JP2007125929A - Vehicle brake device using rotary pump - Google Patents

Vehicle brake device using rotary pump Download PDF

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Publication number
JP2007125929A
JP2007125929A JP2005318438A JP2005318438A JP2007125929A JP 2007125929 A JP2007125929 A JP 2007125929A JP 2005318438 A JP2005318438 A JP 2005318438A JP 2005318438 A JP2005318438 A JP 2005318438A JP 2007125929 A JP2007125929 A JP 2007125929A
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Japan
Prior art keywords
cylinder
pump
case
side
brake device
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JP2005318438A
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Japanese (ja)
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JP4508083B2 (en
Inventor
Takeshi Fuchida
Hideki Igai
Taku Sato
Shigeki Torii
Takahiro Yamaguchi
卓 佐藤
貴洋 山口
剛 渕田
英己 猪飼
重希 鳥居
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Advics:Kk
株式会社アドヴィックス
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Priority to JP2005318438A priority Critical patent/JP4508083B2/en
Priority claimed from US11/589,237 external-priority patent/US7530647B2/en
Publication of JP2007125929A publication Critical patent/JP2007125929A/en
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Publication of JP4508083B2 publication Critical patent/JP4508083B2/en
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Abstract

<P>PROBLEM TO BE SOLVED: To provide a vehicle brake device capable of decreasing the pump length of a pump body unitizing a rotary pump. <P>SOLUTION: The brake device is constituted so that a disc spring 210 is disposed between a third cylinder 71c and a fourth cylinder 71d. The space is effectively utilized thereby and the total axial length (pump axial length) of the pump body 100 including the third cylinder 71c, the fourth cylinder 71d and the disc spring 210 can be shortened compared to the conventional case where the disc spring 210 is disposed at the tip end position of the pump body 100. <P>COPYRIGHT: (C)2007,JPO&INPIT

Description

  The present invention relates to a vehicle brake device that performs brake hydraulic pressure control using a rotary pump such as a trochoid pump.

  In recent years, for example, a rotary pump such as a trochoid pump has been used as a brake fluid pressure control pump in a vehicle brake device in order to reduce operation noise during brake fluid pressure control such as ABS control. ing.

  A vehicle brake device using such a rotary pump is proposed in Patent Document 1. FIG. 5 is a diagram showing a cross-sectional configuration of a pump main body J100 of a rotary pump provided in the vehicle brake device disclosed in Patent Document 1. As shown in FIG.

  As shown in this figure, the pump main body J100 includes a unit in which two rotary pumps J10 and J13 and a drive shaft J54 of the rotary pumps J10 and J13 are accommodated in cylindrical cases J71a to 71d, J72a and J72b. The unitized pump body J100 is fixed to the housing J150 by being inserted into the recess J150a of the housing J150 constituting the vehicle brake device.

  At this time, a large axial force must be secured in order to prevent the pump body J100 from rattling inside the housing J150 due to a high brake fluid pressure during the suction and discharge of the brake fluid by the pump body J100.

However, if the axial force is obtained by screw tightening, large variations in the axial force may occur. For this reason, by disposing the leaf spring J210 at the tip position or the root position of the pump body J100, the axial force of the pump body J100 can be secured while the axial force is stabilized and the axial force applied to the pump body J100. Is made to be the minimum necessary without becoming excessive.
JP 2001-80498 A

  However, since the plate spring J210 is arranged at the tip position or the root position, the pump length in the axial direction of the pump body J100 is increased in order to arrange the plate spring J210. For this reason, the pump body J100 cannot be downsized, and thus the vehicle brake device cannot be downsized sufficiently.

  An object of the present invention is to provide a vehicle brake device that can reduce the pump length of a pump body in which a rotary pump is unitized.

  In order to achieve the above object, according to the first aspect of the present invention, a cylindrical first case (71a, 71b, 71c, 73a, 73b) that accommodates a plurality of rotary pumps is coaxial with the first case. The pump body (100) is configured by including the second case (71d) disposed and the spring means (210) disposed between the first case and the second case, and the housing is formed by the fixing means (200). On the inlet side of the recess (150a) of (150), the second case is pressed and fixed toward the insertion direction of the pump body.

  As described above, by arranging the spring means between the first case and the second case, the space can be effectively used as compared with the case where the spring means is arranged at the tip or the root of the pump means. For this reason, compared with the case where a spring means is arrange | positioned in the front-end | tip position or root position of a pump main body, the total axial direction length (pump shaft length) of a pump main body including a spring means can be shortened. Therefore, it is possible to provide a vehicle brake device that can reduce the pump length of the pump body in which the rotary pump is unitized.

  For example, as shown in claim 2, the plurality of rotary pumps includes a first rotary pump (10) and a second rotary pump (13). In this case, the first case is disposed adjacent to the first cylinder (71a) in which the first center hole (72a) in which the drive shaft is inserted is formed, and the first cylinder. A first central plate (73a) that accommodates the rotating portion; a second cylinder (71b) that is disposed adjacent to the first central plate and has a second central hole (72b) into which the drive shaft is inserted; A second central plate (73b) that is disposed adjacent to the second cylinder and accommodates the rotating portion of the second rotary pump, and a third central plate that is disposed adjacent to the second central plate and into which the drive shaft is inserted. A unit having a third cylinder (71c) in which a center hole (72c) is formed and in which the first cylinder, the first center plate, the second cylinder, the second center plate, and the third cylinder are integrated. It is said. The second case includes a fourth cylinder (71d) that is disposed adjacent to the first center plate and has a fourth center hole (72d) into which the drive shaft is inserted. A spring means can be provided between the third cylinder and the fourth cylinder.

  Specifically, as shown in claim 3, a disc spring can be used as the spring means. In this case, among the disc springs, the bottom surface side of the disc spring that functions as the load receiving portion faces the first case side, and the upper surface side that functions as the load receiving portion of the disc spring faces the second case side. Such an arrangement is preferable.

  That is, for example, the reaction force when the pump body is pressed against the bottom surface of the recess of the housing causes the outer periphery of the first cylinder, the first center plate, the outer periphery of the second cylinder, the outer periphery of the second center plate, and the third cylinder. Is transmitted to the disc spring side. At this time, since the load can be received on the bottom surface side of the disc spring, that is, the outer peripheral side of the third cylinder, the load can be reliably received and the deformation of the third cylinder can be prevented.

  For example, as shown in claim 5, the third cylinder side of the fourth cylinder may be partially reduced in diameter, and a disc spring may be provided in the reduced diameter part. In this case, as shown in claim 6, the third center hole of the third cylinder has an inner diameter that is equal to or slightly larger than the reduced diameter portion of the fourth cylinder on the fourth cylinder side. It can be set as the structure which can insert the diameter-reduced site | part of a 4th cylinder in a hole.

  According to a seventh aspect of the present invention, in the reduced diameter portion of the fourth cylinder, a sealing means (90) is provided between the fourth center hole and the drive shaft, and the disc spring is provided in the fourth cylinder. It can also be arranged on the outer peripheral side of the part where the sealing means is arranged.

  Thus, the space can be effectively utilized by arranging the disc spring in the dead space where nothing is arranged, that is, the outer peripheral position rather than the seal.

  The invention according to claim 8 is characterized in that a screw member (200) is screwed and fixed as a fixing means at an entrance of a recess formed in the housing, and the second case is pressed in the insertion direction of the recess by the screw member. It is said.

  In this way, the second case is pressed in the insertion direction of the recess by screwing and fixing the screw member, thereby generating an axial force and suppressing the variation of the axial force by the elastic force of the disc spring, thereby stabilizing the axial force. It becomes possible to make it.

  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.

  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)
DESCRIPTION OF THE PREFERRED EMBODIMENTS Embodiments shown in the drawings will be described below. FIG. 1 is a schematic diagram of a brake pipe of a vehicle brake device to which an internal gear pump (trochoid pump) is applied as a rotary pump. Hereinafter, 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 constituting an X-pipe hydraulic circuit including right front wheel-left rear wheel and left front wheel-right rear wheel piping systems 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 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 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-increasing control valves 30 and 31 are configured as two-position valves that can control the communication / blocking state by an ABS 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 pump discharge 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.

  A pipeline (suction pipeline) B connecting the pipeline A and the reservoir 40 between the first and second pressure increase control valves 30 and 31 and the wheel cylinders 4 and 5 is communicated by the ABS ECU. Depressurization control valves 32 and 33 that can control the shut-off state are 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 13 is disposed in a pipe line (refluxing pipe line) C connecting the linear differential pressure control valve 22 and the pressure increase control valves 30 and 31 in the pipe line A and the reservoir 40. A safety valve 13A is provided on the discharge port side of the rotary pump 13 so that the brake fluid does not flow backward. A motor 11 is connected to the rotary pump 13, and the rotary pump 13 is driven by the motor 11. In addition, the 2nd piping system is equipped with the rotary pump 10 (refer FIG. 2) comprised similarly to the rotary pump 13. As shown in FIG. Details of these rotary pumps 10 and 13 will be described later.

  A conduit (auxiliary conduit) D is provided so as to connect the 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 13 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 reservoir 40 is connected to the pipeline D to receive the brake fluid from the master cylinder 3 side, and the reservoir hole 40a is connected to the pipeline B and pipeline C to receive the brake fluid released from the wheel cylinders 4 and 5. 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 reservoir 40 configured in this manner, 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 reservoir 40. Therefore, more brake fluid than the suction capacity of the rotary pump 13 does not flow into the reservoir chamber 40c, and no high pressure is applied to the suction side of the rotary pump 13.

  Next, FIG. 2 shows a sectional view of the pump body 100 including the rotary pumps 10 and 13. This figure shows a state where the pump main body 100 is assembled to the housing 150 of the ABS actuator, and is assembled so that the vertical direction of the paper is the vehicle top-to-bottom direction. Hereinafter, the overall configuration of the pump body 100 will be described with reference to FIG.

  As described above, the brake device includes two systems, the first piping system and the second piping system. Therefore, the pump main body 100 is provided with two rotary pumps 13 for the first piping system shown in FIGS. 1 and 2 and the rotary pump 10 for the second piping system shown in FIG. ing. These rotary pumps 10 and 13 are driven by a single drive shaft 54.

  The casing constituting the outer shape of the pump body 100 is constituted by first, second, third, and fourth cylinders (side plates) 71a, 71b, 71c, and 71d and cylindrical first and second center plates 73a and 73b. Has been.

  The 1st cylinder 71a, the 1st center plate 73a, the 2nd cylinder 71b, the 2nd center plate 73b, and the 3rd cylinder 71c are piled up in order, and the circumference of the overlapping part is joined by welding. The welded unitized portion is used as a first case, and a disc spring 210 corresponding to a spring means is sandwiched between the first cylinder and the third cylinder 71c in the first case, and a fourth cylinder corresponding to the second case. 71d is arranged coaxially with respect to the first case. In this way, the integral pump body 100 is configured.

  The pump body 100 having such an integral structure is inserted into a substantially cylindrical recess 150a formed in the housing 150 for the brake fluid pressure control actuator.

  A ring-shaped male screw member 200 is screwed into a female screw groove 150 b dug in the inlet of the recess 150 a so that the pump body 100 is fixed to the housing 150. Specifically, a circular second recess 150 c is formed in the recess 150 a of the housing 150 at a position corresponding to the tip of the drive shaft 54 in the tip position in the insertion direction of the pump body 100. The diameter of the second recess 150c is larger than the drive shaft 54 but smaller than the outer diameter of the first cylinder 71a. For this reason, the tip of the drive shaft 54, that is, the portion protruding from the end surface of the first cylinder 71a enters the second recess 150c, and the portion of the bottom surface of the recess 150a other than the second recess 150c is the first cylinder 71a. The pump body 100 can obtain an axial force by screwing the male screw member 200.

  Here, regarding the structure for fixing the pump main body 100 to the recess 150a of the housing 150, since the disc spring 210 is provided, the disc spring 210 acts as follows.

  In order to fix the pump body 100 to the housing 150, in other words, to prevent the pump body 100 from rattling inside the housing 150 due to a high brake fluid pressure when the pump body 100 sucks and discharges the brake fluid, We must secure power.

  However, if the axial force is obtained only by tightening the male screw member 200, a large variation in the axial force may occur.

  On the other hand, in this embodiment, the disc spring 210 is arrange | positioned between the 3rd, 4th cylinders 71c and 71d, and the edge part by the side of the 3rd cylinder 71c among the 4th cylinders 71d is diameter-reduced, The part is inserted into a third center hole 72c of a third cylinder 71c described later. The diameter of the portion of the fourth cylinder 71d that is inserted into the third center hole 72c of the third cylinder 71c is set to be approximately the same as or slightly smaller than the diameter of the third center hole 72c. The four cylinders 71d are loosely fitted to the third center hole 72c of the third cylinder 71c.

  For this reason, when the male screw member 200 is screwed, the pump body 100 is fixed to the hole 150a of the housing 150 by the elastic force of the disc spring 210 disposed between the fourth cylinder 71d and the third cylinder 71c. Axial force is generated. In other words, a member located on the right side of the drawing with respect to the third cylinder 71c is pressed against the bottom surface of the recess 150a by the disc spring 210, and the fourth cylinder 71d is pressed against the male screw member 200 side by the disc spring, so that the axial force is increased. Be generated. Therefore, the axial force can be stabilized, and the axial force applied to the pump body 100 can be minimized without being excessive. Thereby, deformation of the pump body 100 can be suppressed.

  The direction of the disc spring 210 is such that the bottom side of the disc spring 210 (the side on which the load is applied to the outer periphery) faces the rotary pumps 10 and 13 and the upper side of the disc spring 210 (the side on which the load is applied to the inner periphery). Is configured to face the motor 11 side.

  The first to fourth cylinders 71a to 71d are provided with first, second, third, and fourth center holes 72a, 72b, 72c, and 72d, respectively. A bearing 51 is provided on the inner periphery of the first center hole 72a formed in the first cylinder 71a, and a bearing 52 is provided on the inner periphery of the third center hole 72c formed in the third cylinder 71c. Yes. These bearings 51 and 52 are comprised by the ball bearing narrower than a needle bearing.

  Both the bearing 51 and the bearing 52 are provided with seal plates 51a and 52a. With respect to the bearing 51, the seal plate 51a is located on the tip side of the drive shaft 54, and with respect to the bearing 52, the seal plate 52a is on the fourth cylinder 71d side. It is arranged to be directed to.

  3A and 3B are views showing only the third cylinder 71c. FIG. 3A is a perspective view of the third cylinder 71c, and FIG. 3B is a front view of the third cylinder 71c (the axial direction of the pump main body 100). Figure seen from).

  As shown in this figure, the third center hole 72c has a portion having an inner diameter equivalent to the outer diameter of the bearing 52 and a portion reduced than the inner diameter of the bearing 52, whereby the stepped portion is formed. It is configured. When the bearing 52 is pushed to the stepped portion, the bearing 52 enters the inside of the third center hole 72c, and a cavity remains on the fourth cylinder 71d side in the third center hole 72c. A part of the fourth cylinder 71d enters the cavity.

  The drive shaft 54 is fitted into the first to fourth center holes 72 a to 72 d and is supported by bearings 51 and 52. As described above, the bearings 51 and 52 are arranged on both sides of the rotary pumps 10 and 13.

  Note that a suction port 62, which will be described later, is also configured by the third cylinder 71c. The configuration of the suction port 62 will be described later in detail.

  Next, FIG. 4 is a cross-sectional view taken along the line AA of FIG. 2, and the configuration of the rotary pumps 10 and 13 will be described based on FIGS.

  The rotary pump 10 is disposed in a rotor chamber 50a formed by sandwiching both sides of a cylindrical first central plate 73a between a first cylinder 71a and a second cylinder 71b, and is driven by a drive shaft 54. It consists of a tangential gear pump (trochoid pump).

  Specifically, the rotary pump 10 includes a rotating portion including an outer rotor 10a having an inner tooth portion formed on the inner periphery and an inner rotor 10b having an outer tooth portion formed on the outer periphery, and the inner rotor 10b. The drive shaft 54 is inserted into the hole. A key 54b is inserted into a long hole 54a (see FIG. 2) in which the axial direction formed in the drive shaft 54 is a longitudinal direction, and torque transmission to the inner rotor 10b is achieved by this key 54b. It has become.

  The outer rotor 10a and the inner rotor 10b have a plurality of gaps 10c 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 10 c by the rotation of the drive shaft 54.

  On the other hand, the rotary pump 13 is disposed in a pump chamber 50b formed by sandwiching both sides of a cylindrical second central plate 73b between a third cylinder 71c and a fourth cylinder 71d. Similarly to the rotary pump 10, the rotary pump 13 is also composed of an internal gear pump having an outer rotor 13a and an inner rotor 13b, and is arranged by rotating the rotary pump 10 by 180 ° around the drive shaft 54. It has become. By arranging in this way, the suction-side gap 10c and the discharge-side gap 10c of each of the rotary pumps 10 and 13 are symmetric with respect to the drive shaft 54, so that the high-pressure on the discharge side is high. The force applied to the drive shaft 54 by the brake fluid pressure can be offset.

  The first cylinder 71 a is formed with a suction port 60 that communicates with the suction-side gap 10 c of the rotary pump 10. The suction port 60 is formed so as to penetrate from the end surface on the rotary pump 10 side of the first cylinder 71a to the end surface on the opposite side. For this reason, the brake fluid is introduced with the end surface of the suction port 60 opposite to the end surface on the rotary pump 10 side as an inlet.

  The suction port 60 is connected to a suction conduit 151 formed so as to reach the bottom surface of the recess 150 a with respect to the housing 150.

  The second cylinder 71 b is provided with a discharge port 61 that communicates with the gap 10 c on the discharge side of the rotary pump 10. The discharge port 61 extends from the end surface on the rotating portion side of the rotary pump 10 to the outer peripheral surface. Specifically, the discharge port 61 is configured as follows.

  An annular groove (first annular groove) 61 a formed so as to surround the drive shaft 54 is provided on the end surface of the rotary pump 10 on the rotating part side of the first cylinder 71 a and the second cylinder 71 b.

  In this annular groove 61a, a ring-shaped seal member 171 is provided so as to sandwich the outer rotor 10a and the inner rotor 10b. The seal member 171 includes a resin member 171a disposed on the rotating portion side and a rubber member 171b that presses the resin member 171a toward the rotating portion side. The inner peripheral side of the seal member 171 includes a gap between the outer periphery of the outer rotor 10a and the central plate 73a facing the suction-side gap 10c and the suction-side gap 10c. Includes a gap between the outer periphery of the outer rotor 10a facing the discharge-side gap 10c and the discharge-side gap 10c and the central plate 73a. That is, the seal member 171 is configured to seal the relatively low pressure portion and the relatively high pressure portion of the inner and outer circumferences of the seal member 171.

  Further, the seal member 171 is configured to be in contact with the inner periphery of the annular groove 61a and to be in contact with only a part of the outer periphery, and a portion of the annular groove 61a that is not partially in contact with the outer periphery side of the seal member 171 is There is a gap. That is, the annular groove 61a has a region configured so that the entire outer periphery does not come into contact with the seal member 171, and the brake fluid can flow in this region. Further, a pipe 61b is drawn from a part of the annular groove 61a to the first cylinder 71a. The discharge port 61 is configured by the gap between the annular groove 61a configured as described above and the pipeline 61b.

  The discharge port 61 is a discharge pipe formed in the housing 150 via an annular groove 162 formed in the entire circumference of the inner peripheral surface of the recess of the housing 150 where the tip position of the pump body 100 is disposed. It is connected to the path 152.

  In addition, a discharge port 63 communicating with the gap on the discharge side is provided on the end surface of the second cylinder 71b opposite to the end surface where the discharge port 61 is formed.

  The discharge port 63 is formed from the end surface of the second cylinder 71b to the outer peripheral surface. The discharge port 63 is formed in the same structure as the discharge port 61 described above, and the gap between the annular groove 63a that accommodates the ring-shaped seal member 172 including the resin member 172a and the rubber member 172b, and the annular groove 63a. It is comprised from the pipe line 63b pulled out from the uppermost position. The discharge port 63 is connected to the discharge conduit 154 via an annular groove 163 formed in the entire periphery of the inner peripheral surface of the recess 150a of the housing 150 facing the outer periphery of the center plate 73b.

  The third cylinder 71 c is provided with a suction port 62 that communicates with a suction side gap of the rotary pump 13.

  The suction port 62 is formed so as to penetrate from the end face on the rotary pump 13 side to the opposite end face of the third cylinder 71c and to the outer peripheral face of the third cylinder 71c on the opposite end face.

  Specifically, the suction port 62 is configured by utilizing a third center hole 72c formed in the third cylinder 71c, and is configured by expanding the diameter of the third center hole 72c to form a groove. ing. As shown in FIGS. 3A and 3B, the third center hole 72c of the third cylinder 71c has an oval shape on the rotary pump 13 side. Since the drive shaft 54 is disposed along the semicircular shape at one end of the oval, the semicircular shape at the other end is partially enlarged in diameter than the drive shaft 54. Yes. The portion where the diameter is enlarged is larger than the outer periphery of the bearing 52. In addition, about the shape of the 3rd center hole 72c here, although the edge part which does not follow the drive shaft 54 was made into circular arc shape, it is good also as rectangular shape.

  The third center hole 72c is expanded in diameter so as to have the same diameter as the bearing 52 at an intermediate position of the third cylinder 71c, and is long on the end surface of the third cylinder 71c opposite to the rotary pump 13 side. The circular end is connected to a groove reaching the outer peripheral surface. This groove is formed by, for example, a rectangular cross section or an oval semicircular shape, but in this embodiment, it is a rectangular cross section.

  The suction port 62 is a portion that is not blocked even when the drive shaft 54 is disposed in the third center hole 72c, that is, a crescent-shaped portion, and a portion of the third cylinder 71c that is opposite to the rotary pump 13 side. It is comprised by the groove | channel extended to the outer peripheral surface in the end surface. For this reason, the brake fluid is introduced with the outer peripheral surface side of the third cylinder 71c of the suction port 62 as the inlet. The suction port 62 is a suction pipe formed in the housing 150 via an annular groove 164 formed on the entire inner peripheral surface of the recess 150a of the housing 150 so as to include the position of the inlet of the suction port 62. It is connected to the path 153.

  In FIG. 2, a suction conduit 153 and a discharge conduit 154 correspond to the conduit C in FIG.

  As described above, by configuring the suction port 62 using the third center hole 72c, the brake fluid is supplied to the drive shaft 54, the bearing 52, and the like, so that the drive shaft 54 rotates smoothly. Further, since the suction port 62 is located closer to the motor 11 (outside the housing 150) than the discharge port 63, the brake fluid pressure in the portion near the outside of the housing 150 can be lowered.

  The second center hole 72b of the second cylinder 71b is partially made larger in diameter than the drive shaft 54, and the first rotary pump 10 and the second rotary pump 13 are placed in the enlarged part. A sealing member 80 is stored. The seal member 80 is obtained by fitting an O-ring 81, which is a ring-shaped elastic member, into a ring-shaped resin member 82 in which a groove portion having a radial direction as a depth direction is formed. The resin member 82 is pressed by force so as to come into contact with the drive shaft 54.

  Although not shown, for example, the cross-sectional shapes of the resin member 82 and the third center hole 72c of the third cylinder 71c are both circular arcs having a circular cutout, and the third cylinder 71c has a third shape. The resin member 82 is configured to be fitted into the center hole 72c. For this reason, the notch part of the resin member 82 plays a role as a key, and the seal member 80 is configured not to rotate relative to the third cylinder 71c.

  The fourth cylinder 71d is recessed on the surface opposite to the surface on which the disc spring 210 is disposed, and the drive shaft 54 is protruded from the recess. The drive shaft 54 is provided with a key-shaped connection portion 54c at the protruding end, and the drive shaft 11a of the motor 11 is inserted into the connection portion 54c. A single drive shaft 54 is rotated by the motor 11 via the drive shaft 11a, and the rotary pumps 10 and 13 are driven.

  The diameter of the inlet of the recessed portion of the fourth cylinder 71d is the same as the hole 11c formed in the holder 11b of the motor 11, and the recessed portion of the fourth cylinder 71d and the hole 11c of the holder 11b of the motor 11 The bearing 180 is arranged with a small gap between them, and the drive shaft 11a is pivotally supported. In this example, the drive shaft 11a is pivotally supported by the bearing 180, but the drive shaft 54 may be pivotally supported.

  Thus, when the bearing 180 is disposed in the hole 11c formed in the holder 11b of the motor 11 and the recessed portion of the fourth cylinder 71d, the motor 11 and the fourth cylinder 71 are positioned in the radial direction. Thus, the axial displacement between the 11 drive shafts 11a and the drive shaft 54 can be minimized.

  Further, an oil seal 90 and an oil seal 91 are aligned and fixed in the axial direction of the drive shaft 54 so as to cover the outer periphery of the drive shaft 54 in a recess formed in the fourth cylinder 71d. The oil seal 90 serves to seal the brake fluid leaking from the suction port 62 through the center hole 72d. The oil seal 91 serves as a seal for blocking the inside and outside of the pump body 100.

  Furthermore, O-rings 74a, 74b, 74c, and 74d are disposed on the outer peripheral surfaces of the first to fourth cylinders 71a to 71d, respectively. These O-rings 74 a to 74 d seal the brake fluid in suction pipes 151, 153 and discharge pipes 152, 154 formed in the housing 150, and the suction pipe 151 and the discharge pipe 152. Between the discharge conduit 152 and the discharge conduit 154, between the discharge conduit 154 and the suction conduit 153, and between the suction conduit 153 and the outside of the housing 150.

  In addition, the outer peripheral surface of the front end on the inlet side of the recessed portion of the fourth cylinder 71d is reduced in diameter to form a stepped portion. The ring-shaped male screw member 200 described above is fitted into the reduced diameter portion, and the pump body 100 is fixed.

  Next, the operation of the brake device and the pump body 100 configured as described above will be described.

  The brake device is at the time of ABS control in which the wheel tends to be locked, or when a large braking force is required (for example, when the braking force corresponding to the brake pedal force cannot be obtained or the operation amount of the brake pedal 1 is large). , The pump body 100 is driven to suck and discharge the brake fluid in the reservoir 40. Then, the pressure of the wheel cylinders 4 and 5 is increased by the discharged brake fluid.

  At this time, in the pump body 100, the basic pump operation is such that the rotary pumps 10 and 13 suck the brake fluid through the suction pipes 151 and 153 and discharge the brake fluid through the discharge pipes 152 and 154. Do.

  At this time, in the rotary pumps 10 and 13, the pressure on the discharge side becomes very large. For this reason, the brake fluid pressure acts in a direction in which the pump main body 100 is removed from the housing 150. However, as described above, the axial force of the pump main body 100 is ensured by the disc spring 210 and the male screw member 200. It is possible to prevent the 100 from rattling in the housing 150.

  In the case of this embodiment, on the motor 11 side with respect to the rotary pump 10, the cylinder parts constituting the outer shape of the pump body 11 are not constituted by one part, but two parts such as a third cylinder 71c and a fourth cylinder 71d. The disc spring 210 is disposed between the third cylinder 71c and the fourth cylinder 71d.

  In the pump body provided in the conventional vehicle brake device, as shown in FIG. 5, the cylinder part constituting the outer shape of the pump body is constituted by one part on the motor side of the rotary pump, and the suction port is provided in this part. The structure is formed. Therefore, since the cylinder parts must be provided with bearings and seals, the length in the axial direction has to be large, but there is a space where nothing is arranged at the outer peripheral position than the bearings and seals. A dead space was formed.

  On the other hand, in this embodiment, since the disc spring 210 is arranged between the third cylinder 71c and the fourth cylinder 71d, the space can be effectively used. For this reason, compared with the case where the disc spring 210 is arrange | positioned in the front-end | tip position of the pump main body 100, the total axial direction length (pump shaft of the pump main body 100 including the 3rd cylinder 71c, the 4th cylinder 71d, and the disc spring 210). (Length) can be shortened.

  In such a structure, the disc spring 210 is oriented such that the bottom side of the disc spring 210 (the side on which the outer peripheral portion is loaded) faces the rotary pumps 10 and 13 and the top side of the disc spring 210 (inner circumference). The side on which the load is applied to the part) faces the motor 11 side.

  If the disc spring 210 is configured such that the upper surface side of the disc spring 210 faces the rotary pumps 10 and 13 and the bottom surface side of the disc spring 210 faces the motor 11 side, the following problems occur. there's a possibility that.

  That is, for example, the reaction force when the pump body 100 is pressed against the bottom surface of the recess 150a causes the outer periphery of the first cylinder 71a, the first center plate 73a, the outer periphery of the second cylinder 71b, the second center plate 73b, and the third When transmitted to the disc spring 210 side via the outer peripheral portion of the cylinder 71c, this load must be received on the upper surface side of the disc spring 210. In this case, since the position where the load is applied is on the outer peripheral side of the third cylinder 71c, the position where the load is received is on the inner peripheral side of the third cylinder 71c, so that the displacement of the third cylinder 71c is possible. There is sex.

  On the other hand, in this embodiment, the load can be received on the bottom surface side of the disc spring 210, that is, on the outer peripheral side of the third cylinder 71c. For this reason, the load can be reliably received on the bottom surface side of the disc spring 210, and the deformation of the third cylinder 71c can be prevented.

  In the case of such a structure, as shown in FIG. 3, the third cylinder 71c has a simple shape in which the third center hole 72c is formed in the cylindrical part. For this reason, it is possible to form the third cylinder 71c only by simple plastic working, and it is not necessary to form the suction port 62 from the outer peripheral surface of the third cylinder 71c by drilling.

  Further, as can be seen from the conventional pump body, since the suction port is formed by providing an oil passage that is orthogonal from the end surface side and the outer peripheral surface side of the cylinder part, a varistor is formed at the portion where the oil passage intersects. However, if the structure of this embodiment is used, it is not necessary.

  Similarly, the fourth cylinder 71d has a simple shape in which a center hole 72d is formed in the cylindrical part. For this reason, the 4th cylinder 71d can be formed only by simple plastic processing.

  Accordingly, the third and fourth cylinders 71c and 71d can be easily formed, and in addition, the occurrence of burrs can be prevented, and therefore various problems caused by the burrs being mixed into the brake fluid. It can also be prevented.

  Furthermore, in this embodiment, the bearings 51 and 52 are constituted by ball bearings. For this reason, compared with the case where a needle bearing is used, it becomes possible to shorten the axial direction.

(Other embodiments)
In the above embodiment, the pump main body 100 is fixed to the housing 150 by screwing the male screw member 200 into the female screw groove 150b formed in the concave portion of the housing 150, but other methods, for example, the concave portion 150a You may fix by caulking an inner peripheral surface.

  In addition, although the said embodiment gave and demonstrated the thing provided with two rotary pumps 10 and 13 as an example, the number beyond it may be sufficient.

It is the partial cross section schematic diagram which showed the piping structure of the brake device for vehicles in 1st Embodiment of this invention. A sectional view of a pump body 100 including the rotary pumps 10 and 13 shown in FIG. 1 is shown. (A) is a perspective view of the third cylinder 71c, and (b) is a front view of the third cylinder 71c (viewed from the axial direction of the pump body 100). It is AA sectional drawing of FIG. It is sectional drawing of the pump main body with which the conventional brake device for vehicles was equipped.

Explanation of symbols

  DESCRIPTION OF SYMBOLS 100 ... Pump main body 10, 13 ... Rotary pump, 10a ... Outer rotor, 10b ... Inner rotor, 10c ... Gap part, 51, 52 ... Bearing, 54 ... Drive shaft, 60, 62 ... Suction port, 61, 63 ... Discharge port, 71a-71d ... 1st-4th cylinder, 72a-72d ... 1st-4th center hole, 73a, 73b ... Center plate, 90, 91 ... Seal member, 150 ... Housing, 150a ... Recessed part, 151- 154 ... pipe line, 210 ... disc spring.

Claims (8)

  1. Including an inner rotor (10b, 13b) having an outer tooth portion formed on the outer periphery and an outer rotor (10a, 13a) having an inner tooth portion formed on an inner periphery, and biting the inner tooth portion and the outer tooth portion Rotation part which forms a plurality of gap parts (10c) by combining, a suction port (60, 62) for sucking brake fluid into the rotation part, and a discharge port for discharging brake fluid from the rotation part ( 61, 63), and a plurality of rotary pumps (10, 13),
    A plurality of rotary pumps are housed together with a single drive shaft (54) to drive the inner rotor of each of the plurality of rotary pumps, and a cylindrical shape that houses the plurality of rotary pumps. A first case (71a, 71b, 71c, 73a, 73b) and a second case (71d) arranged coaxially with the first case are provided, and between the first case and the second case. A pump body (100) configured with spring means (210)
    A housing (150) formed with a recess (150a) into which the pump body is inserted with the first case side as a tip;
    A vehicular brake device comprising fixing means (200) for pressing and fixing the second case in the insertion direction of the pump body on the inlet side of the recess of the housing.
  2. The plurality of rotary pumps includes a first rotary pump (10) and a second rotary pump (13),
    The first case is
    A first cylinder (71a) having a first center hole (72a) into which the drive shaft is inserted;
    A first central plate (73a) disposed adjacent to the first cylinder and containing the rotating part of the first rotary pump;
    A second cylinder (71b) disposed adjacent to the first central plate and having a second central hole (72b) into which the drive shaft is inserted;
    A second central plate (73b) disposed adjacent to the second cylinder and containing the rotating part of the second rotary pump;
    A third cylinder (71c) disposed adjacent to the second central plate and having a third central hole (72c) into which the drive shaft is inserted;
    The first cylinder, the first center plate, the second cylinder, the second center plate, and the third cylinder are integrated into a unit,
    The second case is
    A fourth cylinder (71d) disposed adjacent to the first central plate and having a fourth central hole (72d) into which the drive shaft is inserted;
    2. The vehicle brake device according to claim 1, wherein the spring means is provided between the third cylinder and the fourth cylinder.
  3. The vehicle brake device according to claim 1, wherein the spring means is a disc spring.
  4. Among the disc springs, the bottom surface side, whose outer peripheral side functions as a load receiving portion, faces the first case side, and the upper surface side, which functions as the load receiving portion, faces the second case side. The vehicle brake device according to claim 3.
  5. 5. The vehicle brake according to claim 3, wherein the fourth cylinder is partially reduced in diameter on the third cylinder side, and the disc spring is provided in the reduced diameter portion. apparatus.
  6. The third center hole of the third cylinder has an inner diameter that is the same as or slightly larger than the reduced diameter portion of the fourth cylinder on the fourth cylinder side, and the third center hole is in the third center hole. The vehicle brake device according to claim 5, wherein the reduced diameter portion of the four cylinders is configured to be inserted.
  7. Sealing means (90) is provided between the fourth central hole and the drive shaft at the reduced diameter portion of the fourth cylinder, and the disc spring is configured to The vehicle brake device according to claim 5, wherein the vehicle brake device is disposed on an outer peripheral side of a portion where the sealing means is disposed.
  8. A screw member (200) is screwed and fixed as the fixing means to the entrance of the recess formed in the housing, and the second case is pressed in the insertion direction of the recess by the screw member. The brake device for vehicles as described in any one of Claim 1 thru | or 7.
JP2005318438A 2005-11-01 2005-11-01 Brake device for vehicle using rotary pump Active JP4508083B2 (en)

Priority Applications (1)

Application Number Priority Date Filing Date Title
JP2005318438A JP4508083B2 (en) 2005-11-01 2005-11-01 Brake device for vehicle using rotary pump

Applications Claiming Priority (4)

Application Number Priority Date Filing Date Title
JP2005318438A JP4508083B2 (en) 2005-11-01 2005-11-01 Brake device for vehicle using rotary pump
CN2006101425610A CN1959115B (en) 2005-11-01 2006-10-30 Vehicular brake device
US11/589,237 US7530647B2 (en) 2005-11-01 2006-10-30 Vehicular brake device
DE200610035378 DE102006035378B4 (en) 2005-11-01 2006-10-30 Vehicle brake device

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JP2007125929A true JP2007125929A (en) 2007-05-24
JP4508083B2 JP4508083B2 (en) 2010-07-21

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JP2011106382A (en) * 2009-11-19 2011-06-02 Advics Co Ltd Rotary shaft connection structure and rotary pump device
JP5304726B2 (en) * 2010-05-20 2013-10-02 株式会社アドヴィックス Rotating device with seal structure
JP5598222B2 (en) * 2010-09-30 2014-10-01 株式会社アドヴィックス Shaft seal device and pump device and brake fluid pressure control device using the same
WO2012103921A1 (en) * 2011-01-31 2012-08-09 Robert Bosch Gmbh Method for circuit separation testing in a double gearwheel pump
DE102015211430A1 (en) * 2015-06-22 2016-12-22 Robert Bosch Gmbh Electronically slip-controllable power brake system, in particular for a motor vehicle

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JP4069698B2 (en) * 2002-07-24 2008-04-02 株式会社アドヴィックス Oil seal structure
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JPH06211124A (en) * 1993-01-19 1994-08-02 Toyota Motor Corp Brake stroke simulator
JPH11343982A (en) * 1998-05-30 1999-12-14 Suzuki Motor Corp Trochoid oil pump
JP2001080498A (en) * 1999-07-09 2001-03-27 Denso Corp Vehicular brake system

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DE102010044070A1 (en) 2009-11-19 2011-05-26 Advics Co., Ltd, Kariya-city Rotary pump device and vehicle brake control system
JP2011105207A (en) * 2009-11-19 2011-06-02 Advics Co Ltd Rotary pump device and brake device for vehicle with the same
US8851578B2 (en) 2009-11-19 2014-10-07 Advics Co., Ltd. Rotary pump device and vehicle brake control system
DE102010044070B4 (en) * 2009-11-19 2015-05-21 Advics Co., Ltd. Rotary pump device and vehicle brake control system

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CN1959115B (en) 2010-09-22
JP4508083B2 (en) 2010-07-21
CN1959115A (en) 2007-05-09

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