81b can be physically integrated by fitting the engagement protrusion 81ba into the engagement recess 81ab to be engaged.

  Also, as shown in FIGS. 10A and 10B, an engagement recess 81ad is formed in the resin portion 81a in the contact surface between the deformation suppression portion 81b and the resin portion 81a, and the deformation suppression portion 81b is engaged. An engaging protrusion 81bc corresponding to the mating recess 81ad is formed. Even with such a structure, the resin portion 81a and the deformation suppressing portion 81b can be physically integrated by fitting the engagement protrusion 81bc into the engagement recess 81ad to be engaged.

  Moreover, as shown in FIG. 11, it is good also as a structure where the deformation | transformation suppression part 81b is wrapped in the resin part 81a. That is, as shown in FIG. 12, in the deformation suppressing portion 81b, the outer rotor 51 side and the surface on the low pressure site side of the outer peripheral clearance S on the inner wall surface of the recess 50e are partially covered by the resin portion 81a. Also good.

  DESCRIPTION OF SYMBOLS 10 ... Rotary pump, 50 ... Casing, 50a ... Rotor chamber, 50b ... Center plate, 50c, 50d ... Side plate, 50e, 50f ... Recess, 51 ... Outer rotor, 51a ... Inner tooth part, 52 ... Inner rotor, 54 DESCRIPTION OF SYMBOLS ... Drive shaft, 60 ... Suction port, 61 ... Discharge port, 80, 90 ... Seal member, 81 ... Seal function part, 81a ... Resin part, 81b ... Deformation suppression part, 82 ... Elastic press part

Claims (3)

A drive shaft (54);
An outer rotor (51) having an inner tooth portion (51a) on the inner periphery;
An inner rotor (52) having an outer tooth portion (52a) on the outer periphery and rotating about the drive shaft (54) as a rotation shaft, and engaging the inner tooth portion with the outer tooth portion to A rotating part assembled and formed to form a gap (53);
The drive shaft is fitted, and the rotary portion has a suction port (60) for sucking fluid and a discharge port (61) for discharging the fluid from the rotary portion, and the rotary portion is rotatably arranged. And a casing (50) in which a rotor chamber (50a) is formed,
An outer peripheral clearance (S) is formed between an inner wall surface of the casing facing the outer peripheral surface of the outer rotor and an outer peripheral surface of the outer rotor, and a portion of the outer peripheral clearance corresponding to the suction port is inhaled. The rotation portion of the rotating part is communicated with the outlet, and a portion of the outer peripheral gap corresponding to the outlet is connected with the outlet, and a low suction pressure and a high discharge pressure are introduced into the outer peripheral gap. In the rotary pump that sucks the fluid from the suction port into the plurality of gaps and discharges the fluid from the discharge port.
The inner wall surface of the casing that faces the outer peripheral surface of the outer rotor is recessed in the outer peripheral gap between a portion where the suction pressure is introduced and a portion where the discharge pressure is introduced. A concave portion (50e, 50f) is formed, and a seal member (80, 90) for holding a differential pressure between the suction pressure and the discharge pressure is provided in the concave portion,
The seal member includes a seal function part (81) that holds the differential pressure by contacting the suction pressure side surface of the outer circumferential gap among the inner wall surfaces of the outer rotor and the recess, and more than the seal function part. An elastic pressing portion (82) disposed on the bottom side of the recess and pressing the sealing function portion toward the outer peripheral surface of the outer rotor;
The sealing function part is harder than the resin part and the resin part (81a) that holds the differential pressure by contacting the suction pressure side surface of the outer peripheral clearance among the inner wall surfaces of the outer rotor and the recess. A deformation suppressing portion (81b) made of a material and disposed on the suction pressure side of the outer peripheral gap and having a boundary position with the resin portion on the inner wall surface side of the concave portion with respect to the outer peripheral gap. A rotary pump characterized by having.   2. The rotary pump according to claim 1, wherein a dimension of the deformation suppressing portion in an axial direction of the rotating shaft is shorter than a dimension of the rotor chamber in the same direction as the direction.   The dimension of the sealing function part in the axial direction of the rotating shaft is longer than the dimension of the rotor chamber in the same direction as the direction, and the sealing function part is crushed in this direction and disposed in the case. The rotary pump according to claim 1, wherein the rotary pump is provided.

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