JP2014119011A - Rotating machine - Google Patents

Abstract

PROBLEM TO BE SOLVED: To regulate the rotation of a seal member without the necessity of a pin, and to avoid the application of a load to the seal member to the outside of a radial direction.SOLUTION: A rotation regulation part 132d including an inclined line which gradually becomes short in distance from a center axis of a resin member 132 toward the front of an insertion direction is formed at a portion abutting on an internal wall face of a center hole 132a out of the resin member 132. Furthermore, a rotation regulation part 72d which abuts on the inclined line by the rotation of a rotating shaft 54 and applies a force Fa to a side opposite to the front of the insertion hole with respect to the inclined line is formed at an internal wall face of a center hole 72a of a plug 72. By this, the rotation regulation part 132d can regulate the co-rotation of the seal member 130 by abutting on the plug 72, and the movement of the seal member 130 to an axial direction can be regulated by the force Fa. Then, a force Fb in a radial direction is applied to the inclined line. Therefore, the rigidity of the resin member 132 is not necessary to be high, and the enlargement of the resin member 132 accompanied by the reinforcement of rigidity can be suppressed.

Description

  The present invention relates to a rotary machine that seals by placing a seal member having a ring-shaped resin member and a rubber ring between a case and a shaft inserted through the case and bringing the resin member into close contact with the shaft side. For example, it is suitable when applied to a gear pump.

  Conventionally, Patent Document 1 discloses a brake device provided with a rotary pump. In the rotary pump provided in this brake device, a seal member having a resin member and a rubber ring is disposed between a drive shaft (shaft) for driving the rotary pump and a case housing the rotary pump. doing. This seal member suppresses brake fluid leakage between the drive shaft and the case. Specifically, the seal member is arranged so that the resin member is in contact with the drive shaft and the rubber ring is in contact with the case side, and the resin member is pressed against the drive shaft by the elastic force of the rubber ring. ing.

  Further, a recess (notch) having an inclined surface inclined with respect to the axial direction and the circumferential direction of the resin member is formed at the tip of the resin member, and a pin inserted into the recess is formed in the case. Is formed. These recesses and pins constitute a rotation restricting portion, and when the resin member brought into contact with the drive shaft is rotated along with the rotation of the drive shaft, the inclined surface and the pin come into contact with each other so that the seal member The rotation of the is regulated. And since the part which contact | abuts with a pin among resin members is made into the inclined surface, the force accompanying rotation of a drive shaft is converted into the force which urges | biases a resin member to the insertion direction of a case. As a result, the front end of the resin member in the insertion direction into the case comes into contact with the stopper surface of the case, and the movement of the seal member in the axial direction of the drive shaft can be restricted.

JP 2012-77762 A

  However, since a pin is provided in the case, a pin is required and a process for press-fitting the pin into a hole formed in the case is required. For this reason, high-precision hole machining is required, and the occurrence of burrs due to press-fitting of pins becomes a problem.

  Furthermore, the pin and the concave portion of the resin member are brought into contact with each other for restricting the rotation of the seal member, but at the time of contact, a load is applied to the resin member in the radially outward direction, that is, in the direction in which the resin member is deformed. Become. For this reason, the rigidity of the resin member is required, and there is a problem that the size of the resin member becomes large in order to obtain the rigidity.

  In view of the above points, the present invention can restrict the rotation of the seal member without requiring a pin, and prevents the resin member from being subjected to a radially outward load on the seal member. It aims at providing the rotary machine which can suppress the enlargement accompanying rigidity reinforcement.

  In order to achieve the above object, in the first aspect of the present invention, the sealing member (130) is formed by fitting the elastic ring (131) into the groove (132b) of the resin member (132), The portion of the member (132) that is brought into contact with the inner wall surface of the second center hole (72a) formed in the case (72) is gradually moved toward one side in the axial direction of the rotating shaft (54). The first rotation restricting portion (132d) including an inclined line that shortens the distance from the central axis of the resin member is provided, and the inner wall surface of the second central hole comes into contact with the inclined line by the rotation of the rotating shaft and the inclined line A second rotation restricting portion (72d) for applying a force (Fa) to one side opposite to the axial direction with respect to the line is provided.

  In such a configuration, since the resin member is brought into contact with the rotation shaft by the elastic force of the elastic ring, the seal member is rotated along with the rotation of the rotation shaft. However, when the first rotation restricting portion comes into contact with the case, the rotation of the seal member is thereby restricted. As described above, since the circulation of the seal member can be regulated only by the elastic ring and the resin member, it is not necessary to regulate the circulation using a pin as in Patent Document 1.

  Furthermore, the first rotation restricting portion has an inclined line that gradually decreases in distance from the central axis toward one side in the axial direction. For this reason, the contact force (Ft) between the case and the resin member based on the rotational torque of the rotation shaft is equal to the force (Fa) on the opposite side to the one side in the axial direction due to the inclination of the first rotation restricting portion. Can be converted into a force (Fb). Therefore, a force (Fa) opposite to the one axial side can be applied to the resin member with the rotation of the rotary shaft, and the movement of the seal member in the axial direction can be restricted.

  Further, the force (Fb) generated at the same time is not applied radially outward to the resin member but applied radially inward. For this reason, the load in the direction in which the inner peripheral surface of the seal member is brought into contact with the rotation shaft is applied rather than the load in the deformation direction on the seal member, and the deformation of the seal member is prevented. However, it is possible to further improve the sealing performance. And since the force (Fb) applied to the inside of the resin member in the radial direction can be supported by the rotating shaft, the rigidity of the resin member does not need to be high, and the increase in size due to the strengthening of the rigidity of the resin member is suppressed. it can.

  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.

The brake piping schematic of the brake device for vehicles which applied the gear pump apparatus as a rotary machine concerning 1st Embodiment of this invention is shown. 1 is a cross-sectional view of a gear pump device including a pump body 100 including gear pumps 19 and 39 and a motor 60. FIG. It is AA sectional drawing of FIG. FIG. 3 is an enlarged view of a region R in FIG. 2. 3 is a cross-sectional perspective view of a plug 72. FIG. It is an enlarged view when the inside of the center hole 72a is seen from the insertion direction rear. 3 is a perspective view of a resin member 132. FIG. It is a cross-sectional enlarged view of the seal member 130 vicinity in the gear pump apparatus concerning 2nd Embodiment.

  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)
With reference to FIG. 1, a vehicle brake device 1 to which a gear pump device that is a rotating machine according to an embodiment of the present invention is applied will be described. Here, an example in which the vehicle brake device 1 according to the present invention is applied to a vehicle constituting a hydraulic circuit for front and rear piping will be described. The right front wheel and the left rear wheel are connected to the first piping system, and the left front wheel and the right rear wheel are connected to the first. The present invention can also be applied to an X pipe that is a two-pipe system.

  As shown in FIG. 1, the vehicle brake device 1 includes a brake pedal 11, a booster device 12, an M / C 13, W / Cs 14, 15, 34, and 35, and a brake fluid pressure control actuator 50. And are provided. Further, the vehicle brake device 1 is provided with a brake ECU 70, 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 12 and the M / C 13, and when the driver depresses the brake pedal 11, the pedaling force is boosted by the booster 12, and the master piston disposed in the M / C 13. Press 13a, 13b. 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, 35 through the brake hydraulic pressure control 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 brake fluid pressure control actuator 50 has a first piping system 50a and a second piping system 50b. The first piping system 50a is a rear system that controls the brake fluid pressure applied to the right rear wheel RR and the left rear wheel RL, and the second piping system 50b is the brake fluid pressure that is applied to the left front wheel FL and the right front wheel FR. It is assumed to be a front system.

  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 in the left rear wheel RL and the W / C 15 provided in the right rear wheel RR, 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 gear pump device is obtained by integrating the gear pumps 19 and 39 among them. The detailed structure of the gear 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 according to a program stored in a ROM or the like, and executes vehicle motion control such as 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, at the time of anti-skid (ABS) control, the pressure increase control valves 17, 18, 37, and 38 and the pressure reduction control valves 21, 22, 41, and 42 are appropriately controlled, and the gear pumps 19 and 39 are driven to drive the W / C. The pressure increase / decrease is controlled so that the W / C pressure becomes a desired control amount.

  Next, the detailed structure of the gear pump device in the vehicle brake device 1 configured as described above will be described with reference to FIGS. FIG. 2 shows a state in which the pump body 100 is assembled to the housing 101 of the brake fluid pressure control actuator 50. For example, the pump body 100 is assembled so that the vertical direction on the paper surface is the vehicle top-to-bottom direction.

  As described above, the vehicle brake device 1 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 50a and a gear pump 39 for the second piping system 50b.

  The gear pumps 19 and 39 built in the pump main body 100 are driven by the motor 60 rotating the rotating shaft 54 supported by the first bearing 51 and the second bearing 52. The casing constituting the outer shape of the pump main body 100 is composed of an aluminum cylinder 71 and a plug 72, the first bearing 51 is disposed on the cylinder 71, and the second bearing 52 is disposed on the plug 72.

  In a state where the cylinder 71 and the plug 72 are coaxially arranged, one end side of the cylinder 71 is integrated by being press-fitted into the plug 72, and the case of the pump body 100 is configured. And the pump main body 100 is comprised by providing the gear pumps 19 and 39, various sealing members, etc. with the cylinder 71 and the plug 72. FIG.

  In this way, the integral pump body 100 is configured. The pump body 100 having an integral structure is inserted into a substantially cylindrical recess 101a formed in an aluminum housing 101 from the right side of the drawing. 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.

  In the present specification, 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. Further, the axial direction and circumferential direction of the pump main body 100 (axial direction and circumferential direction of the rotating shaft 54) are simply referred to as axial direction and circumferential direction.

  A circular second concave portion 101c is formed at a front end position in the insertion direction in the concave portion 101a, that is, at a position corresponding to the front end of the rotating shaft 54 (the left end portion in FIG. 2) in the bottom portion of the concave portion 101a. The diameter of the second recess 101c is larger than the diameter of the rotation shaft 54, and the tip of the rotation shaft 54 is located in the second recess 101c so that the rotation shaft 54 does not contact the housing 101. Yes.

  The cylinder 71 and the plug 72 are provided with center holes 71a and 72a, respectively. The rotation shaft 54 is inserted into the center holes 71 a and 72 a, and the first bearing 51 fixed to the inner periphery of the center hole 71 a in the cylinder 71 and the second bearing 52 fixed to the inner periphery of the center hole 72 a in the plug 72. It is supported by.

  The gear pumps 19 and 39 are provided on both sides of the first bearing 51, that is, in a region in front of the first bearing 51 in the insertion direction and a region sandwiched between the first and second bearings 51 and 52, respectively.

  As shown in FIG. 3, the gear pump 19 is disposed in a rotor chamber (accommodating portion) 100 a configured by a concave portion in which one end surface of the cylinder 71 is recessed in a circular shape. The gear pump 19 is constituted by an inscribed gear pump (trochoid pump) driven by a rotating shaft 54 inserted into the rotor chamber 100a.

  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 rotation shaft 54 is inserted into the hole in the. A key 54b is inserted into a hole 54a formed in the rotating 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 rotating shaft 54.

  On the other hand, as shown in FIG. 2, the gear pump 39 is disposed in a rotor chamber (accommodating portion) 100b constituted by a concave portion in which the other end surface of the cylinder 71 is recessed in a circular shape. It is driven by a rotating shaft 54 inserted into the inside. Similarly to the gear pump 19, the gear pump 39 includes an outer rotor 39a and an inner rotor 39b. The gear pump 39 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 such that the gear pump 19 is rotated approximately 180 ° around the rotation shaft 54. By arranging in this way, the gaps 19c, 39c on the suction side and the gaps 19c, 39c on the discharge side of the gear pumps 19, 39 are symmetrical with respect to the rotation shaft 54. The force applied to the rotating shaft 54 by the high brake fluid pressure can be offset.

  These gear pumps 19 and 39 have basically the same structure, but have different axial thicknesses, and the gear pump 39 provided in the front system is more in comparison with the gear pump 19 provided in the rear system. However, the axial length is increased. Specifically, the rotors 39 a and 39 b of the gear pump 39 are longer in the axial direction than the rotors 19 a and 19 b of the gear pump 19. For this reason, the gear pump 39 has a larger intake and discharge amount of brake fluid than the gear pump 19 and can supply more brake fluid to the front system than the rear system.

  On one end surface side of the cylinder 71, a seal mechanism 111 that presses the gear pump 19 toward the cylinder 71 is provided on the opposite side of the cylinder 71 with the gear pump 19 interposed therebetween, that is, between the cylinder 71 and the gear pump 19 and the housing 101. Yes. Further, on the other end face side of the cylinder 71, a seal mechanism 115 that presses the gear pump 39 toward the cylinder 71 on the opposite side of the cylinder 71 with the gear pump 39 interposed therebetween, that is, between the cylinder 71 and the gear pump 39 and the plug 72. Is provided.

  The seal mechanism 111 is configured by a ring-shaped member having a hollow portion into which the rotating shaft 54 is inserted. With this sealing mechanism 111, the outer rotor 19a and the inner rotor 19b are pressed toward the cylinder 71, thereby sealing a relatively low pressure portion and a relatively high pressure portion on one end face side of the gear pump 19. Yes. Specifically, the sealing mechanism 111 exhibits a sealing function by contacting the bottom surface of the concave portion 101a that is an outline of the housing 101 and desired positions of the outer rotor 19a and the inner rotor 19b.

  Further, the outer diameter of the seal mechanism 111 is set to be smaller than the inner diameter of the recess 101a of the housing 101 at least above the plane of FIG. For this reason, it is set as the structure which can flow brake fluid through the clearance gap between the sealing mechanism 111 and the recessed part 101a of the housing 101 above the paper surface. This gap constitutes the discharge chamber 80 and is connected to a discharge conduit 90 formed at the bottom of the recess 101 a of the housing 101. With such a structure, the gear pump 19 can discharge brake fluid using the discharge chamber 80 and the discharge conduit 90 as a discharge path.

  The cylinder 71 is formed with a suction port 81 that communicates with a gap portion 19 c on the suction side of the gear pump 19. The suction port 81 extends from the end surface of the cylinder 71 on the gear pump 19 side to the outer peripheral surface, and is connected to a suction pipe 91 provided on the side surface of the recess 101 a of the housing 101. With such a structure, the gear pump 19 can introduce brake fluid using the suction pipe 91 and the suction port 81 as a suction path.

  On the other hand, the seal mechanism 115 is also formed of a ring-shaped member having a central portion into which the rotating shaft 54 is inserted. With this sealing mechanism 115, the outer rotor 39a and the inner rotor 39b are pressed toward the cylinder 71, thereby sealing a relatively low pressure portion and a relatively high pressure portion on one end face side of the gear pump 39. Yes. Specifically, the sealing mechanism 115 exhibits a sealing function by contacting the end surface of the portion of the plug 72 in which the sealing mechanism 115 is accommodated and the desired positions of the outer rotor 39a and the inner rotor 39b.

  The basic structure of the seal mechanism 115 is the same as that of the seal mechanism 111, but the surface constituting the seal with the above-described seal mechanism 111 is on the opposite side, and the structure is changed accordingly. Specifically, the sealing mechanism 115 is configured to have a symmetrical shape with respect to the sealing mechanism 111, and is arranged with a 180 ° phase shift with respect to the sealing mechanism 111 around the rotation shaft 54. Other than that, the seal mechanism 115 has the same structure as the seal mechanism 111.

  The outer diameter of the seal mechanism 115 is smaller than the inner diameter of the plug 72 at least in the lower part of the drawing. For this reason, the brake fluid can flow through the gap between the seal mechanism 115 and the plug 72 below the paper surface. This gap constitutes the discharge chamber 82, and is connected to a communication path 72 b formed in the plug 72 and a discharge conduit 92 formed on the side surface of the recess 101 a of the housing 101. With such a structure, the gear pump 39 can discharge brake fluid using the discharge chamber 82, the communication path 72b, and the discharge pipe line 92 as discharge paths.

  On the other hand, the end surface of the cylinder 71 on the side of the gear pumps 19 and 39 is also a sealing surface, and the gear pumps 19 and 39 are brought into close contact with the sealing surface to provide a mechanical seal. Thus, the relatively low pressure portion and the relatively high pressure portion on the other end face side of the gear pumps 19 and 39 are sealed.

  Further, the cylinder 71 is formed with a suction port 83 that communicates with a gap 39 c on the suction side of the gear pump 39. The suction port 83 extends from the end surface of the cylinder 71 on the gear pump 39 side to the outer peripheral surface, and is connected to a suction conduit 93 provided on the side surface of the recess 101 a of the housing 101. With such a structure, the gear pump 39 can introduce brake fluid using the suction pipe 93 and the suction port 83 as a suction path.

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

  In addition, an annular resin member 120a having a U-shaped radial cross section and an annular rubber member fitted in the annular resin member 120a at the rear of the first bearing 51 in the center hole 71a of the cylinder 71 in the insertion direction. The sealing member 120 provided with 120b is accommodated. The seal member 120 provides a seal between the two systems in the center hole 71a of the cylinder 71.

  The center hole 72a of the plug 72 has a stepped shape with an inner diameter reduced in a plurality of steps from the rear to the front in the insertion direction, and the seal member 130 is accommodated in a stepped portion on the front side in the insertion direction. ing. The seal member 130 is configured to include an elastic ring 131 and a resin member 132, and performs shaft seal when the resin member 132 is in contact with the rotating shaft 54. The seal member 130 has a configuration that characterizes the present invention. The detailed structure of the seal member 130 will be described later.

  A stopper ring 140 is provided behind the seal member 130 in the center hole 72a of the plug 72 in the insertion direction. The stopper ring 140 is press-fitted and fixed in the center hole 72a, and the stopper ring 140 prevents the seal member 130 from coming off from the center hole 72a in the rear in the insertion direction.

  Furthermore, an oil seal (seal member) 150 is provided at the stepped portion behind the stopper ring 140 in the insertion direction. With such a configuration, basically, the seal member 130 prevents the brake fluid leaking to the outside through the center hole 72a, and the oil seal 150 more reliably provides the brake fluid to the outside. There is no leakage.

  Note that the inner diameter of the center hole 72a is reduced in a plurality of stages from the front to the rear in the insertion direction. Among these, the above-described seal mechanism 115 is accommodated in a stepped portion on the rear side in the insertion direction. The communication passage 72b described above is formed so as to reach from the stepped portion to the outer peripheral surface of the plug 72. Further, the end of the cylinder 71 in the insertion direction rear side is press-fitted into the stepped portion which is the frontmost in the insertion direction in the center hole 72a. A portion of the cylinder 71 that is fitted into the center hole 72 a of the plug 72 has a smaller outer diameter than other portions of the cylinder 71. Since the axial dimension of the portion of the cylinder 71 whose outer diameter is reduced is larger than the axial dimension of the stepped portion on the most front side in the insertion direction of the center hole 72a, the cylinder 71 is the center of the plug 72. When press-fitted into the hole 72a, a groove 74c formed by the cylinder 71 and the plug 72 is formed at the tip of the plug 72.

  O-rings 73a to 73d as annular seal members are provided on the outer periphery of the pump main body 100 configured in this manner so as to seal each part. These O-rings 73a to 73d seal the brake fluid between the two systems formed in the housing 101 or between the discharge path and the suction path of each system. The O-ring 73 a is disposed between the discharge chamber 80 and the discharge conduit 90 and the suction port 81 and the suction conduit 91. The O-ring 73 b is disposed between the suction port 81 and the suction conduit 91 and the suction port 83 and the suction conduit 93. The O-ring 73 c is disposed between the suction port 83 and the suction conduit 93 and the discharge chamber 82 and the discharge conduit 92. The O-ring 73 d is disposed between the discharge chamber 82 and the discharge conduit 92 and the outside of the housing 101. The O-rings 73a, 73c, and 73d are simply arranged in a circular shape so as to wrap around the circumferential direction around the rotation axis 54, but the O-ring 73b is an axis that surrounds the circumferential direction around the rotation axis 54. By disposing in the direction, the size can be reduced in the axial direction of the rotating shaft 54.

  Further, groove portions 74a to 74d are provided on the outer periphery of the pump body 100 so that the O-rings 73a to 73d can be arranged. The groove portions 74 a and 74 b are formed by partially denting the outer periphery of the cylinder 71. The groove 74 c is formed by a recessed portion on the outer periphery of the cylinder 71 and a tip portion of the plug 72. The groove 74d is formed by partially denting the outer periphery of the plug 72. By inserting the pump body 100 into the recess 101a of the housing 101 with the O-rings 73a to 73d fitted in the grooves 74a to 74d, the O-rings 73a to 73d are formed on the inner wall surface of the recess 101a. It is crushed and made to function as a seal.

  In addition, the outer peripheral surface of the plug 72 is reduced in diameter in the rear in the insertion direction 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 gear pump device is configured by the structure as described above. Next, the detailed structure of the sealing member 130 described above and the detailed structure of the center hole 72a of the plug 72 in the portion where the sealing member 130 is disposed will be described with reference to FIGS.

  As shown in FIG. 4, the seal member 130 is configured such that a ring-shaped elastic ring 131 made of an elastic member is fitted into the resin member 132, and one side in the axial direction of the rotary shaft 54 with respect to the center hole 72 a Is fitted from the rear side in the insertion direction. The elastic ring 131 is formed of, for example, a rubber seal having a square cross section, and the inner peripheral surface abuts on the resin member 132 and the outer peripheral surface abuts on the inner wall surface of the center hole 72a, so that the resin member 132 and the plug are plugged. 72 is sealed. The elastic member 131 is pressed radially inward by the elastic force generated by the elastic ring 131 being crushed by the resin member 132 and the plug 72.

  The resin member 132 is formed of a substantially cylindrical member, and the rotation shaft 54 is inserted through a center hole 132a formed with a constant diameter along the center axis. On the outer peripheral surface of the resin member 132, a groove portion 132b having a radial direction of the resin member 132 as a depth direction is formed, and an elastic ring 131 is fitted in the groove portion 132b. The resin member 132 is pressed inward in the radial direction by the elastic ring 131, whereby the inner wall surface of the center hole 132 a is brought into contact with the rotation shaft 54. As a result, a seal is formed between the resin member 132 and the rotating shaft 54.

  As shown in FIG. 7, the front end of the resin member 132 in the insertion direction has a diameter that is conical with respect to the conical portion (first conical portion) 132c whose outer shape is conical and the conical portion 132c. The shape has a changed rotation restricting portion (first rotation restricting portion) 132d. The conical portions 132c are formed symmetrically on both sides of the central axis of the resin member 132, in the case of this embodiment, on the top and bottom of the paper surface of FIG. The rotation restricting portion 132d is formed symmetrically in both directions sandwiching the central axis of the resin member 132 in the direction perpendicular to the direction in which both conical portions 132c are arranged, in the case of this embodiment, in the left-right direction in FIG. ing. In the case of the present embodiment, the rotation restricting portion 132d is configured by a plane parallel to the direction in which both conical portions 132c are arranged.

  Both the conical portion 132c and the rotation restricting portion 132d are tapered such that the distance from the central axis gradually decreases toward the front in the insertion direction, and are tapered surfaces inclined with respect to the central axis. For this reason, the boundary line between the conical portion 132c and the rotation restricting portion 132d is also an inclined line inclined with respect to the central axis.

  On the other hand, as shown in FIGS. 4 to 6, the plug 72 also has an inner peripheral dimension of the center hole 72 a set in accordance with the shape of the seal member 130. As described above, the center hole 72a of the plug 72 has a stepped shape in which the inner diameter is reduced in a plurality of steps from the rear to the front in the insertion direction. Of these, the most contracted portion functions as a stopper portion, and this portion is brought into contact with the tip of the resin member 132, so that the movement of the resin member 132 forward in the insertion direction is restricted. A conical portion (second conical portion) 72c and a rotation restricting portion (second rotation) which are opposed to and fitted to the conical portion 132c and the rotation restricting portion 132d are formed on the inner wall surface of the center hole 72a functioning as the stopper portion. A restricting portion 72d is formed.

  The pump body 100 is configured by including the seal member 130 having such a structure and the plug 72 having a shape corresponding to the seal member 130. In the pump main body 100 configured as described above, the built-in gear pumps 19 and 39 perform a pump operation of sucking and discharging brake fluid when the rotating shaft 54 is rotated by the motor 60. 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.

  Specifically, the seal member 130 according to the present embodiment is configured by only the elastic ring 131 and the resin member 132. Such a seal member 130 is rotated along with the rotation of the rotation shaft 54 because the resin member 132 is brought into contact with the rotation shaft 54 when the pump operation is performed. However, when the rotation restricting portion 132d comes into contact with the rotation restricting portion 72d, the rotation of the seal member 130 is thereby restricted. As described above, since the circulation of the seal member 130 can be regulated only by the elastic ring 131 and the resin member 132, it is not necessary to regulate the circulation using a pin as in Patent Document 1.

  Further, the rotation restricting portions 72d and 132d are tapered surfaces whose distance from the central axis gradually decreases toward the front side in the insertion direction. For this reason, the contact force Ft between the plug 72 and the resin member 132 based on the rotational torque of the rotating shaft 54 is the force Fa on the rear side in the insertion direction as shown in FIG. 4 due to the inclination of the rotation restricting portions 72d and 132d. It can be converted into a radially inward force Fb. Accordingly, a force Fa in the rearward direction of insertion can be applied to the resin member 132 as the rotary shaft 54 rotates, and the movement of the seal member 130 in the axial direction can be restricted.

  Further, the force Fb generated at the same time is not applied radially outward to the resin member 132 but is applied radially inward. For this reason, instead of applying a load in the deformation direction to the seal member 132, a load in a direction in which the inner peripheral surface of the seal member 132 is brought into contact with the rotating shaft 54 more is applied. It is also possible to improve the sealing property while preventing the deformation of the material. Further, since the force Fb applied radially inward to the resin member 132 can be supported by the rotary shaft 54, the resin member 132 does not have to have high rigidity, and the resin member 132 is increased in size due to the rigidity enhancement. Can be suppressed.

  A portion of each rotation restricting portion 132d that comes into contact with the rotation restricting portion 72d when the rotation shaft 54 is rotated is a boundary line formed at the boundary between each rotation restricting portion 132d and each conical portion 132c. Is the boundary line on the side located on the rear end side in the rotation direction. For this reason, if the boundary line is an inclined line whose distance from the central axis gradually decreases toward the front side in the insertion direction, the inclined line comes into contact with the rotation restricting portion 72d by the rotation of the rotating shaft 54 and is inserted. The force Fa on the rear side in the direction is applied, and the above effect can be obtained.

  As described above, according to the present embodiment, the rotation of the seal member 130 can be restricted without the need for a pin and without applying a radially outward load to the seal member 130. It becomes possible.

(Second Embodiment)
A second embodiment of the present invention will be described. In this embodiment, the configuration of the plug 72 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. 8, in this embodiment, the plug 72 is provided with a stopper portion 72e, that is, the plug 72 is constituted by two members having a main body and a stopper portion 72e, and the stopper portion 72e is provided with a conical portion 72c or the like. The rotation restricting portion 72d is provided. Further, the seal member 130 is fitted into the center hole 72a of the plug 72 from one side described in the first embodiment to the opposite side. Then, on one side of the seal member 130, the stopper portion 72e is integrated with the main body of the plug 72, and the center hole 72a is closed, so that the stopper portion 72e constitutes a part of the inner wall surface of the center hole 72a. I have to. The stopper 72e can be integrated with the main body of the plug 72 by any method such as press fitting or welding.

  Thus, if the plug 72 is constituted by two members, the main body and the stopper portion 72e, and the stopper portion 72e is provided with the conical portion 72c and the rotation restricting portion 72d, the seal member 130 is opposite to that of the first embodiment. It can be configured to be fitted into the center hole 72a from the direction.

  And in such a structure, the stopper part 72e becomes a part which comprises the inner wall face contact | abutted to the resin member 132 among the plugs 72, and it becomes possible to show an effect similar to 1st Embodiment.

(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, although the rotation restricting portion 132d is formed at two places, it may be formed at one place or three or more places. However, if the rotation restricting portion 132d is formed symmetrically with respect to the central axis of the resin member 132 as in the above-described embodiment, it is possible to further increase the force Fa toward the rear in the insertion direction.

  In addition, the rotation restricting portions 72d and 132d may be inclined so that at least a portion to be brought into contact with the rotation shaft 54 is inclined so that the distance from the central axis gradually decreases toward the front side in the insertion direction. . The boundary between the conical portion 132c and the rotation restricting portion 132d and the boundary between the conical portion 72c and the rotation restricting portion 72d are not necessarily linear, and may be rounded. However, even in such a case, the resin member 132 abuts against the plug 72 at the boundary line included in the curved surface serving as the boundary, thereby generating a force Fa on the rear side in the insertion direction and a force Fb in the radial direction. The above effect can be obtained.

  Moreover, in the said embodiment, although an example of the rotary machine was shown, it can also change suitably about the component of a rotary machine. For example, a gear pump device has been described as an example of a rotating machine, but an annular seal that suppresses the flow of liquid through a gap between a rotating shaft such as the rotating shaft 54 and a case such as a plug 72 surrounding the rotating shaft. Another rotating machine having the member 130 may be used.

  DESCRIPTION OF SYMBOLS 100 ... Pump main body, 101 ... Housing, 19, 39 ... Gear pump, 54 ... Rotating shaft, 71 ... Cylinder, 72 ... Plug, 72a ... Center hole (2nd center hole), 72c ... Conical part, 72d ... Rotation restriction part , 80, 82 ... discharge chamber, 81, 83 ... suction port, 130 ... sealing member, 131 ... elastic ring, 132 ... resin member, 132a ... center hole (first center hole), 132b ... groove, 132c ... conical part , 132d ... rotation restricting portion

Claims (5)

A resin member (132) having a ring shape in which a first center hole (132a) along the central axis is formed, and having a groove portion (132b) having a radial direction as a depth direction on an outer peripheral surface; A seal member (130) having a ring-shaped elastic ring (131) made of an elastic member fitted in
A rotating shaft (54) inserted through the first central hole;
A second center hole (72a) in which the rotating shaft is inserted and the seal member is disposed is formed. The seal member is fitted into the second center hole, and the second center hole is inserted into the second center hole. A case (72) in which a wall surface is brought into contact with the resin member,
In the portion of the resin member that is brought into contact with the inner wall surface of the second central hole, an inclined line in which the distance from the central axis of the resin member gradually decreases toward one side in the axial direction of the rotation shaft. A first rotation restricting portion (132d) including
A second rotation restriction is applied to the inner wall surface of the second center hole so as to abut against the inclined line by rotation of the rotating shaft and to apply a force (Fa) to the inclined line on one side opposite to the one side in the axial direction. A rotating machine comprising a portion (72d).   The resin member has a first conical portion (132c) having a conical shape in which the diameter from the central axis of the resin member gradually decreases toward one side in the axial direction, and the first rotation The rotating machine according to claim 1, wherein the restricting portion has a diameter changed with respect to the first conical portion.   The first rotation restricting portion is a tapered surface that gradually decreases in distance from the central axis of the resin member toward one side in the axial direction, and the first rotation restricting portion and the first cylindrical portion are The rotating machine according to claim 2, wherein the boundary line is the inclined line.   The inner wall surface of the second center hole has a second conical portion (72c) facing the first conical portion and a second rotation restricting portion (72d) facing the first rotation restricting portion. The rotating machine according to claim 2, wherein the rotating machine is a rotating machine.   5. The rotating machine according to claim 1, wherein the first rotation restricting portion is provided on both sides of the central axis.

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