JP2020148173A - Rotary pump - Google Patents

Abstract

To provide a rotary pump with a seal part, capable of securing excellent sealability and excellent assemblability.SOLUTION: A rotary pump 100 has an accommodating recess part 105c extending along an axial direction of an outer rotor 102 on a peripheral wall surface 105a1 for partitioning a rotor chamber 101a of a casing 101. In the accommodating recess part 105c, a resin member 107a and a rubber member 107b constituting a seal part 107 are integrally accommodated. The rubber member 107b has a length determined based on a tooth width along the axial direction of an inner tooth part 102a of the outer rotor 102, and is provided with a notch part 107b2.SELECTED DRAWING: Figure 3

Description

The present invention relates to a rotary pump.

Conventionally, for example, a rotary pump disclosed in Patent Document 1 below is known. In this conventional rotary pump, between the first side plate portion and the second side plate portion arranged so as to sandwich the outer rotor and the inner rotor from both sides, and the first and second side plate portions thereof. It is provided with a casing composed of a central plate portion provided in the outer rotor and a hole for accommodating the inner rotor. Then, in the conventional rotary pump, a seal portion for suppressing the flow of brake fluid on the outer periphery of the outer rotor is provided inside the accommodating recess provided on the side surface forming the hole of the central plate portion. The seal portion is composed of a rubber member having a spherical or substantially cylindrical shape and a resin member having a rectangular parallelepiped shape.

Japanese Unexamined Patent Publication No. 2000-355274

The seal portion is formed by inserting a rubber member (elastic member) and a resin member (seal member) along the axial direction into a recess extending along the axial direction in the central plate portion of the outer rotor. It is placed on the outer circumference. In this case, the rubber member and the resin member are inserted into the accommodating recess, for example, with the rubber member and the resin member integrally stacked.

By the way, in the above-mentioned conventional rotary pump, when the rubber member and the resin member are inserted, if the rubber member is spherical, the assembly position tends to be biased with respect to the accommodating recess and the side surface of the resin member, and the rubber member If is cylindrical, the rubber member tends to bend with insertion. As a result, in the above-mentioned conventional rotary pump, the contact state of the resin member with respect to the outer circumference of the outer rotor tends to vary, and the resin member may not exhibit sufficient sealing force. Further, the rubber member has a cylindrical shape, and for example, when the rubber member is inserted into the accommodating recess by pushing the end portion, it is necessary to insert the rubber member into the accommodating recess while suppressing bending, which may deteriorate the assembling property. is there.

In particular, in recent years, in a rotary pump provided in a vehicle braking device, a large flow rate is required in order to ensure good boost response in the braking device. In order to meet this requirement, in a rotary pump, lengthening the outer rotor and the inner rotor (that is, increasing the thickness along the axial direction) is one of the means. In this case, the depth of the accommodating recess becomes deeper, and as a result, the length of the sealing portion becomes longer, so that the sealing force and the assembling property deteriorate significantly due to the variation in the contact state described above.

The present invention has been made to solve the above problems, and an object of the present invention is to provide a rotary pump having a sealing portion capable of ensuring good sealing property and good assembly property.

In order to solve the above problems, the rotary pump is provided with an outer rotor having an inner tooth portion, an inner rotor having an outer tooth portion that meshes with the inner tooth portion, and a rotor chamber for accommodating the outer rotor and the inner rotor. , A casing having an accommodating recess extending in the axial direction of the outer rotor on the peripheral wall surface partitioning the rotor chamber, and a fluid in contact with the outer peripheral surface of the outer rotor and the inner surface of the accommodating recess while being accommodated in the accommodating recess. It has a seal member that prevents the outflow of the fluid and a length that is determined based on the axial tooth width in the inner tooth portion of the outer rotor, and elastically deforms the seal member while being accommodated in the accommodating recess. An elastic member including an elastic member that generates an urging force toward the outer peripheral surface of the outer rotor and the inner surface of the accommodating recess, or an integral member integrally formed by using the seal member and the elastic member. , A notch is provided.

According to this, the elastic member can have a length determined based on the tooth width of the inner tooth portion of the outer rotor. As a result, the elastic member can have an appropriate length with respect to the outer peripheral surface of the outer rotor, and is elastically deformed in the state of being accommodated in the accommodating recess so as to be directed toward the outer peripheral surface of the outer rotor and the inner surface of the accommodating recess. The seal member can be uniformly urged. As a result, the sealing member can be in uniform contact with the outer peripheral surface of the outer rotor, and a sufficient sealing force can be exhibited.

Further, a notch portion can be provided in the elastic member or the integral member integrally formed by using the seal member and the elastic member. As a result, during the assembling work, the operator or the assembling device inserts the elastic member or the integral member into the accommodating recess while holding the notch portion by using, for example, a predetermined assembling jig (chucking claw or the like). can do. Therefore, the operator or the assembling device can easily insert the elastic member of the single unit or the elastic member of the integral member while suppressing the bending into the accommodating recess, and good assembling property can be obtained.

It is an example of the block diagram of the brake device of the vehicle to which the hydraulic pressure control device provided with the rotary pump which concerns on embodiment of this invention is applied. It is a top view which shows the structure of a rotary pump. It is sectional drawing for demonstrating the structure of a rotary pump. It is sectional drawing for demonstrating the structure of the seal part. It is a top view for demonstrating the cutout part of the elastic member of FIG. It is a perspective view for demonstrating the assembly of the elastic member of FIG. It is sectional drawing which shows the structure of the elastic member which concerns on the 1st modification of embodiment. It is sectional drawing which shows the structure of the elastic member which concerns on the 2nd modification of embodiment. It is a top view for demonstrating the cutout part of the elastic member of FIG. It is a perspective view for demonstrating the elastic member which concerns on the 3rd modification of embodiment. It is sectional drawing for demonstrating the seal part which concerns on the 4th modification of embodiment. It is sectional drawing for demonstrating the seal part which concerns on the modification example of the 3rd modification. It is sectional drawing for demonstrating the seal part which concerns on the modification example of the 3rd modification. It is sectional drawing which shows the structure of the elastic member which concerns on other modification of embodiment. It is a top view for demonstrating the notch part of the elastic member which concerns on other modification of embodiment.

Hereinafter, embodiments will be described with reference to the drawings. In the following embodiments and the respective modifications, the same or equal parts are designated by the same reference numerals in the drawings. Further, each figure used for explanation is a conceptual view, and the shape of each part may not always be exact.

As shown in FIG. 1, the rotary pump 100 according to the embodiment is applied to a hydraulic pressure control device provided in a vehicle brake device S. First, the vehicle braking device S will be briefly described below.

(Configuration of vehicle brake device S)
As shown in FIG. 1, the brake device S includes a cylinder mechanism 1, a wheel cylinder 2, an actuator 3 as a hydraulic pressure control device, and a brake control device 4. Here, the rotary pump 100 is incorporated in the actuator 3.

The cylinder mechanism 1 includes a brake operating member 11, a brake booster 12, a master cylinder 13, and a master reservoir 14. The brake operating member 11 is stepped on, for example, by the driver.

The brake booster 12 is, for example, a negative pressure type brake booster, and doubles the pedaling force input to the brake operating member 11. Here, as the brake booster 12, in addition to the negative pressure type brake booster, an accumulator type that accumulates a hydraulic fluid such as brake fluid and generates a hydraulic pressure as needed, or a hydraulic pressure by a pump if necessary. It is possible to adopt an on-demand type that generates. In addition to the actuator 3, the rotary pump 100 can be used as the pump of the on-demand type brake booster described above.

The master cylinder 13 slidably accommodates the master piston 15 and the master piston 16 that partition the inside into the first master chamber 13a and the second master chamber 13b. The master reservoir 14 is a reservoir tank that has a conduit that communicates the first master chamber 13a and the second master chamber 13b and stores brake fluid that is a fluid. The master reservoir 14, the first master chamber 13a, and the second master chamber 13b are communicated with each other or cut off by the movement of the master pistons 15 and 16.

The wheel cylinder 2 is connected to the master cylinder 13 via an actuator 3, and has a cylinder member 21, a cylinder member 22, a cylinder member 23, and a cylinder member 24 arranged on each wheel of the vehicle. Specifically, the cylinder member 21 is arranged on the left rear wheel RL. The cylinder member 22 is arranged on the right rear wheel RR. The cylinder member 23 is arranged on the left front wheel FL. The cylinder member 24 is arranged on the right front wheel FR. The cylinder members 21 to 24 apply braking force to the left rear wheel RL, the right rear wheel RR, the left front wheel FL, and the right front wheel FR.

In the brake device S, when the driver steps on the brake operating member 11, the brake booster 12 boosts the pedaling force, and the master pistons 15 and 16 in the master cylinder 13 are pressed. As a result, a dynamic master cylinder pressure is generated in the first master chamber 13a and the second master chamber 13b. The master cylinder pressure is transmitted to the cylinder members 21 to 24 of the wheel cylinder 2 via the actuator 3.

The actuator 3 controls the hydraulic pressure of the cylinder members 21 to 24 (hereinafter, referred to as wheel pressure) in response to the instruction of the brake control device 4. The brake control device 4 is an electronic control unit including a computer whose main components are a CPU, ROM, RAM, and the like.

As shown in FIG. 1, the actuator 3 includes a hydraulic circuit 30. The hydraulic circuit 30 includes a first piping system 30a and a second piping system 30b. The first piping system 30a is a system that controls the hydraulic pressure (that is, wheel pressure) applied to the left rear wheel RL and the right rear wheel RR. The second piping system 30b is a system that controls the hydraulic pressure (that is, wheel pressure) applied to the left rear wheel RL and the right front wheel FR. As shown in FIG. 1, since the basic configurations of the first piping system 30a and the second piping system 30b are the same, the first piping system 30a will be described below as a representative, and the second piping system 30b will be described. The description will be omitted.

The first piping system 30a includes a main pipeline A, a differential pressure control valve 31, and pressure boosting valves 32 and 33. Further, the first piping system 30a includes a pressure reducing pipe line B and pressure reducing valves 34 and 35. Further, the first piping system 30a includes a pressure adjusting reservoir 36, a reflux pipe line C, and an auxiliary pipe line D.

The main pipeline A is a pipeline that connects the master cylinder 13 and the cylinder members 21 and 22. Specifically, as shown in FIG. 1, the main pipeline A has two pipelines A1 on the downstream side (cylinder members 21, 22 side) of the differential pressure control valve 31 so as to correspond to the cylinder members 21 and 22. It is branched to A2.

The differential pressure control valve 31 is provided in the main pipeline A and controls the main pipeline A in a communication state and a differential pressure state. Specifically, in the differential pressure state of the main pipeline A, the differential pressure control valve 31 has the hydraulic pressure of the portion of the main pipeline A on the master cylinder 13 side and the fluid of the cylinder member 21 and 22 sides of the main pipeline A. It is a solenoid valve configured to be able to control the differential pressure from the pressure.

When the differential pressure control valve 31 is energized according to the instruction of the brake control device 4 and controlled to the differential pressure state, the master cylinder 13 side which is the upstream side of the differential pressure control valve 31 and the cylinder member 21 which is the downstream side of the differential pressure control valve 31 , The differential pressure from the 22 side is controlled. The differential pressure control valve 31 is set so that the larger the applied (energized) control current, the larger the differential pressure on both sides. Further, the differential pressure control valve 31 is controlled to a continuous state when it is de-energized according to the instruction of the brake control device 4 in normal brake control except for automatic braking and sideslip prevention control, for example.

Here, when the differential pressure control valve 31 is in the differential pressure state, when the hydraulic pressure on the cylinder members 21 and 22 side becomes higher than the hydraulic pressure on the master cylinder 13 side, the cylinder members 21 and 22 side Brake fluid flow to the master cylinder 13 side is allowed. The predetermined pressure is a pressure determined by the differential pressure set by the control current. Therefore, when the differential pressure control valve 31 is controlled to the differential pressure state, the hydraulic pressure on both sides of the main pipeline A is not higher than the hydraulic pressure on the cylinder members 21 and 22 side by a predetermined pressure or more. Be maintained. That is, the differential pressure control valve 31 realizes a desired differential pressure state on both sides of the main pipeline A. As shown in FIG. 1, a check valve 31a is provided on the differential pressure control valve 31.

The pressure boosting valves 32 and 33 are solenoid valves that open and close according to the instructions of the brake control device 4, and are normally open valves that are in an open state (communication state) when the power is off. The pressure boosting valves 32 and 33 are energized mainly during depressurization control to reduce the wheel pressure to be in a closed state (cutoff state), and shut off the master cylinder 13 and the cylinder members 21 and 22. The pressure boosting valve 32 is arranged in the pipeline A1, and the pressure boosting valve 33 is arranged in the pipeline A2.

The pressure reducing line B is a line connecting the pressure boosting valve 32 and the cylinder member 21 in the line A1 and the pressure adjusting reservoir 36. Further, the pressure reducing line B is a line connecting the pressure increasing valve 33 and the cylinder member 22 in the line A2 and the pressure adjusting reservoir 36.

The pressure reducing valves 34 and 35 are solenoid valves that open and close according to the instruction of the brake control device 4, and are normally closed valves that are closed (shut off) when the power is off. The pressure reducing valves 34 and 35 are mainly energized during decompression control to be in an open state (communication state), and the cylinder members 21 and 22 and the pressure adjusting reservoir 36 are communicated with each other via the pressure reducing pipe line B. The pressure reducing valve 34 is arranged in the pressure reducing pipe line B on the cylinder member 21 side, and the pressure reducing valve 35 is arranged in the pressure reducing pipe line B on the cylinder member 22 side. The pressure adjusting reservoir 36 is a reservoir tank having a cylinder, a piston, and an urging member, and capable of storing brake fluid.

The reflux pipe C as a flow path connects the pressure reducing pipe B (or the pressure adjusting reservoir 36) and the portion of the main pipe A between the differential pressure control valve 31 and the pressure increasing valves 32 and 33. Is. In this embodiment, the rotary pump 100 is provided in the reflux line C. The rotary pump 100 causes the brake fluid (fluid) to flow from the pressure regulating reservoir 36 to the master cylinder 13 side or the cylinder members 21 and 22 sides via the reflux pipe C. The motor 37 is energized and driven via a relay (not shown) according to the instruction of the brake control device 4. The configuration and operation of the rotary pump 100 will be described in detail later.

Further, in the return pipe line C, a damper 38 and a check valve 39 are arranged on the discharge port side of the rotary pump 100, that is, on the discharge side passage C1 of the return pipe line C. The discharge side passage C1 is a portion of the reflux pipe C that connects the discharge port of the rotary pump 100 and the main pipe A (the portion between the differential pressure control valve 31 and the pressure boosting valves 32 and 33). The damper 38 is a damper device that absorbs the discharge pulsation (fluctuation of hydraulic pressure on the high pressure side) of the rotary pump 100. The check valve 39 is a valve mechanism that allows the inflow of brake fluid from the differential pressure control valve 31 side to the rotary pump 100 side in the discharge side passage C1. Further, the check valve 39 exerts the function of a switching orifice that switches the permitted inflow amount of the brake fluid from the rotary pump 100 side to the differential pressure control valve 31 side between a small flow rate and a large flow rate according to the pressure. It has become.

The auxiliary pipeline D is a pipeline that connects the pressure regulating reservoir 36 and the upstream side (or master cylinder 13) of the differential pressure control valve 31 in the main pipeline A. By driving the rotary pump 100, the brake fluid of the master cylinder 13 is moved to the downstream side of the differential pressure control valve 31 in the main pipeline A, that is, to the differential pressure control valve 31 via the auxiliary pipeline D and the pressure regulating reservoir 36. It is discharged to the portion between the cylinder members 21 and 22. As a result, the wheel pressure is increased during vehicle driving control such as automatic braking and sideslip prevention control. Therefore, the actuator 3 functions as an automatic brake operating device and a skid prevention device under the control of the brake control device 4.

(Structure of rotary pump 100)
The rotary pump 100 is a self-priming trochoidal pump driven by a motor 37. As shown in FIGS. 2 and 3, the rotary pump 100 is configured such that the outer rotor 102 and the inner rotor 103 are assembled in a state where their central axes are eccentric inside the rotor chamber 101a of the casing 101. There is. An internal tooth portion 102a is provided on the inner circumference of the outer rotor 102. An outer tooth portion 103a is provided on the outer periphery of the inner rotor 103. Further, a fitting hole 103b that fits with the drive shaft of the motor 37 is provided at the center of the inner rotor 103.

The outer rotor 102 and the inner rotor 103 form a gap portion 104 when the inner tooth portion 102a and the outer tooth portion 103a mesh with each other. Here, as shown in FIG. 2, in the rotary pump 100, the gap portion 104 is formed by the inner tooth portion 102a of the outer rotor 102 and the outer tooth portion 103a of the inner rotor 103, and a partition plate (crescent) is formed. It is a multi-tooth trochoid type pump that does not have. Further, in order to transmit the rotational torque of the inner rotor 103, the inner rotor 103 (outer tooth portion 103a) and the outer rotor 102 (inner tooth portion 102a) have a plurality of contact points.

As shown in FIG. 3, the casing 101 is composed of a main body portion 105 and a plate portion 106 arranged so as to sandwich the outer rotor 102 and the inner rotor 103 from both sides. The main body 105 is provided with a recess 105a for accommodating the outer rotor 102 and the inner rotor 103, and the recess 105a forms a rotor chamber 101a together with the plate 106. Further, a central hole 105b is formed in the central portion of the main body portion 105 to be inserted into the rotor chamber 101a. The drive shaft of the motor 37 is inserted through the center hole 105b.

As a result, the outer rotor 102 and the inner rotor 103 become rotatable inside the rotor chamber 101a of the casing 101 by transmitting the driving force of the motor 37. That is, the outer rotor 102 and the inner rotor 103 rotate around different rotation axes (in other words, eccentrically) inside the rotor chamber 101a.

Then, in the rotary pump 100, the brake fluid is sucked into the gap 104 whose volume expands from the outside (specifically, the pressure adjusting reservoir 36) by rotating the outer rotor 102 and the inner rotor 103, and at the same time. The sucked brake fluid is pressurized from the gap portion 104 whose volume is reduced and discharged to the outside (specifically, the auxiliary pipe D). Here, the volume of the gap 104 is set based on, for example, the amount of brake fluid required when the braking device S automatically brakes. Specifically, it is appropriately set based on the axial depth of the rotor chamber 101a, in other words, the axial tooth width (thickness) of the inner tooth portion 102a of the outer rotor 102 and the outer tooth portion 103a of the inner rotor 103. Will be done.

Of the plurality of gaps 104, the confinement portion on the side where the volume is maximum and the confinement portion on the side where the volume is minimum are provided in the casing 101 and are suction ports for sucking brake fluid. It is designed so that it does not communicate with either the discharge port (not shown) or the discharge port (not shown) that discharges brake fluid. As a result, in the rotary pump 100, the differential pressure between the suction pressure at the suction port and the discharge pressure at the discharge port is maintained.

Further, as shown in FIGS. 2 and 3, the peripheral wall surface 105a1 extending in the circumferential direction to form the recess 105a of the main body 105 and partitioning the rotor chamber 101a has a housing recess 105c extending in the axial direction. Is formed. A seal portion 107 for preventing the outflow of brake fluid on the outer periphery of the outer rotor 102 and preventing the outflow of brake fluid in the plate portion 106 is housed inside the accommodating recess 105c. The seal portion 107 seals a portion where the brake fluid becomes low pressure and a portion where the brake fluid becomes high pressure on the outer circumference of the outer rotor 102.

As shown in FIGS. 2 to 5, the seal portion 107 is composed of a resin member 107a as a prismatic seal member and a rubber member 107b as a columnar (specifically, columnar) elastic member. There is. The resin member 107a and the rubber member 107b have a length substantially matching the tooth width (thickness) of the inner tooth portion 102a of the outer rotor 102 in a state of being housed (assembled) in the housing recess 105c.

As shown in FIGS. 3 and 4, the resin member 107a is directed toward the outer peripheral surface 102b of the outer rotor 102 that is rotated in the arrow direction (see FIG. 4) by the rubber member 107b while being housed in the housing recess 105c. At the same time, it is urged toward the inner surface 105c1 of the accommodating recess 105c. As a result, the resin member 107a prevents the brake fluid from flowing out.

As shown in FIGS. 3 and 4, the rubber member 107b is elastically deformed while being housed in the housing recess 105c, and the resin member 107a is attached toward the outer peripheral surface 102b of the outer rotor 102 and the inner surface 105c1 of the housing recess 105c. Generates an energizing force. Here, the rubber member 107b has a length determined based on the length of the internal tooth portion 102a of the outer rotor 102. As a result, the rubber member 107b housed in the housing recess 105c evenly contacts the inner surface 105c1 of the housing recess 105c in the axial direction and evenly contacts the side surface of the resin member 107a. As a result, in the length direction (direction corresponding to the axial direction) of the resin member 107a, the rubber member 107b can uniformly urge the resin member 107a toward the outer peripheral surface 102b of the outer rotor 102, and the resin member 107a can be uniformly urged. Can exert good sealing power.

Further, the outer peripheral surface 107b1 of the rubber member 107b is provided with a groove-shaped notch 107b2 so as to be parallel to the axial direction. The notch 107b2 extends axially to reach at least one end of the rubber member 107b, both ends in the present embodiment. That is, as shown in FIG. 3, the notch portion 107b2 has the same length as the rubber member 107b. As a result, as will be described later, after the rubber member 107b is inserted into the accommodating recess 105c and assembled, the jig J (see FIG. 6) can be removed from the accommodating recess 105c without interfering with the rubber member 107b. it can.

Further, as shown in FIGS. 4 and 5, a plurality of notches 107b2 are provided (four in the present embodiment) so as to be evenly spaced in the circumferential direction of the rubber member 107b. As a result, as will be described later, when the rubber member 107b is inserted into the accommodating recess 105c and assembled, the rubber member 107b can be stably held when the jig J grips the notch portion 107b2. Further, as shown in FIG. 5, the notch portion 107b2 is formed so that the depth L of the rubber member 107b in the radial direction is smaller than the radius r of the rubber member 107b. As a result, the rubber member 107b provided with the notch portion 107b2 can generate a desired urging force, and a plurality of notch portions 107b2 can be provided in the circumferential direction of the rubber member 107b.

Here, the assembly of the seal portion 107, specifically, the resin member 107a which is a seal member and the rubber member 107b which is an elastic member into the accommodating recess 105c will be described. First, at the time of assembly, a lubricating oil such as grease is applied to the surface of the rubber member 107b. As a result, the frictional resistance between the rubber member 107b and the inner peripheral surface of the accommodating recess 105c when the rubber member 107b is inserted into the accommodating recess 105c is reduced.

Then, for example, in a state where the resin member 107a is housed in the storage recess 105c at a predetermined position (see FIG. 4 and the like), as shown in FIG. 6, the outer peripheral surface 107b1 of the rubber member 107b is formed by the chuck claw of the jig J or the like. The provided notch 107b2 is gripped. Then, the rubber member 107b is inserted along the axial direction into the inside of the accommodating recess 105c.

By the way, the jig J can stably hold the rubber member 107b by gripping the notch portion 107b2 as compared with the case of gripping the rubber member formed in a simple columnar or cylindrical shape. Therefore, during the assembling work, the operator or the assembling device (robot arm) can be inserted into the accommodating recess 105c extremely easily and smoothly without bending the rubber member 107b. Therefore, good assembling property can be ensured.

Further, the radial depth L of the notch portion 107b2 is set to be smaller than the radius r of the rubber member 107b. As a result, when the jig J is removed from the housing recess 105c after the rubber member 107b is inserted into the housing recess 105c, for example, the chuck claw of the jig J can be opened. Therefore, the rubber member 107b can be maintained in a state of being housed in the housing recess 105c without bending, and the jig J can be prevented from interfering with the inner surface 105c1 of the housing recess 105c. Also by this, good assembling property can be ensured.

(Operation of rotary pump 100)
Next, the operation of the rotary pump 100 will be described. In the rotary pump 100, when the drive shaft is rotated by the drive of the motor 37, the inner rotor 103 is rotated. When the inner rotor 103 rotates, the outer rotor 102 also rotates in the same direction due to the meshing of the inner tooth portion 102a and the outer tooth portion 103a. At this time, the rotary pump 100 sucks the brake fluid from the pressure adjusting reservoir 36 and sucks the brake fluid from the pressure adjusting reservoir 36 because the volume of each gap 104 changes in size while the outer rotor 102 and the inner rotor 103 make one rotation. Brake fluid is discharged toward D. Therefore, the cylinder pressure supplied to the wheel cylinder 2 is increased by the brake fluid that is pressurized and discharged.

Further, in the rotary pump 100, an suction pressure due to sucking the brake fluid and a discharge pressure due to discharging the brake fluid are generated on the outer circumference of the outer rotor 102. That is, a low pressure portion and a high pressure portion are generated on the outer circumference of the outer rotor 102. Correspondingly, as described above, the seal portion 107 separates the low pressure portion and the high pressure portion on the outer circumference of the outer rotor 102. Therefore, the brake fluid is prevented from leaking from the high-pressure portion that discharges the brake fluid through the outer peripheral surface 102b of the outer rotor 102 toward the low-pressure portion that sucks the brake fluid.

Further, in the seal portion 107, the resin member 107a is urged by the rubber member 107b toward the outer peripheral surface 102b of the outer rotor 102 and the inner surface 105c1 of the accommodating recess 105c. Therefore, the outer rotor 102 is pressed by the resin member 107a, and a load acts in the gap 104 in the direction in which the tooth tip gap between the inner tooth portion 102a of the outer rotor 102 and the outer tooth portion 103a of the inner rotor 103 is reduced. This also prevents the brake fluid from leaking through the tooth tip gap between the inner tooth portion 102a of the outer rotor 102 and the outer tooth portion 103a of the inner rotor 103.

As can be understood from the above description, the rotary pump 100 according to the present embodiment includes an outer rotor 102 having an inner tooth portion 102a, an inner rotor 103 having an outer tooth portion 103a that meshes with the inner tooth portion 102a, and an outer. A rotor chamber 101a for accommodating the rotor 102 and the inner rotor 103 is provided, and a casing 101 having an accommodating recess 105c extending in the axial direction of the outer rotor 102 on the peripheral wall surface 105a1 for partitioning the rotor chamber 101a, and the accommodating recess 105c. The resin member 107a as a sealing member that comes into contact with the outer peripheral surface 102b of the outer rotor 102 and the inner surface 105c1 of the accommodating recess 105c to prevent the outflow of the brake fluid, which is a fluid, and the inner teeth of the outer rotor 102. The portion 102a has a length determined based on the tooth width in the axial direction, and is elastically deformed while being accommodated in the accommodating recess 105c to elastically deform the resin member 107a to the outer peripheral surface 102b and the accommodating recess 105c of the outer rotor 102. The rubber member 107b is provided with a rubber member 107b as an elastic member for generating an urging force toward the inner surface 105c1, and the rubber member 107b is provided with a notch portion 107b2.

According to this, the rubber member 107b can have a length determined based on the tooth width of the inner tooth portion 102a of the outer rotor 102. As a result, the rubber member 107b can have an appropriate length with respect to the outer peripheral surface 102b of the outer rotor 102, and is elastically deformed while being accommodated in the accommodating recess 105c to form the outer peripheral surface 102b and the outer rotor 102. The resin member 107a can be uniformly urged toward the inner surface 105c1 of the accommodating recess 105c. As a result, the resin member 107a can be in uniform contact with the outer peripheral surface 102b of the outer rotor, and a sufficient sealing force can be exhibited.

Further, the rubber member 107b may be provided with a notch portion 107b2. As a result, during the assembling work, the operator or the assembling device (robot arm or the like) inserts the rubber member 107b into the accommodating recess 105c while holding the notch 107b2 by using the chucking claw of the jig J or the like. Can be assembled. Therefore, the operator or the assembling device can easily insert the rubber member 107b into the accommodating recess 105c while suppressing bending, and good assembling property can be obtained.

In this case, the notch 107b2 extends parallel to the axial direction on the outer peripheral surface 107b1 of the rubber member 107b so as to reach at least one end. The notch portion 107b2 is formed so that the depth L of the rubber member 107b in the radial direction is smaller than the radius r of the rubber member 107b.

According to these, when the rubber member 107b is inserted into the accommodating recess 105c and assembled, and then the grip by the jig J is released and the jig J is removed from the accommodating recess 105c, the rubber member 107b and the jig J Interference can be prevented. As a result, the rubber member 107b inserted into the accommodating recess 105c is maintained in a state in which the occurrence of bending is suppressed, and as a result, the resin member 107a can be uniformly urged.

Further, in these cases, a plurality of notch portions 107b2 are provided at equal intervals in the circumferential direction of the rubber member 107b.

According to this, when the rubber member 107b is inserted into the accommodating recess 105c and assembled, the jig J can stably hold the rubber member 107b by gripping the notch portion 107b2. Therefore, the rubber member 107b can be accurately inserted into the accommodating recess 105c and assembled.

(First modification)
In the above embodiment, the outer peripheral surface 107b1 of the rubber member 107b is provided with four notches 107b2 in the circumferential direction. However, the number of notches 107b2 provided in the circumferential direction on the outer peripheral surface 107b1 is not limited to four. For example, as shown in FIG. 7, it is also possible to provide three recessed notches 107b2 in the circumferential direction on the outer peripheral surface 107b1 of the rubber member 107b. Alternatively, although not shown, it is also possible to provide two or five or more notches 107b2 in the circumferential direction of the rubber member 107b.

In this way, even when the number of the notch portions 107b2 is changed, the rubber member 107b can be stably held by the jig J gripping the notch portion 107b2, and the rubber member 107b can be held extremely without bending. It can be easily and smoothly inserted into the accommodating recess 105c. Therefore, good assembling property can be ensured.

(Second modification)
In the above embodiment and the above first modification, a plurality of notches 107b2 are provided in the circumferential direction on the outer peripheral surface 107b1 of the cylindrical rubber member 107b. Instead, as shown in FIGS. 8 and 9, when the rubber member 107b has a hollow cylindrical shape having a through hole penetrating in the axial direction, the inner peripheral surface 107b3 of the rubber member 107b formed by the through hole is formed. It is also possible to provide a notch portion 107b4 in the. In this second modification, three notches 107b4 are provided at equal intervals in the circumferential direction of the inner peripheral surface 107b3.

As described above, when the notch portion 107b4 is provided on the inner peripheral surface 107b3 of the rubber member 107b, that is, even if the notch portion 107b4 extends in the axial direction and is included inside the rubber member 107b, for example, The rubber member 107b can be stably held by inserting a shaft-shaped jig and gripping (or engaging with the notch 107b4) the notch 107b4. As a result, even in this second modification, the rubber member 107b can be inserted into the accommodating recess 105c extremely easily and smoothly without bending. Therefore, good assembling property can be ensured. In this case, the notch 107b4 may be omitted, and the notch extending in the axial direction and included inside the rubber member 107b may be a through hole penetrating in the axial direction.

(Third variant)
In the above-described embodiment and each of the above-described modifications, the length of the notch portion 107b2 or the notch portion 107b4 in the axial direction is made the same as the length of the rubber member 107b. Instead of this, if it is formed so as to reach the end of the rubber member 107b, the length x in the axial direction of the notch portion 107b2 is set to the length x of the notch portion 107b2 as illustrated in FIG. It is also possible to make it shorter than the length y in the axial direction of. In this case, at the time of assembling, the chuck claw of the jig J can push the end portion 107b21 on the side opposite to the end portion of the rubber member 107b in the notch portion 107b2, and the assembling property is further improved. In order to urge the resin member 107a evenly on the outer peripheral surface 102b of the outer rotor 102 in the axial direction, as shown in FIG. 10, the notch 107b2 (or the notch 107b4) is provided at both ends of the rubber member 107b. It is provided so as to be symmetrical.

As described above, even when the length x of the notch portion 107b2 (or the notch portion 107b4) is made shorter than the length y of the rubber member 107b, the same effect as that of the above embodiment and each of the above modifications is obtained. Is obtained.

(Fourth modification)
In the above-described embodiment and each of the above-described modifications, the seal portion 107 is composed of an independent resin member 107a and a rubber member 107b, respectively. Instead of this, it is also possible to form the seal portion 107 by an integral member integrally formed by using the seal member and the elastic member. Specifically, as shown in FIGS. 11 to 13, the resin member 108a as a seal member and the rubber member 108b as an elastic member are made into an integral member 108 by, for example, two-color molding or the like to form a seal portion 107. It is also possible to do.

In this case, a notch is provided in at least one of the resin member 108a and the rubber member 108b, and the integrated member 108 can be inserted (assembled) into the accommodating recess 105c. Specifically, as shown in FIG. 11, it is possible to provide the notch portion 108b2 corresponding to the notch portion 107b2 of the above embodiment on the outer peripheral surface 108b1 of the rubber member 108b. In this case, the notch 108b2 can be gripped and the integrated member 108 can be inserted (assembled) into the accommodating recess 105c.

Further, as shown in FIG. 12, when it is possible to provide a through hole in the resin member 108a, the notch portion 108a1 corresponding to the notch portion 107b4 provided in the rubber member 107b in the second modification is provided. Can be provided. In this case, the notch 108b2 can be gripped and the integrated member 108 can be inserted (assembled) into the accommodating recess 105c. Further, as shown in FIG. 13, the resin member 108a is provided with the notch portion 108a1, and the rubber member 108b is provided with the notch portion 108b4 corresponding to the notch portion 107b4 provided in the rubber member 107b in the second modification. It is also possible to provide it. In this case, the notch portion 108a1 provided in the resin member 108a and the notch portion 108b2 provided in the rubber member 108b can be grasped, and the integrated member 108 can be inserted (assembled) into the accommodating recess 105c. Therefore, in this fourth modification, the same effects as those of the above-described embodiment and each of the above-mentioned modifications can be obtained.

The practice of the present invention is not limited to the above-described embodiment and each of the above-mentioned modifications, and various modifications can be made as long as the object of the present invention is not deviated.

For example, in the above embodiment, the rubber member 107b is cylindrical, and the notch portion 107b2 is provided so as to reach the end portion on the outer peripheral surface 107b1 and parallel to the axial direction. Instead of this, as shown in FIG. 14, it is also possible to provide a notch portion 109b2 parallel to the axial direction on the outer peripheral surface 109b1 of the irregular columnar rubber member 109b having a plurality of spherical portions in the axial direction.

In this case, even if the notch 109b2 does not reach the end, it is possible to grasp the notch 109b2 with a jig and insert (assemble) it into the accommodating recess 105c, and insert (assemble) it. After that, the jig can be removed without interfering with the rubber member 109b and the accommodating recess 105c. Therefore, even in this case, the same effect as that of the above embodiment can be obtained.

Further, in the above-described embodiment and each modification, the notch portion 107b2 and the like are notched so as to form one (one) groove. Instead of this, as shown in FIG. 15, it is also possible to provide the notch portion 107b2 or the like by notching so as to form a groove shape of a pair of two (a pair of two). That is, the notch portion is composed of one or a plurality of notches.

Further, in the above-described embodiment and each of the above-described modifications, the notch portions 107b2 and the like are provided at equal intervals in the circumferential direction. However, it is also possible to provide the notches 107b2 and the like at unequal intervals (discontinuous) in the circumferential direction.

Further, in the third modification, the cutout portion 107b2 having a length x shorter than the length y of the rubber member 107b is provided so as to reach the end portion of the rubber member 107b. In this case, the notches 107b2 are provided at equal intervals in the circumferential direction.

Alternatively, it is possible to provide a notch 107b2 that does not reach the end and has a short length x so as to be continuous in the circumferential direction. That is, it is also possible to provide the notch 107b2 along the circumferential direction (for example, in an annular shape). In this case, when the jig grips the notch 107b2 and inserts (assembles) the rubber member 107b into the housing recess 105c, and when the jig is removed from the housing recess 105c, the inside of the housing recess 105c. By utilizing the gap formed in the above, it is possible to prevent the jig from interfering with the rubber member 107b and the accommodating recess 105c.

Further, in the third modification, the cutout portion 107b2 (notch portion 107b4) having a length x shorter than the length y of the rubber member 107b is formed into the rubber member 107b so as to reach the end portion of the rubber member 107b. It is provided so that it is symmetrical at both ends of the rubber. However, it is also possible to provide the notch 107b2 (notch 107b4) only at one end of the rubber member 107b.

Further, in the above-described embodiment and each of the above-described modified examples, the notch portion 107b2 and the like are provided so as to be parallel to the axial direction. However, the notch 107b2 and the like are not limited to extending so as to be parallel to the axial direction. For example, if the shape of the chuck claw of the jig J is substantially triangular in the axial direction, it is not parallel to the axial direction as shown by the broken line in FIG. 10 according to the shape of the chuck claw of the jig J. It is also possible to provide the notch 107b2 so as not to be present.

Further, in the above-described embodiment and each of the above-described modifications, it is assumed that the rubber member 107b and the rubber member 108b are columnar having a circular cross-sectional shape on a plane orthogonal to the axial direction. However, as long as the rubber member 107b and the rubber member 108b are columnar, the cross-sectional shape is not limited to a circular shape, and may be, for example, a polygon such as a triangle or a quadrangle, or an elliptical shape.

Further, in the above-described embodiment and each of the above-described modifications, the rotary pump 100 is assembled to the brake device S of the vehicle to pressurize and discharge the brake fluid which is a fluid. Alternatively, the rotary pump 100 can be assembled into a device other than the brake device to suck, pressurize, and discharge the desired fluid.

Further, in the above-described embodiment and each of the above-described modifications, in the rotary pump 100, the driving force of the motor 37 is transmitted to the inner rotor 103, so that the outer rotor 102 and the inner rotor 103 rotate to be a fluid brake. The fluid was inhaled, pressurized, and discharged. Instead of this, a drive source other than the motor 37 may be used as long as the driving force can be transmitted (output) so that the inner rotor 103 (outer rotor 102) of the rotary pump 100 rotates.

100 ... rotary pump, 101 ... casing, 101a ... rotor chamber, 102 ... outer rotor, 102a ... inner tooth part, 102b ... outer peripheral surface, 103 ... inner rotor, 103a ... outer tooth part, 103b ... fitting hole, 104 ... Void part, 105 ... Main body part, 105a ... Recessed part, 105a1 ... Peripheral wall surface, 105b ... Center hole, 105c ... Accommodating recessed part, 105c1 ... Inner surface, 106 ... Plate part, 107 ... Seal part, 107a ... Resin member (seal member), 107b ... Rubber member (elastic member), 107b1 ... Outer surface, 107b2 ... Notch, 107b21 ... Termination, 107b3 ... Inner peripheral surface, 107b4 ... Notch, 108 ... Integrated member, 108a ... Resin member (seal member) , 108a1 ... Notch, 108b ... Rubber member (elastic member), 108b1 ... Outer surface, 108b2 ... Notch, 108b3 ... Inner peripheral surface, 108b4 ... Notch, 109b ... Rubber member (elastic member), 109b1 ... Outer peripheral surface, 109b2 ... Notch, 3 ... Actuator (hydraulic pressure control device), 30 ... Hydraulic circuit, 32, 33 ... Pressure boosting valve (electromagnetic valve), 34, 35 ... Pressure reducing valve (electromagnetic valve), 36 ... Pressure regulation Reservoir, 37 ... motor, C ... recirculation pipeline, S ... braking device, L ... depth, r ... radius, x ... (notch) length, y ... (rubber member) length

Claims (7)

Outer rotor with internal teeth and
An inner rotor having an outer tooth portion that meshes with the inner tooth portion,
A casing provided with a rotor chamber for accommodating the outer rotor and the inner rotor, and a casing having an accommodating recess extending in the axial direction of the outer rotor on the peripheral wall surface for partitioning the rotor chamber.
A seal member that comes into contact with the outer peripheral surface of the outer rotor and the inner surface of the housing recess to prevent fluid from flowing out while being housed in the housing recess.
The outer rotor has a length determined based on the axial tooth width of the inner tooth portion, and is elastically deformed while being accommodated in the accommodating recess to form the seal member of the outer rotor. An elastic member that generates an urging force that urges the outer peripheral surface and the inner surface of the accommodating recess is provided.
A rotary pump in which a notch is provided in the elastic member, or the seal member and the integral member integrally formed by using the elastic member. The rotary pump according to claim 1, wherein the notch is provided in the elastic member and extends in the axial direction so as to reach at least one end of the elastic member. The notch is
The rotary pump according to claim 2, wherein a plurality of rotary pumps are provided in the circumferential direction of the elastic member and are formed so that the depth of the elastic member in the radial direction is smaller than the radius of the elastic member. The notch is
The rotary pump according to claim 3, which is provided at equal intervals in the circumferential direction of the elastic member. The notch is
The rotary pump according to any one of claims 1 to 4, which is provided on the outer peripheral surface of the elastic member. The rotary pump according to any one of claims 1 to 4, wherein the elastic member extends in the axial direction and has the notch portion included inside the elastic member. The length of the notch in the axial direction is
The rotary pump according to any one of claims 1 to 6, which is shorter than the length of the elastic member in the axial direction.

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