JP5463770B2 - Rotary pump and brake device having the same - Google Patents

Description

  The present invention relates to a rotary pump that sucks and discharges fluid and a brake device including the rotary pump, and is particularly suitable for application to an internal gear pump such as a trochoid pump.

  Internal gear type rotary pumps such as trochoid pumps are composed of an inner rotor with outer teeth on the outer periphery, an outer rotor with inner teeth on the inner periphery, a casing that houses these outer rotors and inner rotor, etc. Has been. The inner rotor and the outer rotor are disposed in the casing in a state where the inner teeth and the outer teeth are engaged with each other and a plurality of gaps are formed by these teeth.

  In such a rotary pump, a groove is formed in the inner wall surface of the casing corresponding to the end surfaces of the outer rotor and the inner rotor, a seal member is disposed in the groove, and the seal member is disposed on the end surfaces of the outer rotor and the inner rotor. A pressed structure is disclosed (see Patent Document 1). As a result, the end surfaces of the outer rotor and the inner rotor and the inner wall surface of the casing are sealed between the high-pressure part and the low-pressure part, and brake fluid leakage from the high-pressure part to the low-pressure part is prevented.

JP 2000-355274 A

  However, in the case of the above-described conventional rotary pump, the brake fluid pressure in the confined portion that does not communicate with both the suction port and the discharge port and the brake fluid pressure in the suction port and the discharge port (hereinafter referred to as the suction pressure respectively). And discharge pressure). Specifically, at the confined portion where the volume is the smallest in the rotation direction, the brake fluid pressure decreases due to the expansion of the gap portion, and a negative pressure is generated. The suction pressure is lower than the suction pressure. On the contrary, in the upper closed part located in front of the discharge port in the rotation direction, the brake fluid pressure increases due to the compression of the gap, so that the pressure becomes higher than the high discharge pressure. For this reason, there is a difference in the brake fluid pressure when the gap portion passes through the confined portion with rotation and communicates with the suction port or the discharge port, so that a large pulsation due to the difference occurs.

  An object of this invention is to provide the rotary pump which can suppress the pulsation resulting from the hydraulic pressure difference of a confinement part and a suction inlet or a discharge outlet, and a brake device provided with the same in view of the said point.

In order to achieve the above object, in the invention according to claims 1 to 4 , a seal groove (71b) formed in a surface corresponding to the axial end surfaces of the outer rotor (51) and the inner rotor (52) in the casing (50). 72b), and in the gap between the axial end faces of the inner and outer rotors and the casing, it passes between the discharge port and the drive shaft when viewed in the axial direction and passes through the confined part. Sealed portions (100e, 100f, 101e, 101f) that reach the outer periphery of the rotor and seal the closed portions (53a, 53b) and have sliding contact surfaces that are in sliding contact with the axial end surfaces of the outer rotor and inner rotor. ) provided with sealing means (100, 101) having, at least the volume of the sealing portion of the sealing means is minimum The sealing portion to cover the closed portion of the side, is constituted by depressions opening to the sliding surface, with the rotation movement, the volume portion that is in communication with the closed portion and the void spaces part in the closed state (100 g, 101g ).

  According to such a rotary pump, until the gap portion moves from the range where the gap portion becomes the closed portion to a place where the gap portion communicates with the suction port or the discharge port, the gap portion that is set as the closed portion is communicated with the volume portion. be able to. As a result, the brake fluid pressure in the gap can be made substantially equal to the brake fluid pressure in the volume portion. Therefore, the brake fluid pressure at the closing portion can be brought close to the suction pressure or the discharge pressure immediately before the suction port or the discharge port, so that the gap portion passes through the range that becomes the close portion and communicates with the suction port or the discharge port. It is possible to suppress the occurrence of pulsation due to the hydraulic pressure difference when it is caused.

Specifically, in the first aspect of the invention, the volume portion is disposed only in a region where the volume of the gap portion serving as the confinement portion on the side where the volume is minimum is increased, so that the volume portion is closed immediately before the suction port. The brake fluid pressure at the recess is brought close to the suction pressure so that the above-described effect can be obtained .

Further, as described in claim 2, when the gap portion becomes closed portion has been communicated to the suction port from via the volume portion in accordance with the rotation movement, so as to communicate with the suction port through the airspace It is preferable that the volume part is constructed.

With such a configuration, the brake fluid is filled for example when the void portion is moved from the range of the closed portion via the volume portion in a location that communicates with the inlet port, through the gap portion in communication with the inlet port . Therefore, it is possible before communicating with the gap portion becomes next closed portion, should return the brake fluid pressure in the volume portion to the suction-pressure corresponding.

In the invention according to claim 4 , the sealing means is provided only on one end face in the axial direction of the outer rotor and the inner rotor in the casing, and the other end face of the casing is in direct contact with the outer rotor and the inner rotor. Adopting a mechanical seal to seal, sealing the sealing part (53a, 53b) of the end face to be the mechanical seal, and sealing the seal part to the axial end face of the outer rotor and the inner rotor It is characterized by comprising a volume part (72c) that is configured by an open dent and communicates with the gap part of the closed part in a sealed state in accordance with the rotational movement.

  As described above, one end face in the axial direction of the outer rotor and the inner rotor in the casing can be sealed by a sealing means, and the other end face can be sealed by a mechanical seal. In this case, a volume portion can be provided on the end surface on the side where the mechanical seal is made.

In the invention according to claim 5 , the end surfaces corresponding to the axial end surfaces of the outer rotor and the inner rotor in the casing are mechanical seals that seal the end surfaces directly in contact with the outer rotor and the inner rotor. Of the end surfaces to be sealed, the confined portions (53a, 53b) are covered so as to be sealed, and the sliding contact surfaces that are in sliding contact with the axial end surfaces of the outer rotor and the inner rotor are constituted by recesses that are opened and rotated. Accordingly, a volume portion (72c) that is communicated with a gap portion of the closed portion in a sealed state is provided.

Thus, even when the mechanical seal is employed, the same effect as in the first aspect can be obtained by providing the sliding contact surface with the volume portion. Even in the case where such a mechanical seal is employed, by adopting the configuration described in claim 2 as shown in claim 6 , it is possible to obtain the same effects as in the above claims.

The rotary pump as described above is preferably applied to a brake device in which a high hydraulic pressure is used. Specifically, as described in claim 7 , the brake fluid pressure generating means (1-3) for generating the brake fluid pressure based on the pedaling force, and the control for generating the braking force on the wheel based on the brake fluid pressure. The power generation means (4, 5) and the brake fluid pressure generation means are connected to the main pipeline (A) for transmitting the brake fluid pressure to the brake force generation means, and the brake fluid pressure generation means is connected to the brake force generation means. In order to increase the braking force generated by the brake device, the brake device having the auxiliary pipelines (C, D) for supplying the brake fluid to the main pipeline side, the brake is provided on the brake fluid pressure generating means side through the auxiliary pipeline. The rotary pump can be arranged so that the liquid can be sucked and the discharge port can discharge the brake liquid toward the braking force generating means through the main pipeline.

  In addition, the code | symbol in the bracket | parenthesis of each said means shows the correspondence with the specific means as described in embodiment mentioned later.

It is a pipe line lineblock diagram of a brake equipment provided with rotary pump 10 concerning a 1st embodiment of the present invention. It is a figure which shows the specific structure of the rotary pump 10 in FIG. 1, (a) is a schematic diagram of the rotary pump 10, (b) is AA-A sectional drawing of (a). The resin member 100b in the sealing member 100 is enlarged, (a) is a front view, (b) is a perspective view. It is an enlarged view of the vicinity of the closing part 53b and the volume parts 100g and 101g in the rotary pump 10 with which the brake device concerning 2nd Embodiment of this invention is equipped. The volume change of the space | gap part 53 accompanying rotation of the rotary pump 10 is shown. 4 is a graph showing a change in brake fluid pressure (absolute pressure) of a confining portion 53b as the rotary pump 10 rotates. (A) is the schematic diagram of the rotary pump 10 with which the brake device of this embodiment is equipped, (b) is a BB sectional drawing of (a). 4 is a graph showing a change in brake fluid pressure (absolute pressure) of a confining portion 53b as the rotary pump 10 rotates. It is sectional drawing of the rotary pump 10 with which the brake device of 3rd Embodiment of this invention is equipped.

  Hereinafter, embodiments of the present invention will be described with reference to the drawings. In the following embodiments, the same or equivalent parts are denoted by the same reference numerals in the drawings.

(First embodiment)
First, the basic configuration of the brake device will be described with reference to FIG. Here, an example in which the brake device according to the present invention is applied to a vehicle that constitutes a hydraulic circuit of an X pipe having a right front wheel-left rear wheel and a left front wheel-right rear wheel piping system in a front wheel drive four-wheel vehicle will be described. However, it can also be applied to front and rear piping.

  As shown in FIG. 1, the brake pedal 1 is connected to a booster device 2, and the brake pedal force and the like are boosted by the booster device 2.

  The booster 2 has a push rod or the like that transmits the boosted pedaling force to the master cylinder 3, and the push cylinder presses a master piston disposed in the master cylinder 3 to thereby master cylinder. Pressure is generated. The brake pedal 1, the booster 2, and the master cylinder 3 correspond to brake fluid pressure generating means.

  The master cylinder 3 is connected to a master reservoir 3 a that supplies brake fluid into the master cylinder 3 and stores excess brake fluid in the master cylinder 3. The master cylinder pressure is transmitted to the wheel cylinder 4 for the right front wheel FR and the wheel cylinder 5 for the left rear wheel RL as braking force generating means via a brake fluid pressure control actuator that performs ABS control and the like. .

  In the following description, the right front wheel FR and the left rear wheel RL side will be described. However, since the same applies to the left front wheel FL and the right rear wheel RR side which are the second piping system, the description will be omitted.

  The brake device includes a pipe line (main pipe line) A connected to the master cylinder 3, and the pipe line A is provided with a linear differential pressure control valve 22 together with a check valve 22a. The pipe A is divided into two parts by the linear differential pressure control valve 22. That is, the pipeline A includes a pipeline A1 that receives the master cylinder pressure between the master cylinder 3 and the linear differential pressure control valve 22, and a pipeline A2 between the linear differential pressure control valve 22 and the wheel cylinders 4 and 5. It is divided into.

  The linear differential pressure control valve 22 is normally in communication, but when the brake is suddenly applied to the wheel cylinders 4 and 5 when the master cylinder pressure is lower than a predetermined pressure, or during traction control, the master cylinder side and the wheel cylinder It will be in the state (differential pressure state) which generates a predetermined differential pressure between the two sides. The linear differential pressure control valve 22 can linearly adjust the set value of the differential pressure.

  Further, in the pipeline A2, the pipeline A is branched into two, and one of the openings is provided with a pressure increase control valve 30 for controlling the increase of the brake fluid pressure to the wheel cylinder 4, and the other is provided. A pressure increase control valve 31 for controlling the increase in brake fluid pressure to the wheel cylinder 5 is provided.

  These pressure increase control valves 30 and 31 are configured as two-position valves that can control the communication / blocking state by an electronic control unit (hereinafter referred to as ECU). When the two-position valve is controlled to be in communication, the master cylinder pressure or the brake fluid pressure generated by the discharge of the pump 10 described later can be applied to the wheel cylinders 4 and 5. These first and second pressure-increasing control valves 30 and 31 are always controlled to communicate during normal braking when ABS control is not being executed.

  The pressure increase control valves 30 and 31 are provided with safety valves 30a and 31a, respectively, so that brake fluid is removed from the wheel cylinders 4 and 5 side when the brake depression is stopped and the ABS control is finished. It has become.

  An ECU communicates with a conduit (suction conduit) B connecting the conduit A and the pressure regulating reservoir 40 between the first and second pressure increase control valves 30 and 31 and the wheel cylinders 4 and 5. Pressure reduction control valves 32 and 33 that can control the shut-off state are respectively provided. These pressure reduction control valves 32 and 33 are always cut off in the normal brake state (when the ABS is not operating).

  A rotary pump 10 is disposed in a pipeline (auxiliary pipeline) C connecting the linear differential pressure control valve 22 and the pressure increase control valves 30, 31 in the pipeline A and the pressure regulating reservoir 40. A safety valve 10A is provided on the discharge port side of the rotary pump 10 so that the brake fluid does not flow backward. A motor 11 is connected to the rotary pump 10, and the rotary pump 10 is driven by the motor 11.

  A conduit (auxiliary conduit) D is provided so as to connect the pressure regulating reservoir 40 and the master cylinder 3. A two-position valve 23 is disposed in the pipeline D, and the two-position valve 23 is normally shut off and the pipeline D is shut off. When the two-position valve 23 is in a communication state at the time of brake assist or traction control and the pipe D is in a communication state, the rotary pump 10 draws the brake fluid in the pipe A1 through the pipe D, The wheel cylinder pressure in the wheel cylinders 4 and 5 is discharged to the pipe line A2 to be higher than the master cylinder pressure to increase the wheel braking force. At this time, the differential pressure between the master cylinder pressure and the wheel cylinder pressure is held by the linear differential pressure control valve 22.

  The pressure regulating reservoir 40 is connected to the pipeline D and receives the brake fluid from the master cylinder 3 side, and receives the brake fluid that is connected to the pipelines B and C and escapes from the wheel cylinders 4 and 5. And a reservoir hole 40b. A ball valve 41 is disposed inside the reservoir hole 40a. The ball valve 41 is provided with a rod 43 having a predetermined stroke for moving the ball valve 41 up and down separately from the ball valve 41.

  Also, in the reservoir chamber 40c, there are a piston 44 that works in conjunction with the rod 43, and a spring 45 that generates a force that pushes the piston 44 toward the ball valve 41 to push out the brake fluid in the reservoir chamber 40c. Is provided.

  In the pressure regulating reservoir 40 configured in this way, when a predetermined amount of brake fluid is stored, the ball valve 41 is seated on the valve seat 42 so that the brake fluid does not flow into the pressure regulating reservoir 40. . Therefore, more brake fluid than the suction capacity of the rotary pump 10 does not flow into the reservoir chamber 40c, and an excessively high pressure is not applied to the suction side of the rotary pump 10.

  2A is a schematic diagram of the rotary pump 10, and FIG. 2B is a cross-sectional view taken along the line A-O-A in FIG. 2A. The structure of the rotary pump 10 will be described based on b).

  In the rotor chamber 50a of the casing 50 of the rotary pump 10, the outer rotor 51 and the inner rotor 52 are assembled and stored with their respective central axes (points X and Y in the figure) being eccentric. Yes. The outer rotor 51 includes an inner tooth portion 51a on the inner periphery, and the inner rotor 52 includes an outer tooth portion 52a on the outer periphery. The outer rotor 51 and the inner rotor 52 are meshed with each other by forming a plurality of gap portions 53 by the tooth portions 51a and 52a. As can be seen from FIG. 2A, the rotary pump 10 according to the present embodiment is a partition in which a gap portion 53 is formed by the inner tooth portion 51 a of the outer rotor 51 and the outer tooth portion 52 a of the inner rotor 52. It is a multi-tooth trochoid type pump without a plate (crescent). Further, in order to transmit the rotational torque of the inner rotor 52, the inner rotor 52 and the outer rotor 51 have a plurality of contact points.

  As shown in FIG. 2 (b), the casing 50 includes a first side plate portion 71 and a second side plate portion 72 arranged so as to sandwich both rotors 51 and 52 from both sides, and the first, A central plate portion 73 is provided between the second side plate portions 71 and 72 and provided with a hole for accommodating the outer rotor 51 and the inner rotor 52, thereby forming a rotor chamber 50a. .

  In addition, center holes 71a and 72a communicating with the inside of the rotor chamber 50a are formed in the center portions of the first and second side plate portions 71 and 72. The center holes 71a and 72a are connected to the inner rotor 52. The arranged drive shaft 54 is inserted. The outer rotor 51 and the inner rotor 52 are rotatably disposed in the hole of the central plate portion 73. That is, the rotating part constituted by the outer rotor 51 and the inner rotor 52 is rotatably incorporated in the rotor chamber 50a of the casing 50, and the outer rotor 51 rotates about the point X as shown in FIG. The inner rotor 52 rotates around the point Y.

  Furthermore, when the line passing through the point X and the point Y serving as the respective rotation axes of the outer rotor 51 and the inner rotor 52 is a center line Z of the rotary pump 10, the center line Z of the first side plate portion 71 is sandwiched. On the left and right sides, a suction port 60 and a discharge port 61 communicating with the rotor chamber 50a are formed. The suction port 60 and the discharge port 61 are disposed at positions that communicate with the plurality of gaps 53. The brake fluid from the outside can be sucked into the gap 53 through the suction port 60 and the brake fluid in the gap 53 can be discharged to the outside through the discharge port 61.

  Among the plurality of gaps 53, the closed portion 53a on the side with the largest volume and the closed portion 53b on the side with the smallest volume do not communicate with either the suction port 60 or the discharge port 61. The closed portions 53a and 53b maintain a differential pressure between the suction pressure at the suction port 60 and the discharge pressure at the discharge port 61.

  A concave portion 73a and a concave portion 73b are formed on the inner wall surface of the central plate portion 73 at a position of about 45 degrees from the center line Z toward the suction port 60 with the point X serving as the rotation axis of the outer rotor 51 as the center. Seal members 80 and 81 for suppressing the flow of brake fluid on the outer periphery of the outer rotor 51 are provided in the recesses 73a and 73b. These seal members 80 and 81 seal the portion where the brake fluid pressure is low and the portion where the brake fluid pressure is high on the outer periphery of the outer rotor 51.

  The seal member 80 includes a rubber member 80a having a spherical or substantially cylindrical shape and a resin member 80b having a rectangular parallelepiped shape. As the resin member 80b, PTFE, PTFE containing carbon fiber, or PTFE containing graphite is used. The resin member 80 b is pressed by the rubber member 80 a and comes into contact with the outer rotor 51. That is, a slight error is generated in the size of the outer rotor 51 due to a manufacturing error or the like, and this error can be absorbed by the rubber member 80a having an elastic force.

  The width of the resin member 80b (the width in the rotation direction of the outer rotor 51) is such that a gap is left to some extent when the resin member 80b is disposed in the recess 73a. In other words, if the width of the resin member 80b is formed to be equal to the width of the recess 73a, the resin member 80b becomes difficult to come out when entering the recess 73a due to the flow of the brake fluid pressure when the pump is driven. By forming the resin member 80b with a certain size, the brake fluid enters the rubber member 80a side of the resin member 80b, and the pressure of the brake fluid makes it easy for the resin member 80b to come out of the recess 73a. Yes. The seal member 81 is also configured to include a rubber member 81a and a resin member 80b. However, since the seal member 81 has the same structure as the seal member 80, the description thereof is omitted.

  Further, as shown in FIG. 2B, seal groove portions 71b and 72b are formed in the first and second side plate portions 71 and 72, respectively. The seal groove portions 71b and 72b are formed in an annular shape (frame shape) surrounding the drive shaft 54, as shown by a one-dot chain line in FIG. 2A, and the groove width is widened in a predetermined region. It has a configuration. Further, the centers of the seal groove portions 71b and 72b are eccentric to the suction port 60 side (left side in the drawing) with respect to the shaft center of the drive shaft 54.

  As a result, the seal groove portions 71 b and 72 b pass between the discharge port 61 and the drive shaft 54 and pass through the portions where the closing portions 53 a and 53 b and the seal members 80 and 81 seal the outer rotor 51. Arrangement.

  Seal members 100 and 101 are disposed in the seal groove portions 71b and 72b having such a configuration. The seal members 100 and 101 are constituted by elastic members 100a and 101a made of an elastic body such as rubber, and resin members 100b and 101b made of resin, and the resin members 100b and 101b are made into outer rotors by the elastic members 100a and 101a. 51 and the inner rotor 52 side.

  3 is an enlarged view of the resin member 100b in the seal member 100, FIG. 3 (a) is a front view, and FIG. 3 (b) is a perspective view. Hereinafter, the detailed structure of the resin members 100b and 101b will be described with reference to FIG. 3, but the resin member 100b and the resin member 101b have a symmetrical shape sandwiching the outer rotor 51 and the inner rotor 52, and basically have the same structure. Therefore, the resin member 100b will be described as an example.

  As shown in FIG. 3, the resin member 100b has a shape similar to the shape of the seal groove 71b and has an annular shape. Further, the resin member 100b is a stepped plate in which a concave portion 100c and a convex portion 100d are formed on one end surface side.

  Further, the resin member 100b is arranged such that the surface on which the convex portion 100d is formed is disposed on the opening side of the seal groove portion 71b, so that the convex portion 100d is in contact with one end surfaces of both the rotors 51 and 52 and the central plate portion 73. It has become. Since the elastic member 100a is disposed on the bottom side of the seal groove 71b with respect to the resin member 100b, the resin member 100b is pressed by the elastic force of the elastic member 100a and the discharge pressure of the brake fluid introduced into the seal groove 71b. Fulfills the sealing function.

  The convex part 100d has a sealing part 100e and a sealing part 100f. The sealing part 100e and the sealing part 100f are in the suction port from the state in which the gap 53 communicates with the discharge port 61 until the transition from the state in which the gap 53 communicates with the suction port 60 to the state in which the gap 53 communicates with the discharge port 61. 60 until the transition to the state communicated with 60. These sealing portions 100e and 100f are configured to have a width so as to cover at least the closed portions 53a and 53b, and seal the closed portions 53a and 53b.

  Further, a convex portion 100d is partially formed inside the sealing portion 100f that covers the confining portion 53b (the lower confining portion in FIG. 2A) on the side where the volume is minimum among the plurality of gap portions 53. A volume portion 100g is formed in which is recessed. The opening of the volume portion 100g is provided only at the inside of the sliding contact surface that is in sliding contact with the axial end surfaces of the outer rotor 51 and the inner rotor 52 so as to terminate in the sealed portion 100f. The brake fluid is accommodated in the volume portion 100g by entering the brake fluid through a gap between the resin member 100b and the outer rotor 51 and the inner rotor 52. When the gap 53 that has become the closed portion 53b is moved in the rotation direction in accordance with the rotation of the outer rotor 51 and the inner rotor 52, the volume portion 100g is communicated.

  The resin member 101b in the seal member 101 is also symmetrical with the resin member 100b with the outer rotor 51 and the inner rotor 52 interposed therebetween. Since FIG. 3 shows the resin member 100b, the resin member 101b actually has a symmetrical shape with respect to this figure. However, as shown in FIG. It is set as the structure provided with each part 101c-101g similar to 100g.

  With the seal members 100 and 101 arranged in this way, in the gap between the axial end surfaces of the inner rotor 52 and the outer rotor 51 and the first and second side plate portions 71 and 72, a high-pressure discharge port 61, The gap between the low-pressure drive shaft 54 and the inner rotor 52 and the suction port 60 are sealed.

  In order to seal the high pressure portion and the low pressure portion in the gap between the axial end surfaces of the inner rotor 52 and the outer rotor 51 and the first and second side plate portions 71 and 72, the sealing members 100 and 101 are used. However, it is necessary to pass between the discharge port 61 and the drive shaft 54 and between the discharge port 61 and the suction port 60 and reach the outer periphery of the outer rotor 51.

  In the present embodiment, of the seal members 100 and 101, the region from the seal member 80 to the seal member 81 passing between the drive shaft 54 and the discharge port 61 is a high pressure portion and a low pressure portion. In other regions where sealing is not required, the portions in contact with the inner rotor 52 and the outer rotor 51 are negligibly small. For this reason, the contact resistance by the sealing members 100 and 101 can be reduced, and the mechanical loss can be reduced.

  Next, the operation of the thus configured brake device and rotary pump 10 will be described.

  When it is desired to generate a large braking force by generating a wheel cylinder pressure larger than the master cylinder pressure generated by the operation of the brake pedal 1 by the driver, for example, when a braking force corresponding to the brake pedal force cannot be obtained or the brake pedal 1 When the operation amount is large, the two-position valve 23 provided in the brake device is appropriately brought into a communication state, and the linear differential pressure control valve 22 is brought into a differential pressure state.

  On the other hand, in the rotary pump 10, the inner rotor 52 rotates in accordance with the rotation of the drive shaft 54 by driving the motor 11, and the outer rotor 51 also moves in the same direction due to the meshing of the inner tooth portion 51a and the outer tooth portion 52a. Rotate to. At this time, the volume of each gap portion 53 changes in size while the outer rotor 51 and the inner rotor 52 make one rotation, so that the brake fluid is sucked from the suction port 60 and is directed from the discharge port 61 toward the pipeline A2. Exhale brake fluid. The wheel cylinder pressure is increased by the discharged brake fluid. That is, the rotary pump 10 performs a basic pumping operation in which the brake fluid is sucked from the suction port 60 and the brake fluid is discharged from the discharge port 61 as the rotors 51 and 52 rotate.

  Since the differential pressure is generated by the linear differential pressure control valve 22, the discharge pressure of the rotary pump 10 is downstream of the linear differential pressure control valve 22, that is, the wheel cylinders 4, 5. Acting, a wheel cylinder pressure larger than the master cylinder pressure is generated. For this reason, a wheel cylinder pressure larger than the master cylinder pressure generated by the operation of the brake pedal 1 by the driver can be generated by the brake device.

  In the pump operation at this time, the suction port 60 side of the outer periphery of the outer rotor 51 is set to suction pressure (atmospheric pressure) by the brake fluid sucked through the pressure regulating reservoir 40, and the discharge port of the outer periphery of the outer rotor 51 is discharged. 61 side is made into discharge pressure by the brake fluid discharged to high pressure.

  For this reason, a low pressure portion and a high pressure portion are generated on the outer periphery of the outer rotor 51. However, as described above, since the low pressure portion and the high pressure portion of the outer periphery of the outer rotor 51 are sealed and separated by the seal members 80 and 81, the high pressure portion on the discharge port 61 side through the outer periphery of the outer rotor 51. Brake fluid leakage does not occur toward the low pressure portion on the suction port 60 side. In addition, due to the seal members 80 and 81, the suction port 60 side of the outer periphery of the outer rotor 51 becomes a low pressure, and the pressure is the same as that of the gap 53 communicating with the suction port 60. The discharge port 61 side has a high pressure, which is the same pressure as the gap portion 53 communicating with the discharge port 61. For this reason, the pressure balance inside and outside of the outer rotor 51 is maintained, and the pump can be driven stably.

  Further, in the rotary pump 10 shown in the present embodiment, since the seal members 80 and 81 are located on the suction port 60 side, high-pressure discharge is performed up to a position surrounding the closed portions 53a and 53b in the outer periphery of the outer rotor 51. Pressure. For this reason, the outer rotor 51 is pressed in the vertical direction on the paper surface, and a load is applied in a direction in which the tooth gap between the inner tooth portion 51a of the outer rotor 51 and the outer tooth portion 52a of the inner rotor 52 is reduced in the closing portion 53a. It acts so that the tooth tip gap between the inner tooth portion 51a and the outer tooth portion 52a is reduced. As a result, it is possible to suppress leakage of brake fluid that occurs through the tooth tip gap between the inner tooth portion 51 a of the outer rotor 51 and the outer tooth portion 52 a of the inner rotor 52.

  On the other hand, the clearance between the axial end surfaces of the inner rotor 52 and the outer rotor 51 and the first and second side plate portions 71, 72 is also between the low-pressure inlet 60 and the drive shaft 54 and the inner rotor 52. The low pressure portion and the high pressure portion are generated by the gap and the high pressure discharge port 61. However, the seal members 100 and 101 seal the low pressure portion and the high pressure portion of the gap between the axial end surfaces of the inner rotor 52 and the outer rotor 51 and the first and second side plate portions 71 and 72. Therefore, no brake fluid leaks from the high pressure part to the low pressure part. Since the seal members 100 and 101 are formed so as to pass through the seal members 80 and 81, no gap is generated between the seal members 100 and 101 and the seal members 80 and 81. There is no leakage.

  Furthermore, in the brake device of this embodiment, the volume parts 100g and 101g are formed with respect to the sealing parts 100f and 101f for sealing the closing parts 53b in the resin parts 100b and 101b of the rotary pump 10. The volume parts 100g and 101g have a predetermined depth when viewed from the front, for example, a triangular shape. Further, the distance from the volume parts 100g, 101g to the discharge port 61 is set such that the volume parts 100g, 101g do not communicate with the discharge port 61 through the gap 53, which is the closed part 53b. , 101 g so that the discharge pressure is not applied.

  Since the volume parts 100g and 101g are provided, the brake fluid pressure in the confining part 53b is changed to the atmospheric pressure with the rotation of the rotary pump 10 (the rotation of the outer rotor 51 and the inner rotor 52). It is possible to prevent the pressure from becoming lower than the suction pressure, that is, the negative pressure. Although the details of this mechanism are not clear, it is assumed as follows. This will be described with reference to FIGS.

  FIG. 4 is an enlarged view of the rotary pump 10 in the vicinity of the closing portion 53b and the volume portions 100g and 101g. FIG. 5 shows a change in the volume of the gap 53 as the rotary pump 10 rotates, and the place where the capacity of the gap 53 is the smallest is represented as a rotation angle θ = 0 °. FIG. 6 is a graph showing a change in the brake fluid pressure (absolute pressure) of the confining portion 53b as the rotary pump 10 rotates.

  As shown in FIG. 4, the gap portion 53 communicating with the discharge port 61 moves with rotation and is sandwiched between the sealing portions 100f and 101f to be sealed, thereby forming the closing portion 53b. The volume of the gap 53 changes with the rotation. At this time, as shown in FIG. 5, there is a process in which the volume of the gap 53 gradually increases from the range of the closed portion 53 b to the inside of the suction port 60. For this reason, the brake fluid pressure decreases due to the expansion of the volume in the gap portion 53 that becomes the closed portion 53b, and a negative pressure is generated.

  However, in this embodiment, since the sealing portions 100f and 101f are provided with the volume portions 100g and 101g, when the rotation further proceeds, the gap portion 53 that becomes the closed portion 53b is communicated with the volume portions 100g and 101g. For this reason, the brake fluid pressure in the gap portion 53 that becomes the closed portion 53b is determined by the volume of the gap portion 53, the volumes of the volume portions 100g and 101g, and the amount of brake fluid existing therebetween. Therefore, as shown in FIG. 6, it is possible to raise the brake fluid pressure in the gap portion 53 to substantially the brake fluid pressure in the volume portions 100g and 101g, so that almost no negative pressure is generated.

  Thereafter, the brake fluid pressure slightly decreases with the volume change of the gap portion 53 until the gap portion 53 moves from the range where the gap portion 53 becomes the closed portion 53b to the place where it is communicated with the suction port 60. However, since this change can be determined including not only the volume in the gap 53b but also the volumes of the volume parts 100g and 101g, the brake fluid pressure in the confining part 53b can be brought close to almost atmospheric pressure.

  Therefore, it can suppress that the brake fluid pressure in the space | gap part 53 used as the closed part 53b with rotation of the rotary pump 10 falls rather than the suction pressure used as atmospheric pressure. Since the brake fluid pressure in the gap 53 that has become the closed portion 53b immediately before the suction port 60 can be made closer to the suction pressure, the suction port passes through the range where the gap 53 becomes the closed portion 53b. It is possible to suppress the occurrence of pulsation caused by the hydraulic pressure difference when the valve 60 is communicated.

  Here, if the length of the sealing portions 100f and 101f in the circumferential direction around the rotation center of the rotary pump 10 can be set to a length that makes the gap portion 53 for one tooth the closed portion 53b, the gap portion The range where the volume of 53 expands disappears. For this reason, it is considered that the pulsation caused by the suction pressure and the negative pressure in the gap 53 can be prevented. However, in reality, the lengths of the sealed portions 100f and 101f must be set in consideration of manufacturing errors and assembly variations. Therefore, since negative pressure is always generated, the volume of the hydraulic pressure control unit 100g and 101g as in the present embodiment enables the brake fluid of the confining portion 53b to be immediately before the suction port 60 even if negative pressure is generated. It is effective to suppress the pulsation by bringing the pressure close to the suction pressure.

  The positions of the volume parts 100g and 101g in the sealed parts 100f and 101f are arbitrary, but the volume parts 100g and 101g are arranged at least in a region where the volume of the gap 53 increases as the rotary pump 10 rotates. It only has to be done.

  Also, the brake fluid pressure in the volume parts 100g and 101g is slightly reduced by communicating with the closing part 53b, but through the gaps between the end surfaces of the outer rotor 51 and the inner rotor 52 and the sealing parts 100f and 101f. Alternatively, when the gap portion 53 moves from the range where it becomes the closed portion 53b through the volume portions 100g and 101g to a place where it communicates with the suction port 60, the brake fluid is filled through the gap portion 53 communicated with the suction port 60. Is done. For this reason, the brake fluid pressure of the volume portions 100g and 101g can be returned to the suction pressure (atmospheric pressure) before communicating with the gap portion 53 that becomes the next confinement portion 53b.

  As described above, in the present embodiment, the gap 53 is communicated with the volume parts 100g and 101g before the gap 53 moves from the range where the gap 53 becomes the closed part 53b to the place where it communicates with the suction port 60. I have to. As a result, the brake fluid pressure in the gap portion 53 that becomes the closed portion 53b can be increased to almost the brake fluid pressure in the volume portions 100g and 101g, and almost no negative pressure can be generated. Accordingly, the brake fluid pressure in the gap 53 that has become the closed portion 53b immediately before the suction port 60 can be made close to the suction pressure, and therefore, the suction port 60 passes through the range in which the gap 53 becomes the closed portion 53b. It is possible to suppress the occurrence of pulsation caused by the hydraulic pressure difference when communicating with each other.

(Second Embodiment)
A second embodiment of the present invention will be described. In this embodiment, the location of the volume parts 100g and 101g provided in the rotary pump 10 is changed with respect to the first embodiment, and the other parts are the same as those in the first embodiment. Only different parts will be described.

  Fig.7 (a) is a schematic diagram of the rotary pump 10 with which the brake device of this embodiment is equipped, FIG.7 (b) is BOB sectional drawing of Fig.7 (a). FIG. 8 is a graph showing a change in the brake fluid pressure (absolute pressure) of the confining portion 53b as the rotary pump 10 rotates. The structure and operation of the rotary pump 10 of this embodiment will be described with reference to FIGS. 7 and 8 and FIG. 5 shown in the first embodiment.

  In the first embodiment, the volume portions 100g and 101g are provided for the sealed portions 100f and 101f that are located between the time when the gap 53 is communicated with the suction port 60 and the state when the gap 53 is communicated with the discharge port 61. Structure. Thereby, generation | occurrence | production of the pulsation resulting from the hydraulic pressure difference of the confinement part 53b and the suction inlet 60 is suppressed. On the other hand, in the present embodiment, as shown in FIGS. 7A and 7B, the gap 53 is positioned between the state in which it is communicated with the suction port 60 and the state in which it is communicated with the discharge port 61. The sealing portions 100e and 101e are provided with volume portions 100g and 101g.

  In the case of the rotary pump 10 having such a configuration, the gap portion 53 communicated with the suction port 60 moves with rotation and is sandwiched and sealed between the sealing portions 100e and 101e, whereby the closing portion 53a. Is configured. The volume of the gap 53 changes with the rotation. At this time, as shown in FIG. 5, there is a process in which the volume of the gap portion 53 gradually decreases from the range of the closed portion 53 a to the inside of the discharge port 61. For this reason, the brake fluid pressure rises due to the reduction of the volume of the gap portion 53 that becomes the closed portion 53b, and an excessive pressure is generated.

  However, in the present embodiment, since the sealed portions 100e and 101e are provided with the volume portions 100g and 101g, when the rotation further proceeds, the gap portion 53 that becomes the closed portion 53a is communicated with the volume portions 100g and 101g. For this reason, the brake fluid pressure in the gap portion 53 that becomes the closed portion 53a is determined by the volume of the gap portion 53, the volumes of the volume portions 100g and 101g, and the amount of brake fluid existing therebetween. Therefore, as shown in FIG. 8, the brake fluid pressure in the gap 53 formed as the confining portion 53a can be reduced to almost the brake fluid pressure in the volume portions 100g and 101g, and almost no excessive pressure is generated. It becomes possible.

  Thereafter, the brake fluid pressure slightly increases with the volume change of the gap portion 53 until the gap portion 53 moves from the range where the gap portion 53 becomes the closed portion 53a to the place where it is communicated with the discharge port 61. Since not only the volume in the part 53b but also the volumes of the volume parts 100g and 101g can be determined, the brake fluid pressure in the confining part 53b can be made substantially close to the discharge pressure.

  Therefore, it is possible to suppress the brake fluid pressure in the closing portion 53b from being excessively higher than the discharge pressure as the rotary pump 10 rotates. Since the brake fluid pressure in the gap portion 53 that has become the closed portion 53a immediately before the discharge port 61 can be made close to the discharge pressure, the discharge port 61 passes through the range in which the gap portion 53 becomes the closed portion 53a. It is possible to suppress the occurrence of pulsation caused by the hydraulic pressure difference when communicating with each other.

  In this embodiment, the positions of the volume parts 100g and 101g in the sealed parts 100e and 101e are arbitrary, but at least in the region where the volume of the gap part 53 decreases as the rotary pump 10 rotates. 100g and 101g should just be arrange | positioned.

  Further, the brake fluid pressure in the volume parts 100g and 101g is also slightly increased by communicating with the gap part 53 that becomes the closed part 53a, but the end faces of the outer rotor 51 and the inner rotor 52 and the sealed parts 100e and 101e. , Or when the gap 53 moves from the range where the gap 53 becomes the closed part 53a via the volume parts 100g and 101g to a place where the gap 53 communicates with the discharge port 61, the gap part communicated with the discharge port 61 The brake fluid is filled through 53. For this reason, before communicating with the gap portion 53 that becomes the next confining portion 53a, the brake fluid pressure of the volume portions 100g and 101g can be returned to the discharge pressure.

(Third embodiment)
A third embodiment of the present invention will be described. In the present embodiment, the seal structure of the rotary pump 10 and the location of the volume portion are changed with respect to the first embodiment, and the others are the same as those in the first embodiment, and therefore different from the first embodiment. Only the part will be described.

  FIG. 9 is a cross-sectional view of the rotary pump 10 provided in the brake device of the present embodiment, and is a view corresponding to the cross section A-O-A in FIG.

  As shown in this figure, in this embodiment, the seal member 101 is not provided for the second side plate portion 72, and the outer rotor 51 and the inner rotor 52 are in direct contact with the second side plate portion 72. By doing so, mechanical sealing is performed. Then, the volume portion 100g is provided in the sealing portion 100f of the resin member 100b of the seal member 100 provided in the first side plate portion 71, and a place (slider) corresponding to the confinement portion 53b in the second side plate portion 72 is provided. The structure is provided with a volume portion 72c by recessing the contact surface 72d).

  Thus, also when it is set as the structure which employ | adopted the mechanical seal, it can be set as the structure which equips the 2nd side plate part 72 with the volume part 72c directly. Even with such a structure, the same effect as in the first embodiment can be obtained.

(Other embodiments)
In each of the above embodiments, an example of the structure of the volume parts 100g and 101g has been described. However, the shape, depth, and the like can be appropriately changed.

  In the first embodiment, the volume portions 100g and 101g are provided in the sealed portions 100f and 101f, and in the second embodiment, the volume portions 100g and 101g are provided in the sealed portions 100e and 101e. The structures of the first and second embodiments may be combined to form the volume portions 100g and 101g in the sealed portions 100e, 100f, 101e, and 101f, respectively. Furthermore, it is good also as a structure provided only with one volume part 100g of the resin part 100b of the sealing member 100 by the side of the 1st side plate 71, or resin part 100b of the sealing member 101 by the side of the 2nd side plate 72. . Further, when the mechanical seal shown in the third embodiment is adopted, one of the volume portions 100g, 72c of the resin portion 100b of the seal member 100 on the first side plate 71 side and the second side plate 72 is used. It is good also as a structure provided only with.

  Further, without providing the seal members 100 and 101, the both side plates 71 and 72 have the same mechanical seal structure as described above, and a volume portion is provided on at least one of the sliding contact surfaces of the side plates 71 and 72. Also good.

  In the said embodiment, although the sealing members 100 and 101 are comprised in the annular | circular shape, other than such a shape may be sufficient. That is, the sealing members 100 and 101 may have any shape as long as the seal members 100 and 101 pass between the discharge port 61 and the drive shaft 54 and through the closed portions 53 a and 53 b and reach the outer periphery of the outer rotor 51. However, by reducing the amount of portions that do not need to be sealed, such as the discharge port 61, the suction port 60, and the outer periphery of the outer rotor 51 that is to have the same pressure as the discharge port 61 or the suction port 60 with a seal member. It is possible to reduce the contact resistance. Moreover, the circumference | surroundings of the rotation center axis | shaft of the outer rotor 51 and the inner rotor 52 can be sealed over the perimeter by making the sealing members 100 and 101 into an annular | circular shape. For this reason, a thin part is provided in the radial direction one side of the sealing members 100 and 101, and it becomes possible to form easily the thin part which can be displaced.

  Further, in each of the above embodiments, the trochoid pump has been described as an example of the internal gear pump. However, the present invention is not limited to this, and the present invention may be applied to an internal gear pump having another structure. Moreover, in each said embodiment, the rotary pump 10 of the structure where the inlet port 60 is arrange | positioned at the inner peripheral side of the seal parts 100 and 101, and the discharge port 61 is arrange | positioned at the outer peripheral side of the seal parts 100 and 101 is taken as an example. As described above, the suction port 60 may be disposed on the outer peripheral side of the seal portions 100 and 101, and the discharge port 61 may be disposed on the inner peripheral side of the seal portions 100 and 101.

  DESCRIPTION OF SYMBOLS 1 ... Brake pedal, 2 ... Booster device, 3 ... Master cylinder, 4, 5 ... Wheel cylinder, 10 ... Rotary pump, 50 ... Casing, 50a ... Rotor chamber, 51 ... Outer rotor, 51a ... Internal tooth part, 52 ... inner rotor, 52a ... external teeth, 53 ... gap, 53a, 53b ... closed part, 54 ... drive shaft, 60 ... suction port, 61 ... discharge port, 71 ... first side plate part, 72 ... first 2 side plate part, 72c ... volume part, 73 ... center plate, 80, 81 ... sealing member, 100, 101 ... sealing member, 100a, 101a ... elastic member, 100b, 101b ... resin member, 100c, 101c ... concave part, 100d, 101d ... convex part, 100e, 100f, 101e, 101f ... sealed part, 72c, 100g, 101g ... volume part

Claims (7)

An outer rotor (51) having an inner tooth portion (51a) on an inner periphery, and an inner rotor (52) having an outer tooth portion (52a) and rotating around a drive shaft (54), the inner teeth A rotating part configured to be assembled so as to form a plurality of gaps (53) by meshing the part and the external tooth part;
And having openings (71a, 72a) into which the drive shaft is fitted, a suction port (60) for sucking fluid into the rotating portion, and a discharge port (61) for discharging the fluid from the rotating portion, A casing (50) covering the rotating part,
Among the plurality of gaps, the pressure difference between the suction port and the discharge port is maintained by the closed portion (53b) on the side with the smallest volume and the closed portion (53a) on the side with the largest volume. However, it is a rotary pump configured to suck the fluid from the suction port by the rotational movement of the rotating unit and discharge the fluid through the discharge port,
The casing is disposed in a seal groove (71b, 72b) formed on a surface corresponding to the axial end surfaces of the outer rotor and the inner rotor, and the axial end surfaces of the inner rotor and the outer rotor and the casing. When viewed in the axial direction, the gap between the nozzles passes between the discharge port and the drive shaft and passes through the confining part to reach the outer periphery of the outer rotor, and the confining parts (53a, 53b) And sealing means (100, 101) having a sealing portion (100e, 100f, 101e, 101f) having a sliding contact surface which is slidably in contact with the axial end surfaces of the outer rotor and the inner rotor. And
The sealing part that covers at least the confining part on the side where the volume is minimum among the sealing parts of the sealing means is configured by a recess that opens in the sliding contact surface, and is in a sealed state with the rotational movement. A volume portion (100 g, 101 g) that is in communication with the gap portion that is the confined portion ;
The rotary pump according to claim 1, wherein the volume portion is disposed only in a region where the volume of the gap portion serving as a confinement portion on the side where the volume is minimized increases . The volume portion, when the gap portion becomes the closed portion has been communicated to the inlet port from through said volume portion with the rotary movement, that communicates with the suction port through the airspace The rotary pump according to claim 1 . 3. The rotary pump according to claim 1, wherein an opening of the volume part is provided only on the sliding contact surface and terminates inside the sealed part. 4. The sealing means is provided only on one end face of the casing in the axial direction of the outer rotor and the inner rotor, and the other end face of the casing is in direct contact with the outer rotor and the inner rotor. The sealing portion is sealed by covering the confining portions (53a, 53b) among the end surfaces to be mechanically sealed, and sliding with the axial end surfaces of the outer rotor and the inner rotor. The sliding contact surface comprises a volume part (72c) that is configured by an indent opening to be communicated with the gap part of the confining part in a sealed state with the rotational movement. The rotary pump according to any one of claims 1 to 3 . An outer rotor (51) having an inner tooth portion (51a) on an inner periphery, and an inner rotor (52) having an outer tooth portion (52a) and rotating around a drive shaft (54), the inner teeth A rotating part configured to be assembled so as to form a plurality of gaps (53) by meshing the part and the external tooth part;
And having openings (71a, 72a) into which the drive shaft is fitted, a suction port (60) for sucking fluid into the rotating portion, and a discharge port (61) for discharging the fluid from the rotating portion, A casing (50) covering the rotating part,
Among the plurality of gaps, the pressure difference between the suction port and the discharge port is maintained by the closed portion (53b) on the side with the smallest volume and the closed portion (53a) on the side with the largest volume. However, it is a rotary pump configured to suck the fluid from the suction port by the rotational movement of the rotating unit and discharge the fluid through the discharge port,
The end surfaces of the casing corresponding to the axial end surfaces of the outer rotor and the inner rotor are mechanical seals that seal the end surfaces directly in contact with the outer rotor and the inner rotor. Of the end surfaces, the confined portions (53a, 53b) are covered to seal them, and are formed by dents that open on the sliding contact surfaces that are in sliding contact with the axial end surfaces of the outer rotor and the inner rotor. with the, the gap portion and volume unit is communicated with the closed portion is in a closed state (72c) is provided with al will,
The volume portion is formed in a portion sealing at least the closed portion on the side where the volume is minimized among the closed portions, and the gap portion serving as the closed portion on the side where the volume is minimized. A rotary pump characterized by being arranged only in an area where the volume increases . The volume portion, when the gap portion becomes the closed portion has been communicated to the inlet port from through said volume portion with the rotary movement, that communicates with the suction port through the airspace The rotary pump according to claim 5 . Brake fluid pressure generating means (1-3) for generating brake fluid pressure based on the pedal effort;
Braking force generating means (4, 5) for generating a braking force on the wheel based on the brake fluid pressure;
A main line (A) connected to the brake fluid pressure generating means and transmitting the brake fluid pressure to the braking force generating means;
An auxiliary pipeline (C, D) connected to the brake fluid pressure generating means and supplying brake fluid to the main pipeline side in order to increase the braking force generated by the braking force generating means;
In the rotary pump, the suction port can suck the brake fluid on the brake fluid pressure generating means side through the auxiliary conduit, and the discharge port can discharge the brake fluid toward the braking force generating device through the main conduit. The brake device provided with the rotary pump according to claim 5 or 6 , wherein the brake device is arranged as described above.

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