JP2014173566A - Rotary pump device and brake device for vehicle including the same - Google Patents

Abstract

PROBLEM TO BE SOLVED: To provide a rotary pump device in which fluid leakage hardly occurs in space between a seal member and an oil seal, and in which the fluid blocked in the space hardly leaks outside from the oil seal.SOLUTION: By a two-stage seal structure of a seal member 130 and an oil seal 140, while brake fluid leakage from a first chamber to a second chamber is being suppressed, the brake fluid leakage from the second chamber to the outside is suppressed. Furthermore, at a contact part between a resin ring 131 and a shaft 54, a spiral groove 131h is formed on an inner peripheral surface of the resin ring 131. Thereby, a fluid force can be made to act in the direction pushing back the brake fluid entered inside the spiral groove 131h to the first chamber side according to the rotation of the shaft 54. Therefore, the brake fluid leakage from the first chamber to the second chamber becomes even less likely to occur.

Description

  The present invention has a sealing structure in which a seal member having a resin ring and a rubber ring is arranged in a gap between a housing housing a rotary pump and a shaft, and the resin ring is closely attached to the shaft side to perform sealing. The present invention relates to a type pump device and a vehicular brake device including the same.

  Conventionally, in Patent Document 1, a seal member having a resin ring and a rubber ring is disposed in a gap between a housing and a shaft, and an oil seal is disposed outside the seal member, thereby providing a two-stage seal structure. A rotary pump device has been proposed. In this rotary pump device, the resin ring disposed on the inner peripheral side is pressed against the shaft and sealed by the rubber ring disposed on the outer peripheral side. As a result, the brake fluid pressure is reduced by sealing the fluid leaking from the pump side through the gap between the housing and the shaft, that is, the brake fluid, with the seal member. Further, by providing an oil seal on the outside of the seal member, that is, on the side further away from the pump than the seal member, higher sealing performance can be obtained.

  In such a structure, an oil film is formed between the shaft and the seal member due to the rotation of the shaft, and the pressure applied to the shaft from the seal member is distributed, i.e., there is a variation, so that the brake fluid flows between the seal member and the oil seal. Pumped in between. At this time, if the pressure of the brake fluid blocked between the seal member and the oil seal becomes higher than the opening pressure of the oil seal, the brake fluid leaks from the oil seal to the outside. For this reason, when the brake fluid pressure between the pump and the seal member becomes low at the end of the pump operation, the brake fluid is returned to the pump side through the outer peripheral side of the seal member, that is, the gap between the rubber ring and the housing. It is supposed to flow.

JP 2012-063003 A

  However, before the brake fluid is returned to the pump side from the space between the seal member and the oil seal, the pressure of the brake fluid blocked between the seal member and the oil seal is higher than the release pressure of the oil seal. When it becomes high, the brake fluid leaks from the oil seal to the outside. In particular, during anti-skid (ABS) control, the brake fluid pressure discharged from the wheel cylinder for pressure reduction is applied between the rotary pump and the seal member. Brake fluid easily leaks into the space between the seals. When the operation time of the rotary pump becomes longer, the pressure of the brake fluid blocked in the space between the seal member and the oil seal becomes higher, and the brake fluid leaks from the oil seal to the outside easily. .

  In view of the above, the present invention makes it difficult for fluid leakage to occur in the space between the seal member and the oil seal, and makes it difficult for fluid blocked in this space to leak from the oil seal to the outside. An object of the present invention is to provide a rotary pump device that can perform the above-described operation.

  In order to achieve the above object, according to the first aspect of the present invention, a case (71a-71d) in which holes (72a-72d) through which a shaft (54) for driving the rotary pump (19, 39) is inserted is formed. ), A seal member (130) having a ring-shaped resin ring (131) and a rubber cup (132), and an oil seal (140) disposed on the opposite side of the rotary pump from the seal member. The first chamber is a space between the rotary pump and the seal member, and the second chamber is a space between the seal member and the oil seal, so that fluid leaks from the first chamber to the second chamber. When the fluid leaks into the second chamber, it is sealed with an oil seal, and when the fluid pressure in the first chamber falls below the fluid pressure in the second chamber, the rubber cup and the hole Flow in the second chamber through the inner surface In the rotary pump device configured to return the air to the first chamber, the resin ring has a spiral start position at the position where the resin ring abuts the outer peripheral surface of the shaft. The second chamber side is a spiral end position, and a spiral groove (131h) wound in the direction opposite to the rotation direction of the shaft from the spiral start position to the spiral end position is formed.

  As described above, since the spiral groove is formed at a position in the resin ring that contacts the outer peripheral surface of the shaft, the fluid that has entered the spiral groove with the rotation of the shaft flows in the direction of pushing back to the first chamber side. Physical strength can be applied. Thereby, it becomes possible to suppress the fluid leakage from the first chamber to the second chamber. Furthermore, if a fluid leak occurs from the first chamber to the second chamber, the inner peripheral surfaces of the seal member and the case hole when the fluid pressure in the first chamber is lower than the fluid pressure in the second chamber. The fluid is allowed to flow back through. For this reason, it becomes possible to further suppress the fluid that enters the second chamber and is blocked by the oil seal from leaking from the oil seal to the outside.

  In the invention according to claim 2, the shaft has a position where the first chamber side is set as the spiral start position and the second chamber side is set as the spiral end position at a position in contact with the inner peripheral surface of the resin ring. A spiral groove (54c) wound in the same direction as the rotation direction of the shaft toward the spiral end position is formed.

  Thus, even if the spiral groove is formed on the outer peripheral surface of the shaft, the same effect as in the first aspect can be obtained.

  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 of the brake device for vehicles to which the rotary pump apparatus concerning 1st Embodiment of this invention is applied. 2 is a cross-sectional view of a rotary pump device including a pump body 100 including gear pumps 19 and 39 and a motor 60. FIG. It is sectional drawing on the III-III line of FIG. It is a partial expanded sectional view of the sealing member 130 with which the rotary pump apparatus was equipped. It is a partial expanded sectional view of the resin ring 131 before the assembly | attachment to a rotary pump apparatus. It is a partial expanded sectional view of the rubber cup 132 before the assembly | attachment to a rotary pump apparatus. It is the elements on larger scale which showed a mode when rubber cup 132 was inserted in resin ring 131. It is a partial expanded sectional view of the sealing member 130 with which the rotary pump apparatus concerning 2nd Embodiment of this invention was equipped.

  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)
DESCRIPTION OF THE PREFERRED EMBODIMENTS Embodiments shown in the drawings will be described below. First, a basic configuration of a vehicle brake device to which a rotary pump device according to an embodiment of the present invention is applied will be described with reference to FIG. Here, in the front-wheel drive four-wheeled vehicle, the vehicle brake device according to the present invention is applied to a vehicle 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. An example will be described, but the present invention can also be applied to vehicles such as front and rear piping.

  As shown in FIG. 1, the vehicle brake device 1 includes a brake pedal 11 serving as a brake operation member, a booster device 12, an M / C (master cylinder) 13, and a W / C (wheel cylinder) 14. , 15, 34, 35 and an actuator 50 for controlling the brake fluid pressure. A brake ECU 70 is assembled to the actuator 50, and the brake ECU 70 controls the braking force generated by the vehicle brake device 1.

  The brake pedal 11 is connected to the booster device 12 and the M / C 13, and when the driver depresses the brake pedal 11 and operates it, the pedaling force is boosted by the booster device 12 and disposed in the M / C 13. The master pistons 13a and 13b are pressed. As a result, the same M / C pressure is generated in the primary chamber 13c and the secondary chamber 13d defined by the master pistons 13a and 13b. The M / C pressure generated in the M / C 13 is transmitted to each of the W / Cs 14, 15, 34, and 35 through the actuator 50 constituting the hydraulic pressure path.

  The M / C 13 is connected to a master reservoir 13e having a passage communicating with the primary chamber 13c and the secondary chamber 13d. The master reservoir 13e supplies brake fluid into the M / C 13 and stores excess brake fluid in the M / C 13.

  The actuator 50 has a first piping system 50a and a second piping system 50b. The first piping system 50a controls the brake fluid pressure applied to the right front wheel FR and the left rear wheel RL, and the second piping system 50b controls the brake fluid pressure applied to the left front wheel FL and the right rear wheel RR. Systematic.

  Hereinafter, the first and second piping systems 50a and 50b will be described. However, since the first piping system 50a and the second piping system 50b have substantially the same configuration, the first piping system 50a will be described here. For the second piping system 50b, refer to the first piping system 50a.

  The first piping system 50a transmits the M / C pressure described above to the W / C 14 provided on the right front wheel FR and the W / C 15 provided on the left rear wheel RL, and generates a W / C pressure. A conduit A is provided. A braking force is generated by generating a W / C pressure in each of the W / Cs 14 and 15 through the pipeline A.

  The pipe line A is provided with a differential pressure control valve 16 that can be controlled between a communication state and a differential pressure state. The valve position of this differential pressure control valve 16 is adjusted so that it is in a communicating state during normal braking (when motion control is not executed) that generates a braking force corresponding to the operation of the brake pedal 11 by the driver. Yes. When a current flows through a solenoid coil provided in the differential pressure control valve 16, the valve position of the differential pressure control valve 16 is adjusted so that the larger the current value, the larger the differential pressure state. When the differential pressure control valve 16 is in the differential pressure state, the flow of the brake fluid is regulated so that the W / C pressure is higher than the M / C pressure by the amount of the differential pressure.

  The pipe A branches into two pipes A1 and A2 on the W / C 14 and 15 side downstream of the differential pressure control valve 16. The line A1 is provided with a pressure increase control valve 17 for controlling the increase of the brake fluid pressure to the W / C 14, and the line A2 is a pressure increase control for controlling the increase of the brake fluid pressure to the W / C 15. A valve 18 is provided.

  The pressure increase control valves 17 and 18 are two-position solenoid valves that can control the communication / blocking state. The pressure-increasing control valves 17 and 18 are normally controlled to be in a communication state when no control current is supplied to the solenoid coils provided in the pressure-increasing control valves 17 and 18 and in a disconnected state when the control current is supplied to the solenoid coils. It is an open type.

  A pressure reduction control valve 21 and a pressure reduction control valve 22 are provided in a pressure reduction control line 17 connecting the pressure increase control valves 17 and 18 and the W / Cs 14 and 15 and the pressure regulating reservoir 20 in the line A. Each is arranged. These pressure reduction control valves 21 and 22 are constituted by two-position solenoid valves that can control the communication / cutoff state, and are of a normally closed type that is cut off when not energized.

  Between the pressure regulating reservoir 20 and the pipe A, a pipe C serving as a reflux pipe is disposed. The pipe C is provided with a self-priming gear pump 19 driven by a motor 60 so as to suck and discharge brake fluid from the pressure regulating reservoir 20 toward the M / C 13 side or the W / C 14, 15 side. Yes.

  A conduit D serving as an auxiliary conduit is provided between the pressure regulating reservoir 20 and the M / C 13. The brake fluid is sucked from the M / C 13 by the gear pump 19 through this pipe D and discharged to the pipe A, so that the brake is applied to the W / C 14 and 15 side during motion control such as skid prevention control and traction control. Liquid is supplied, and the W / C pressure of the wheel to be controlled is increased.

  On the other hand, as described above, the second piping system 50b has substantially the same configuration as the first piping system 50a. Specifically, the differential pressure control valve 16 corresponds to the differential pressure control valve 36. The pressure increase control valves 17 and 18 correspond to the pressure increase control valves 37 and 38, respectively, and the pressure reduction control valves 21 and 22 correspond to the pressure reduction control valves 41 and 42, respectively. The pressure regulation reservoir 20 corresponds to the pressure regulation reservoir 40. The gear pump 19 corresponds to the gear pump 39. Further, the pipeline A, the pipeline B, the pipeline C, and the pipeline D correspond to the pipeline E, the pipeline F, the pipeline G, and the pipeline H, respectively. As described above, the hydraulic circuit of the vehicle brake device 1 is configured, and the rotary pump device is obtained by integrating the gear pumps 19 and 39 among them. The detailed structure of the rotary pump device will be described later.

  The brake ECU 70 controls a control system of the vehicle brake device 1 and is configured by a known microcomputer including a CPU, a ROM, a RAM, an I / O, and the like. The brake ECU 70 executes processing such as various calculations in accordance with a program stored in a ROM or the like, and executes vehicle motion control such as ABS control and skid prevention control. Specifically, the brake ECU 70 calculates various physical quantities based on detection of sensors (not shown), and determines whether or not to execute vehicle motion control based on the calculation results. When executing the vehicle motion control, the brake ECU 70 obtains a control amount for the wheel to be controlled, that is, a W / C pressure generated in the W / C of the wheel to be controlled. Based on the result, the brake ECU 70 controls the motors 60 for driving the control valves 16-18, 21, 22, 36-38, 41, 42 and the gear pumps 19, 39, so that the W of the wheel to be controlled is controlled. / C pressure is controlled and vehicle motion control is performed.

  For example, when pressure is not generated in the M / C 13 as in traction control or skid prevention control, the gear pumps 19 and 39 are driven and the differential pressure control valves 16 and 36 are set in a differential pressure state. As a result, the brake fluid is supplied to the downstream side of the differential pressure control valves 16, 36, that is, the W / C 14, 15, 34, 35 side through the pipelines D, H. And the pressure increase control valve 17, 18, 37, 38 and the pressure reduction control valves 21, 22, 41, 42 are appropriately controlled to control the pressure increase / decrease of the wheel to be controlled. Control to achieve a desired control amount.

  Further, during ABS control, the pressure increase control valves 17, 18, 37, 38 and the pressure reduction control valves 21, 22, 41, 42 are appropriately controlled, and the gear pumps 19, 39 are driven to increase / decrease the W / C pressure. To control the W / C pressure to a desired control amount.

  Next, the structure of the rotary pump device in the vehicle brake device configured as described above, that is, the detailed structure of the gear pumps 19 and 39 will be described with reference to FIG. FIG. 2 shows a state where the pump main body 100 of the rotary pump device is assembled to the housing 101 of the actuator 50. For example, the rotary body is assembled such that the vertical direction on the paper surface is the vehicle top-to-bottom direction.

  As described above, the vehicle brake device includes two systems, the first piping system 50a and the second piping system 50b. For this reason, the pump main body 100 includes two gear pumps 19 for the first piping system and a gear pump 39 for the second piping system.

  The gear pumps 19 and 39 built in the pump main body 100 are driven when the motor 60 rotates the shaft 54 supported by the first bearing 51 and the second bearing 52. The casing constituting the outer shape of the pump body 100 is constituted by first, second, third, and fourth cylinders (side plates) 71a, 71b, 71c, and 71d and cylindrical first and second central plates 73a and 73b. Has been. The first bearing 51 is disposed in the first cylinder 71a, and the second bearing 52 is disposed in the fourth cylinder 71d.

  The 1st cylinder 71a, the 1st center plate 73a, the 2nd cylinder 71b, the 2nd center plate 73b, and the 3rd cylinder 71c are piled up in order, and the circumference of the overlapping part is joined by welding. And the case of the pump body 100 is configured by using the welded unitized portion as a first case, and the fourth cylinder 71d corresponding to the second case is coaxially arranged with respect to the first case. Has been. The end surfaces of the third cylinder 71c and the fourth cylinder 71d facing each other are provided with recesses 74a and 74b, and the shafts 54 in the first case and the second case are provided by pins 74c disposed therein. Are aligned in the direction of rotation.

  In this way, the integrally structured pump body 100 is configured and inserted into the substantially cylindrical recess 101a formed in the housing 101 of the actuator 50 from the right side of the drawing. Hereinafter, the direction of insertion of the pump body 100 into the recess 101a of the housing 101 is simply referred to as the insertion direction.

  Then, a ring-shaped male screw member (screw) 102 is screwed into the female screw groove 101 b dug in the entrance of the recess 101 a, and the pump body 100 is fixed to the housing 101. The pump main body 100 is structured not to be detached from the housing 101 by screwing the male screw member 102.

  Further, a circular second recess 101 c is formed in the recess 101 a of the housing 101 at a position corresponding to the tip of the shaft 54 in the tip position in the insertion direction. The first bearing 51 is fitted into the second recess 101c, and a portion of the bottom surface of the recess 101a other than the second recess 101c is opposed to the end surface of the first cylinder 71a.

  The first to fourth cylinders 71a to 71d are provided with first, second, third, and fourth center holes 72a, 72b, 72c, and 72d, respectively. The shaft 54 is inserted into the first to fourth center holes 72a to 72d and formed in the first bearing 51 and the fourth cylinder 71d fixed to the inner periphery of the first center hole 72a formed in the first cylinder 71a. The second bearing 52 is fixed to the inner periphery of the fourth center hole 72d.

  The gear pumps 19 and 39 are provided in a region sandwiched between the first and second bearings 51 and 52. The detailed structure of these gear pumps 19 and 39 will be described with reference to FIG.

  The gear pump 19 is disposed in a rotor chamber 100a formed by sandwiching both sides of a cylindrical first central plate 73a between a first cylinder 71a and a second cylinder 71b, and is an inscribed gear pump driven by a shaft 54. (Trochoid pump).

  Specifically, the gear pump 19 includes a rotating portion including an outer rotor 19a having an inner tooth portion formed on the inner periphery and an inner rotor 19b having an outer tooth portion formed on the outer periphery, and the center of the inner rotor 19b. The shaft 54 is inserted into the hole in the. A key 54b is inserted into a hole 54a formed in the shaft 54, and torque is transmitted to the inner rotor 19b by the key 54b.

  The outer rotor 19a and the inner rotor 19b have a plurality of gaps 19c formed by meshing inner teeth and outer teeth formed respectively. Then, the suction and discharge of the brake fluid is performed by changing the size of the gap 19c by the rotation of the shaft 54.

  On the other hand, the gear pump 39 is disposed in a rotor chamber 100b formed by sandwiching both sides of a cylindrical second central plate 73b between the second cylinder 71b and the third cylinder 71c. Similarly to the gear pump 19, the gear pump 39 includes an outer rotor 39a and an inner rotor 39b, and is an internal gear pump that sucks and discharges brake fluid through a plurality of gaps 39c formed by meshing both teeth. It is configured. The gear pump 39 is arranged by rotating the gear pump 19 about 180 ° around the shaft 54. By arranging in this manner, the suction side gaps 19c and 39c and the discharge side gaps 19c and 39c of the gear pumps 19 and 39 are symmetrical with respect to the shaft 54. As a result, the force applied to the shaft 54 by the high brake fluid pressure on the discharge side can be offset.

  The second cylinder 71b is formed with a suction port 80 that communicates with the gap portion 19c on the suction side of the gear pump 19. The suction port 80 extends from the end surface of the second cylinder 71b on the gear pump 19 side to the outer peripheral surface. And the suction | inhalation formed so that it might connect with a part of this annular groove 90a via the annular groove 90a formed so that the circumferential direction might surround the perimeter along the internal peripheral surface of the recessed part 101a with respect to the housing 101. It is connected to the pipeline 90b. For this reason, the gear pump 19 has a structure in which brake fluid is introduced from the outer peripheral side of the pump body 100 through the suction conduit 90 b, the annular groove 90 a, and the suction port 80.

  Further, the first cylinder 71 a is provided with a discharge port 81 communicating with the gap portion 19 c on the discharge side of the gear pump 19. The discharge port 81 is formed so as to penetrate from the end surface on the gear pump 19 side of the first cylinder 71a to the end surface on the opposite side. The discharge port 81 is connected to a discharge conduit 91 formed so as to reach the bottom surface of the recess 101 a with respect to the housing 101. For this reason, the gear pump 19 has a structure in which the brake fluid is discharged from the bottom side of the recess 101a in the pump body 100 through the discharge port 81 and the discharge pipe 91. More specifically, the discharge port 81 is configured as follows.

  In addition to the portion of the first cylinder 71a that penetrates from the end surface on the gear pump 19 side to the opposite end surface, the discharge port 81 has a shaft 54 on the end surface on the rotating portion side of the gear pump 19 in the first cylinder 71a. A passage constituted by an annular groove 110 formed so as to surround is also included.

  Specifically, a ring-shaped seal member 111 is provided in the annular groove 110 so as to press the outer rotor 19a and the inner rotor 19b. The seal member 111 includes a resin member 111a disposed on the rotating portion side and a rubber member 111b that presses the resin member 111a toward the rotating portion side. The inner peripheral side of the seal member 111 includes a gap between the outer periphery of the outer rotor 19a facing the suction side gap 19c and the suction side gap 19c and the first central plate 73a. Further, the outer peripheral side of the seal member 111 includes a gap between the outer periphery of the outer rotor 19a facing the discharge-side gap 19c and the discharge-side gap 19c and the first central plate 73a. That is, the seal member 111 seals the relatively low pressure portion and the relatively high pressure portion of the inner and outer circumferences of the seal member 111.

  Further, the seal member 111 is configured so as to be in contact with the inner periphery of the annular groove 110 and to be in contact with only a part of the outer periphery, and a portion of the annular groove 110 that is not partially in contact with the outer periphery side of the seal member 111 is There is a gap. In other words, the annular groove 110 has a region configured so that the entire outer periphery does not contact the seal member 111, and the brake fluid can flow in this region. The discharge port 81 is configured including the clearance of the annular groove 110 configured as described above.

  Further, a communication passage 81a for communicating the discharge port 81 and the discharge pipe 91 is formed on the end surface in the insertion direction of the first cylinder 71a. The communication path 81a is configured to surround the entire circumference of the first bearing 51. Even if the formation position of the discharge conduit 91 is shifted by the communication passage 81a, the discharge port 81 and the discharge conduit 91 can be reliably communicated with each other. That is, if the end surface of the first cylinder 71a contacts the bottom surface of the recess 101a, there is a possibility that there is no gap between them and the discharge port 81 and the discharge conduit 91 may not communicate with each other, but the communication passage 81a is formed. This ensures that the discharge port 81 and the discharge conduit 91 are in communication with each other.

  Further, the end surface of the second cylinder 71b opposite to the end surface where the suction port 80 is formed is provided with a suction port 82 that communicates with the suction side gap 39c of the gear pump 39. The suction port 82 is formed so as to reach the outer peripheral surface from the end surface on the gear pump 39 side of the second cylinder 71b. A suction conduit formed so as to be connected to a part of the annular groove 92a through an annular groove 92a formed so as to wrap around the circumferential direction along the inner peripheral surface of the recess 101a with respect to the housing 101. 92b. Therefore, the gear pump 39 has a structure in which brake fluid is introduced from the outer peripheral side of the pump main body 100 through the suction conduit 92b, the annular groove 92a, and the suction port 82.

  Further, the third cylinder 71 c is provided with a discharge port 83 communicating with the gap 39 c on the discharge side of the gear pump 39. The discharge port 83 is formed so as to penetrate from the end surface on the gear pump 39 side of the third cylinder 71c to the end surface on the opposite side. The discharge port 83 is connected to a discharge conduit 93 formed so as to reach the inner peripheral surface of the recess 101a with respect to the housing 101 through a gap 94 between the third cylinder 71c and the fourth cylinder 71d. . For this reason, the gear pump 39 has a structure in which the brake fluid is discharged from the outer peripheral surface side of the pump main body 100 through the discharge port 83, the gap 94 and the discharge conduit 93. More specifically, the discharge port 83 is configured as follows.

  In addition to the portion of the third cylinder 71c that extends from the end surface on the gear pump 39 side to the opposite end surface, the discharge port 83 has a shaft 54 on the end surface on the rotating portion side of the gear pump 39 in the third cylinder 71c. A passage constituted by an annular groove 112 formed so as to surround is also included.

  Specifically, a ring-shaped sealing member 113 is provided in the annular groove 112 so as to sandwich the outer rotor 39a and the inner rotor 39b. The seal member 113 includes a resin member 113a disposed on the rotating portion side and a rubber member 113b that presses the resin member 113a toward the rotating portion side. The inner peripheral side of the seal member 113 includes a gap between the outer peripheral portion 39c of the suction side and the outer periphery of the outer rotor 39a facing the suction portion 39c and the second central plate 73b. Further, the outer peripheral side of the seal member 113 includes a gap between the outer periphery of the outer rotor 39a facing the discharge side gap 39c and the discharge side gap 39c and the second central plate 73b. That is, the seal member 113 is configured to seal the relatively low pressure portion and the relatively high pressure portion of the inner and outer periphery of the seal member 113.

  Further, the seal member 113 is configured to contact the inner periphery of the annular groove 112 and to contact only a part of the outer periphery, and a portion of the annular groove 112 that does not contact a part of the outer periphery side of the seal member 113 is There is a gap. That is, the annular groove 112 has a region configured so that the entire outer periphery does not contact the seal member 113, and the brake fluid can flow in this region. The discharge port 83 is configured including the clearance of the annular groove 112 configured as described above.

  In FIG. 2, the suction conduit 90b and the discharge conduit 91 correspond to the conduit C in FIG. 1, and the suction conduit 92b and the discharge conduit 93 correspond to the conduit G in FIG.

  Further, the second center hole 72b of the second cylinder 71b is partially made larger in diameter than the shaft 54, and a seal member 120 for shutting off the gear pump 19 and the gear pump 39 is accommodated in the enlarged diameter portion. Yes. This seal member 120 is obtained by fitting a ring-shaped O-ring 120a into a ring-shaped resin member 120b in which a groove portion having a radial direction as a depth direction is formed, and a resin member by the elastic force of the O-ring 120a. 120b is pressed to come into contact with the shaft 54.

  Similarly, the third center hole 72c of the third cylinder 71c is also partially made larger in diameter than the shaft 54, and a seal member 130 that shuts off the gear pump 39 and the outside of the housing 101 is provided at the increased diameter portion. Contained. The structure of the seal member 130 will be described later in detail.

  Further, an oil seal 140 is provided on the motor 60 side of the seal member 130, that is, on the side opposite to the gear pump 39, and a two-stage seal structure including the seal member 130 and the oil seal 140 is configured.

  With such a configuration, basically, the seal member 130 prevents the brake fluid leakage to the outside through the center hole 72c, and the oil seal 140 can obtain the effect more reliably. Yes.

  In addition, on the fourth cylinder 71d side of the third cylinder 71c, the outer diameter is smaller than the inner diameter of the recess 101a, and this portion is fitted in the center hole 72d of the fourth cylinder 71d. A groove 74d is formed in a portion of the outer periphery of the third cylinder 71c that is fitted into the center hole 72d of the fourth cylinder 71d, and an O-ring 74e is fitted in the groove 74d. The O-ring 74e prevents the brake fluid from leaking to the second bearing 52 side through between the third cylinder 71c and the fourth cylinder 71d.

  However, the portion of the third cylinder 71c that is fitted into the center hole 72d of the fourth cylinder 71d is shorter than the portion of the third cylinder 71c that has a reduced diameter. For this reason, a gap 94 is formed between the surfaces of the third cylinder 71c and the fourth cylinder 71d facing each other, and the brake fluid discharged from the discharge port 83 of the gear pump 39 through the gap 94 is discharged. Guided to the conduit 93 side.

  In addition, O-rings 75a, 75b, 75c, and 75d are disposed on the outer peripheral surfaces of the first to fourth cylinders 71a to 71d, respectively. These O-rings 75 a to 75 d seal brake fluid in the suction pipes 90 b and 92 b and the discharge pipes 91 and 93 formed in the housing 101. The O-ring 75a is between the suction conduit 90b and the discharge conduit 91, the O-ring 75b is between the suction conduit 90b and the suction conduit 92b, and the O-ring 75c is the suction conduit 92b and the discharge conduit. 93, the O-ring 75 d is disposed between the discharge conduit 93 and the outside of the housing 101.

  And the outer peripheral surface of the front end on the inlet side of the recessed portion of the fourth cylinder 71d is reduced in diameter to form a stepped portion. The ring-shaped male screw member 102 described above is fitted into the reduced diameter portion, and the pump body 100 is fixed.

  The pump body 100 is configured by the structure as described above. Next, the detailed structure of the sealing member 130 described above will be described with reference to FIGS. In FIG. 4, the shaft 54 is omitted and shown by a broken line in order to make the drawing easier to see, but the shaft 54 is actually assembled.

  First, the detailed structure of the seal member 130 will be described. As shown in FIG. 4, the seal member 130 is obtained by fitting a ring-shaped rubber cup 132 into a ring-shaped resin ring 131. The seal member 130 is configured to seal between the third cylinder 71 c and the shaft 54 when the resin ring 131 is pressed by the elastic force of the rubber cup 132 and comes into contact with the shaft 54.

  As shown in FIG. 5A, the resin ring 131 is formed with a cup housing groove 131a having a radial direction in the depth direction on the ring-shaped outer peripheral surface. The rubber cup 132 shown in FIG. 5 (b) is fitted into the cup housing groove 131a to constitute the seal member 130 having the structure shown in FIG. 5 (c).

  The cup storage groove 131a includes wall surfaces 131b and 131c provided on both sides in the axial direction, and a bottom surface 131d. The wall surfaces 131b and 131c are configured to have surfaces parallel to the radial direction (perpendicular to the axial direction). The bottom surface 131d has a stepped shape in this embodiment. As described above, the cup storage groove 131a is divided into a shallow region and a deep region by being stepped, and the boundary portion is inclined obliquely with respect to the axial direction and the radial direction. A groove slope 131e is formed. Of the cup storage groove 131a, a region having a shallow groove depth forms a lip storage portion 131f, and a deep region forms a holding portion storage portion 131g.

Further, a spiral groove 131 h is formed on the inner peripheral surface of the resin ring 131.
The spiral groove 131h is formed at a position in contact with the outer peripheral surface of the shaft 54 on the inner peripheral surface of the resin ring 131. In the case of this embodiment, the spiral groove 131h is formed from the end on the gear pump 39 side of the resin ring 131 to the end (front side) of the region pressed against the shaft 54 by the elastic reaction force of the base portion 132a of the rubber cup 132. doing. Specifically, since the resin ring 131 is pressed by the elastic reaction force of the base portion 132a in a region where the groove depth is deep in the cup storage groove 131a, this region becomes a region pressed by the shaft 54. Therefore, the inner circumference of the resin ring 131 is closer to the position corresponding to the shallow groove region of the cup storage groove 131a, more specifically, closer to the gear pump 39 than the boundary position between the holding section storage section 131g and the lip storage section 131f. A spiral groove 131h is formed on the surface.

  The spiral groove 131h is wound in the direction opposite to the rotation direction of the shaft 54 from the spiral start position to the spiral end position, where the first chamber side is the spiral start position and the second chamber side is the spiral end position. Is formed. The inclination angle of the spiral groove 131h, that is, the angle with respect to the radial direction of the shaft 54 when the spiral groove 131h is viewed from the side of the cross section of the resin ring 131 as shown in FIG. 4 is arbitrary, but is gentler. Is preferred. In addition, the number of spiral grooves 131h and the number of turns are arbitrary, but in the present embodiment, the spiral groove 131h is constituted by one and is wound a plurality of times from the spiral start position to the spiral end position. Further, the groove width and groove depth of the spiral groove 131h are also arbitrary.

  In this way, the seal member 130 seals the shaft 54 and the third cylinder 71c, and the spiral groove 131h is formed at a position in the resin ring 131 that contacts the shaft 54.

  As shown in FIGS. 5B and 5C, the rubber cup 132 is provided with a lip-shaped portion 132b with respect to the ring-shaped base portion 132a formed thick. The base portion 132a of the rubber cup 132 is disposed in the holding portion storage portion 131g, and the lip shape portion 132b is disposed in the lip storage portion 131f.

  The base portion 132a includes a holding portion 132c having an arcuate cross section that protrudes radially inward from the base end of the lip-shaped portion 132b, specifically, the base end of a lip 132g described later, on the inner peripheral side. The base portion 132a includes an annular protrusion 132d that protrudes radially outward from the base end of the lip-shaped portion 132b, specifically, the base end of a lip 132f described later, on the outer peripheral side.

  The holding portion 132c is a portion that is fitted and stored in the holding portion storage portion 131g, and the holding portion 132c abuts the groove slope 131e to restrict the rubber cup 132 from moving forward in the insertion direction. It serves to hold the rubber cup 132 in a fixed position.

  When the seal member 130 is disposed between the shaft 54 and the third cylinder 71c, the annular protrusion 132d is partially or entirely crushed by the third cylinder 71c, thereby pressing the resin ring 131 toward the shaft 54. Generate elastic reaction force. A slit 132e extending in the axial direction is formed in the annular protrusion 132d. For this reason, when the pressure in the first chamber on the gear pump 39 side with respect to the seal member 130 is lower than the pressure in the second chamber on the opposite side by a predetermined pressure or more, it leaks into the second chamber through the slit 132e. This makes it easier to return the brake fluid to the first chamber.

  The lip shape portion 132b is a lip shape extended from one end portion in the axial direction of the base portion 132a, in other words, a portion having a V-shaped cross section. Specifically, the lip-shaped portion 132b is disposed on the gear pump 39 side with respect to the base portion 132a, one lip (second lip) 132f is in contact with the inner peripheral surface of the third cylinder 71c, and the other lip ( The first lip 132g is in contact with the bottom surface 131d of the resin ring 131. The lip 132f is inclined obliquely with respect to the axial direction and the radial direction, and when the seal member 130 is disposed between the shaft 54 and the third cylinder 71c, the third lip 132f is crushed inward in the radial direction. The cylinder 71c is in contact with the inner peripheral surface.

  The pump main body 100 is configured by including the seal member 130 having such a structure. In the pump main body 100 configured as described above, the built-in gear pumps 19 and 39 are rotated by the rotating shaft 61 of the motor 60 via the shaft 54, thereby performing a pump operation of sucking and discharging brake fluid.

  For example, the brake ECU 70 drives the gear pumps 19 and 39 by driving the motor 60 when performing vehicle motion control such as side slip prevention control, traction control, or ABS control. Thus, in the pump body 100, the basic pumping operation is performed in which the gear pumps 19 and 39 suck the brake fluid through the suction conduits 90b and 92b and discharge the brake fluid through the discharge conduits 91 and 93. . Then, the gear pumps 19 and 39 suck and discharge the brake fluid in the reservoirs 20 and 40 and supply them to the pipes A and E.

  For this reason, when no M / C pressure is generated in the M / C 13 as in the side slip prevention control or the traction control, the brake fluid is sucked by the gear pumps 19 and 39 through the lines D and H, and the lines A and E are supplied. Thereby, W / C14,15,34,35 is pressurized. Further, when an excessive W / C pressure that causes a locking tendency is generated as in the ABS control, the brake fluid released to the reservoirs 20 and 40 through the pipes B and F is transferred to the gear pumps 19 and 39. Inhale and discharge. As a result, the reservoirs 20 and 40 are not filled with the brake fluid, and the W / C pressure is increased or decreased so as to achieve an appropriate slip ratio. In this way, the vehicle brake device and the gear pumps 19 and 39 operate.

  When performing such an operation, the present embodiment includes the sealing member 130 configured as described above, and therefore the following effects can be obtained.

  That is, the liquid tightness is maintained by the seal member 130 between the third cylinder 71 c and the shaft 54, specifically, between the first chamber and the second chamber defined by the seal member 130. For example, even if the pressure in the first chamber on the one side in the axial direction from the lip shape portion 132b is higher than that in the second chamber on the other side in the axial direction by the pump drive, the pressure in the first chamber is 132b. For this reason, it is possible to suppress the brake fluid from moving from the first chamber to the second chamber while maintaining the pressure difference between the first chamber and the second chamber.

  In this embodiment, since the spiral groove 131h is formed on the inner peripheral surface of the resin ring 131, the brake fluid that has entered the spiral groove 131h as the shaft 54 rotates is moved to the first chamber side. Fluid force acts in the direction of pushing back. For this reason, the brake fluid leakage from the first chamber to the second chamber side can be further suppressed. In particular, during the ABS control, the brake fluid pressure in the first chamber increases, and the brake fluid easily leaks into the second chamber over the seal member 130. However, the shaft 54 is rotated to enter the spiral groove 131h. Brake fluid leakage can be reduced by pushing the brake fluid back toward the first chamber. Thereby, it becomes possible to suppress the brake fluid leakage from the first chamber to the second chamber.

  Even if the brake fluid leaks from the first chamber to the second chamber and the brake fluid flows into the second chamber, the brake fluid is blocked by the oil seal 140 so that the brake fluid does not leak outside the oil seal 140. Can be. Since the brake fluid leakage into the second chamber is suppressed as described above, the brake fluid pressure in the second chamber can be made difficult to reach the opening pressure of the oil seal 140.

  Further, even if the brake fluid is accumulated in the second chamber, if the brake fluid pressure in the first chamber becomes lower than the second chamber by a predetermined pressure or more due to the pump operation stop, it is returned to the first chamber through the slit 132e. The For example, when the brake pedal 1 is not depressed such as during traction control and the gear pumps 19 and 39 are self-priming, the first chamber does not become too high, but the brake pedal 1 is depressed as during ABS control, and W / When the C pressure is reduced and pressure is supplied to the reservoirs 20 and 40, the first chamber tends to become high pressure, and the brake fluid may leak into the second chamber. In such a situation, when the vehicle is stopped, the ABS control is also released and the pump operation is stopped, the brake fluid pressure in the first chamber becomes lower than the second chamber by a predetermined pressure or more, and the brake fluid is in the first chamber. Will be returned to. In this way, the occurrence of brake fluid leakage from the oil seal 140 can be suppressed.

  As described above, in the present embodiment, the two-stage seal structure of the seal member 130 and the oil seal 140 suppresses brake fluid leakage from the first chamber to the second chamber, and allows the second chamber to go to the outside. Brake fluid leakage is suppressed. And since the spiral groove 131h is formed in the position which contact | abuts with the outer peripheral surface of the shaft 54 among the internal peripheral surfaces of the resin ring 131 in the sealing member 130, it entered into the spiral groove 131h with rotation of the shaft 54. A fluid force can be applied to the brake fluid in a direction to push it back toward the first chamber. Thereby, it is possible to make it difficult for brake fluid to leak from the first chamber to the second chamber.

  Furthermore, if a brake fluid leak occurs from the first chamber to the second chamber, when the brake fluid pressure in the first chamber is lower than the brake fluid pressure in the second chamber by a predetermined pressure or more, The brake fluid is allowed to return through the space between the inner peripheral surface of the third cylinder 71c. For this reason, it becomes possible to further suppress the brake fluid that has entered the second chamber from leaking from the oil seal 140 to the outside. Further, as described above, the brake fluid leakage from the first chamber to the second chamber is less likely to occur, so that the brake fluid pressure in the second chamber is less likely to exceed the opening pressure of the oil seal 140. For this reason, it is possible to make it difficult for the brake fluid blocked in the second chamber to leak from the oil seal 140 to the outside.

  The spiral groove 131h is not formed in the entire region of the inner peripheral surface of the resin ring 131 in contact with the outer peripheral surface of the shaft 54, but by the elastic reaction force of the rubber cup 132 in the resin ring 131. It forms so that it may be just before the area | region currently pressed. That is, the spiral groove 131h is formed only in a part in the axial direction of the shaft 54 in the region where the shaft 54 and the resin ring 131 are in contact, and the spiral groove 131h is formed in these contact portions. There is no area left. Accordingly, it is possible to secure a seal between the resin ring 131 and the shaft 54 as compared with the case where the spiral groove 131h is formed in the entire area of these contact portions, and the spiral groove 131h is formed. It is possible to prevent the deterioration of the sealing performance due to this.

(Second Embodiment)
A second embodiment of the present invention will be described. In the present embodiment, the position where the spiral groove is formed is changed with respect to the first embodiment, and the other parts are the same as those in the first embodiment. Therefore, only the parts different from the first embodiment will be described.

  As shown in FIG. 6, in this embodiment, the spiral groove 54c is formed not on the seal member 130 side but on the shaft 54 side. The spiral groove 54 c is formed at a position in contact with the inner peripheral surface of the resin ring 131 in the seal member 130 on the outer peripheral surface of the shaft 54. In the case of this embodiment, on the outer peripheral surface of the shaft 54, the end of the resin ring 131 that is pressed against the shaft 54 by the elastic reaction force of the base portion 132 a of the rubber cup 132 from the end on the gear pump 39 side (front side) ) Is formed. As described in the first embodiment, since the resin ring 131 is pressed by the elastic reaction force of the base portion 132a in the deep groove region of the cup storage groove 131a, the region is pressed by the shaft 54. It becomes an area. Accordingly, the cup housing groove 131a spirals around the outer peripheral surface of the shaft 54 at a position corresponding to a region where the groove depth is shallow, more specifically, on the gear pump 39 side from the boundary position between the holding portion housing portion 131g and the lip housing portion 131f. A groove 54c is formed.

  The spiral groove 54c is wound in the same direction as the rotation direction of the shaft 54 from the spiral start position to the spiral end position, where the first chamber side is the spiral start position and the second chamber side is the spiral end position. Is formed. The inclination angle of the spiral groove 54c, that is, the angle with respect to the radial direction of the shaft 54 when the shaft 54 is viewed from the side as shown in FIG. 6 is arbitrary, but it is preferably more gradual. In addition, the number of spiral grooves 54c and the number of windings are arbitrary, but in this embodiment, the spiral groove 54c is constituted by one and is wound a plurality of times from the spiral start position to the spiral end position. Further, the groove width and groove depth of the spiral groove 54c are also arbitrary.

  As described above, even when the spiral groove 54 c is formed in the shaft 54, the fluid force acts in a direction in which the brake fluid that has entered the spiral groove 54 c with the rotation of the shaft 54 is pushed back to the first chamber side. For this reason, the brake fluid leakage from the first chamber to the second chamber side can be further suppressed. In particular, during ABS control, the brake fluid pressure in the first chamber increases, and the brake fluid easily leaks into the second chamber over the seal member 130. However, the brake fluid flows into the first chamber by rotating the spiral groove 54c. Brake fluid leakage can be reduced by being pushed back to the side. Thereby, it becomes possible to suppress the brake fluid leakage from the first chamber to the second chamber.

  Therefore, even if the spiral groove 54c is formed at a position corresponding to the seal member 130 in the shaft 54 as in the present embodiment, the brake fluid that enters the spiral groove 54c with the rotation of the shaft 54 is prevented. Thus, the fluid force can be applied in the direction of pushing back to the first chamber side. Thereby, like the first embodiment, it is possible to make it difficult for the brake fluid to leak from the first chamber to the second chamber.

  The spiral groove 54c is not formed in the entire position corresponding to the seal member 130 in the shaft 54, but in front of the region of the resin ring 131 that is pressed against the shaft 54 by the elastic reaction force of the rubber cup 132. It is trying to form up to. This makes it possible to secure a seal between the resin ring 131 and the shaft 54 as compared with the case where the spiral groove 54c is formed in the entire area of these contact portions, and the spiral groove 54c is formed. It is possible to prevent the deterioration of the sealing performance due to this.

(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 spiral groove 54 c may be formed so that a plurality of the spiral grooves 54 c overlap with each other, or the spiral groove 54 c may be formed less than one rotation in the circumferential direction of the shaft 54.

  Further, the form of the rubber cup 132 shown in each of the above embodiments is arbitrary, and any form is possible as long as the brake fluid that has entered the second chamber is transformed into the first chamber. May be. In addition, although the second lip 132f of the rubber cup 132 is separated from the inner peripheral surface of the third cylinder 71c, an example is given in which the brake fluid is returned from the second chamber to the first chamber. The return flow may be performed between the first lip 132g and the resin ring 131. Furthermore, although the rubber cup 132 whose cross-sectional shape is a cup shape has been described here as an example, any rubber ring that surrounds the shaft 54 may be used, and a shape other than the cup shape may be used.

  In each of the above embodiments, the rotary pump device including the gear pumps 19 and 39 has been described as an example. However, the present invention is also applied to a rotary pump device including other types of rotary pumps such as a vane pump. Can be applied.

  In each of the above-described embodiments, the spiral grooves 131h and 54c are provided only in one of the resin ring 131 and the shaft 54. However, the present invention is not limited to this and may be provided in both.

  DESCRIPTION OF SYMBOLS 19, 39 ... Rotary pump, 54 ... Shaft, 54c ... Spiral groove, 60 ... Motor, 71a-71d ... 1st-4th cylinder, 80, 82 ... Suction port, 81, 83 ... Discharge port, 100 ... Pump body , 130: sealing member, 131: resin ring, 131a: cup housing groove, 131d: bottom surface, 131f: lip housing portion, 131g: holding portion housing portion, 131h: spiral groove, 132: rubber cup, 132a: base portion, 132b ... Lip-shaped part, 132c ... Holding part, 132e ... Slit, 132f, 132g ... Lip, 140 ... Oil seal

Claims (5)

Rotary pump (19, 39);
A shaft (54) for driving the rotary pump;
A case (71a-71d) in which holes (72a-72d) through which the shaft is inserted are formed;
A ring-shaped resin ring (131) disposed between the inner peripheral surface of the hole and the shaft, and a rubber ring (132) fitted into the outer periphery of the resin ring. A seal member (130) for sealing between the inner peripheral surface of the hole and the shaft;
Between the inner peripheral surface of the hole and the shaft, the shaft is disposed on the opposite side of the rotary pump with the seal member interposed therebetween, and together with the seal member, the inner peripheral surface of the hole and the shaft An oil seal (140) for sealing between
A space between the rotary pump and the seal member is a first chamber, a space between the seal member and the oil seal is a second chamber, and fluid leakage from the first chamber to the second chamber is the seal member. When the fluid leaks into the second chamber, the oil seal seals, and when the fluid pressure in the first chamber is lower than the fluid pressure in the second chamber by a predetermined pressure or more, the seal A rotary pump device configured to return the fluid in the second chamber to the first chamber through a member;
The resin ring has a position where the first chamber side is set as a spiral start position and a position where the second chamber side is set as a spiral end position at a position in contact with the outer peripheral surface of the shaft. The rotary pump device is characterized in that a spiral groove (131h) wound in the direction opposite to the rotation direction of the shaft is formed toward the spiral end position. Rotary pump (19, 39);
A shaft (54) for driving the rotary pump;
A case (71a-71d) in which holes (72a-72d) through which the shaft is inserted are formed;
A ring-shaped resin ring (131) disposed between the inner peripheral surface of the hole and the shaft, and a rubber ring (132) fitted into the outer periphery of the resin ring. A seal member (130) for sealing between the inner peripheral surface of the hole and the shaft;
Between the inner peripheral surface of the hole and the shaft, the shaft is disposed on the opposite side of the rotary pump with the seal member interposed therebetween, and together with the seal member, the inner peripheral surface of the hole and the shaft An oil seal (140) for sealing between
A space between the rotary pump and the seal member is a first chamber, a space between the seal member and the oil seal is a second chamber, and fluid leakage from the first chamber to the second chamber is the seal member. When the fluid leaks into the second chamber, the oil seal seals, and when the fluid pressure in the first chamber is lower than the fluid pressure in the second chamber by a predetermined pressure or more, the seal A rotary pump device configured to return the fluid in the second chamber to the first chamber through a member;
In the shaft, the first chamber side is a spiral start position and the second chamber side is a spiral end position at a position of the shaft that contacts the inner peripheral surface of the resin ring in the seal member. A rotary pump device characterized in that a spiral groove (54c) wound in the same direction as the rotation direction of the shaft from the spiral start position toward the spiral end position is formed.   3. The rotary pump according to claim 1, wherein the spiral groove is formed only in a part in an axial direction of the shaft in a region where the shaft and the resin ring are in contact with each other. apparatus. The rubber ring is configured as a rubber cup having a ring-shaped base portion (132a) and a lip-shaped portion (132b) extending from one end portion in the axial direction from the base portion,
The base portion has a holding portion (132c) protruding radially inward of the base portion,
The lip-shaped portion includes an inner peripheral first lip (132g) that is in close contact with the resin ring, and an outer peripheral second lip (132f) that is brought into contact with the inner peripheral surface of the case, When the fluid pressure in the first chamber becomes a predetermined pressure or more lower than the fluid pressure in the second chamber, the second lip is separated from the inner peripheral surface of the case or the first lip is separated from the resin ring. Return the fluid in two chambers to the first chamber;
The resin ring includes a cup storage groove (131a) in which the rubber cup whose radial direction is the depth direction on the outer peripheral surface of the resin ring is stored, and the bottom surface (131d) of the cup storage groove is The holding part storage part (131g) in which the holding part is stored is deeper than the lip storage part (131f) in which the lip-shaped part is stored, and is pushed between the inner peripheral surface of the hole and the resin ring. The inner circumferential surface of the resin ring is pressed against the outer circumferential surface of the shaft based on the elastic reaction force of the crushed base portion,
The said spiral groove is formed only in the said 1st chamber side rather than the boundary position of the said lip-shaped part and the said holding | maintenance part accommodating part, The Claim 1 characterized by the above-mentioned. Rotary pump device. A brake operating member (11);
A master cylinder (13) for generating a brake fluid pressure based on the operation of the brake operation member;
A wheel cylinder (14, 15, 34, 35) for generating a braking force based on the brake fluid pressure;
Main pipelines (A, E) connecting the master cylinder and the wheel cylinder;
A pressure-increasing control valve (17, 18, 37, 38) that is provided in the main pipe line and controls an increase in the brake fluid pressure applied to the wheel cylinder;
A pressure reducing pipe (B, F) connected between the pressure increasing control valve and the wheel cylinder in the main pipe;
A pressure reduction control valve (21, 22, 41, 42) that is provided in the pressure reduction line and controls pressure reduction of the brake fluid pressure applied to the wheel cylinder;
Reservoirs (20, 40) for storing brake fluid discharged from the main line through the pressure reducing line when the pressure reducing control valve is in a communication state;
A reflux line (C, G) connected between the master cylinder and the pressure increase control valve in the main line from the reservoir;
The reflux pipe is provided with the rotary pump device according to any one of claims 1 to 4,
An anti-lock brake control is performed in which the wheel tends to lock by increasing or decreasing the brake fluid pressure applied to the wheel cylinder, and the brake fluid in the reservoir is returned to the main pipeline by the rotary pump device. The brake device for vehicles characterized by the above-mentioned.

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