JP2010096008A - Piston pump and hydraulic pressure unit - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To provide a piston pump and a hydraulic pressure unit reducing the size of a housing. <P>SOLUTION: A discharge valve has: a socket member provided in a discharge passage; a valve element seating to a valve seat provided on the socket member; and a bias member biasing the valve element to the valve seat member, and the bias member is constructed of a leaf spring. <P>COPYRIGHT: (C)2010,JPO&INPIT

Description

  The present invention relates to a piston pump that supplies pressurized fluid, and a hydraulic unit that controls hydraulic pressure.

As this type of technology, the technology described in Patent Document 1 is disclosed. In this publication, a discharge-side pump passage and a suction-side pump passage are formed substantially perpendicular to the axial direction of a receiving hole in which a pump plunger is accommodated, and a suction valve and a discharge valve are provided in each passage. Has been.
JP-A-10-227286

  The axial length of the pump can be shortened by forming the discharge-side pump passage and the suction-side pump passage substantially perpendicular to the axial direction of the housing hole in which the plunger of the pump is housed. However, since the suction valve and the discharge valve are configured so that the valve body is biased to the valve seat by the socket and the spring, the axial lengths of the suction valve and the discharge valve become long, and the plunger of the pump is accommodated. There is a problem that the housing is enlarged in a direction substantially orthogonal to the axial direction of the receiving hole.

  The present invention has been made paying attention to the above problems, and an object of the present invention is to provide a piston pump and a hydraulic unit capable of reducing the size of the housing.

  In order to achieve the above object, in the first invention, the discharge valve includes a socket member provided in the discharge passage, a valve body seated in a valve seat provided in the socket member, A biasing member that biases the valve seat member, and the biasing member is configured by a leaf spring. In the second invention, the intake valve and the discharge valve are arranged at positions sandwiching the piston accommodation hole, a socket member mounted on the housing, and a valve body seated on the valve seat member provided on the socket member; The valve body is constituted by a thin plate spring member that urges the valve seat portion.

  Therefore, the housing can be reduced in size.

  Hereinafter, the best mode for realizing the piston pump and the hydraulic unit of the first invention and the second invention will be described in the first embodiment.

[Example 1]
(Brake piping configuration)
FIG. 1 is a piping diagram of a brake system to which a hydraulic unit 1 is applied.

  The brake system according to the first embodiment performs hydraulic pressure control according to a required hydraulic pressure of an anti-lock brake system (hereinafter, ABS) from a controller. The brake system has a piping structure composed of two systems: a brake hydraulic circuit 3f for the front wheel system and a brake hydraulic circuit 3r for the rear wheel system. The front wheel master cylinder M / C (f) and the wheel cylinder W / C (f) are connected to the brake hydraulic circuit 3f of the front wheel system, and the rear wheel is connected to the brake hydraulic circuit 3r of the rear wheel system. Master cylinder M / C (r) and wheel cylinder W / C (r) are connected. The front wheel system brake fluid pressure circuit 3f is provided with a piston pump Pf, and the rear wheel system brake fluid pressure circuit 3r is provided with a piston pump Pr.

  In the following symbols, “f” indicates a component of the brake fluid pressure circuit 3f for the front wheel system, and “r” indicates a component of the brake fluid pressure circuit 3r for the rear wheel system. Since the configuration of the brake hydraulic circuit 3r in the rear wheel system is substantially the same, the symbols “f” and “r” are omitted unless particularly distinguished.

  The front wheel master cylinder M / C (f) is connected to the oil passage 5f via the master cylinder port 4f, and the rear wheel master cylinder M / C (r) is connected to the oil passage 5r via the master cylinder port 4r. . The oil passage 5 is connected to the discharge side of the piston pump P.

  The front wheel cylinder W / C (f) is connected to the oil passage 6f via the wheel cylinder port 19f, and the rear wheel wheel cylinder W / C (r) is connected to the oil passage 6r via the wheel cylinder port 19r. . The oil passage 6 is connected between the master cylinder port 4 of the oil passage 5 and the piston pump P.

  The oil passage 6 is provided with normally-open inflow valves 7f and 7r. The oil passage 6 is provided with oil passages 8f and 8r that bypass the inflow valve 7, and the oil passages 8f and r are provided with check valves 9f and 9r. This check valve 9 allows the flow of brake fluid in the direction from the wheel cylinder W / C toward the oil passage 5 and prohibits the flow in the opposite direction.

  Oil passages 10 f and 10 r branch from between the wheel cylinder W / C of the oil passage 6 and the inflow valve 7. The oil passages 10f and 10r are connected to reservoirs 12f and 12r, respectively, and normally closed outflow valves 11f and 11r are provided on the way.

  Oil passages 13 f and 13 r are branched from the outlet valve 11 and the reservoir 12 of the oil passage 10. The oil passage 13 is connected to the inflow side of the piston pump P.

  The piston pump P is connected to the oil passage 13 via suction valves 14f and 14r. The suction valve 14 allows the flow of brake fluid in the direction from the oil passage 13 toward the piston pump P, and prohibits the flow in the opposite direction. Piston pump P is connected to oil passage 5 via discharge valves 15f and 15r. The discharge valve 15 allows the flow of brake fluid in the direction from the piston pump P toward the oil passage 5 and prohibits the flow in the opposite direction.

  The piston pump P includes pistons 17f and 17r that reciprocate in the cylinders 16f and 16r by an eccentric cam 18 attached to a rotating shaft of the motor M, and a coil spring 20f that urges the pistons 17f and 17r toward the eccentric cam 18. 20r. The cylinders 16f and 16r are formed by piston housing holes 40f and 40r described later.

  The piston pump P draws hydraulic oil from the suction valve 14 and discharges hydraulic oil from the discharge valve 15 when the piston 17 reciprocates in the cylinder 16 by the eccentric cam 18 rotated by the motor M.

(Housing configuration)
FIG. 2 is a perspective view of the housing 2 of the hydraulic unit 1. In the following description, in FIG. 2, the surface where the master cylinder ports 4f and 4r are opened is the front surface 2a, the back surface of the front surface 2a is the rear surface 2b, the surface where the wheel cylinder ports 19f and 19r are opened is the upper surface 2c, and the upper surface 2c. The back surface is referred to as a lower surface 2d and the remaining two surfaces are referred to as a side surface 2e.

3 is a skeleton view seen from the front surface 2a of the housing 2, and FIG. 4 is a skeleton view seen from the side surface 2e of the housing 2. As shown in FIG.
The housing 2 is a rectangular parallelepiped, and the motor M is attached to the front surface 2a side, and the inflow valve 7, the outflow valve 11, and an electric unit for driving the motor M are attached to the rear surface 2b side.

Each hole and oil passage are formed in the housing 2, and each of these holes and oil passages are drilled perpendicularly to each surface from the outside of the housing 2 by a drill or the like.
The front surface 2a of the housing 2 has master cylinder ports 4f and 4r connected to the master cylinder M / C, a power supply shaft hole 30 into which the power supply shaft of the motor M is inserted, and an eccentric cam accommodation hole 31 for accommodating the eccentric cam 18. Is formed.

  Inserted into the rear surface 2b of the housing 2 are inflow valve mounting holes 32f and 32r for mounting the inflow valve 7, outflow valve mounting holes 33f and 33r for mounting the outflow valve 11, and screws for fixing the electric unit to the housing 2. The screw hole 34 to be formed is formed.

  On the upper surface 2c of the housing 2, wheel cylinder ports 19f and 19r connected to the wheel cylinder W / C, discharge valve mounting holes 37f and 37r to which the discharge valve 15 is mounted, oil passages 5f and 5r, oil passages 6f, 6r and oil passages 10f and 10r are formed.

Reservoir housing holes 39f and 39r for housing the reservoir 12, suction valve mounting holes 36f and 36r for mounting the suction valve 14, and oil passages 13f and 13r are formed on the lower surface 2d of the housing 2. The suction valve mounting hole 36 and the above-described discharge valve mounting hole 37 are arranged across the axis of the piston pump P, and communicate with each other on the same axis to form through holes 41f and 41r.
On the side surface 2e of the housing 2, pistons 17f and 17r of the piston pump P are accommodated, and piston accommodating holes 40f and 40r formed as cylinders 16f and 16r are provided. The piston accommodation hole 40 communicates with the through hole 41.

(Configuration of intake and discharge valves)
FIG. 5 is an enlarged view of the intake valve 14 and the discharge valve 15. Although the suction valve 14 and the discharge valve 15 are different in size, the shapes of the constituent members are the same. 5A is a view seen from the upper surface 2c when the suction valve 14 and the discharge valve 15 are mounted in the suction valve mounting hole 36 and the discharge valve mounting hole 37, and FIG. 6 is a partial cross-sectional view seen from the front surface 2a when the valve is mounted in the suction valve mounting hole 36 and the discharge valve mounting hole 37. 6 is a cross-sectional view taken along the line AA in FIG.

The suction valve 14 and the discharge valve 15 are constituted by a socket member 50, a leaf spring 51, and a valve body 52.
The socket member 50 is formed in a bottomed cup shape, and the bottom portion is inclined in a convex shape toward the center to form a valve seat portion 50 a of the valve body 52. An opening 50b having a smaller diameter than the valve body 52 formed in a spherical shape is formed in the center of the valve seat portion 50a. The socket member 50 has an opening on the opposite side to the valve seat portion 50 a, and the opening is bent toward the inner peripheral side to form an engaging portion 50 c that engages with the leaf spring 51. The inner peripheral diameter of the engaging portion 50 c is formed larger than the valve body 52.

The leaf spring 51 is formed in a cross shape, and the length between the opposing ends is formed larger than the inner peripheral diameter of the socket member 50.
The suction valve 14 and the discharge valve 15 are formed by inserting a valve body 52 inside the socket member 50 and then bending the leaf spring 51 so that the center is convex toward the valve body. The part is engaged with the engaging part 50c and formed as one assembly.
The suction valve 14 is inserted into the oil passage 13 from the reservoir accommodation hole 39 and is press-fitted into the suction valve mounting hole 36. The discharge valve 15 is inserted into the oil passage 5 and press-fitted into the discharge valve mounting hole 37.

(Operation of Example 1)
Next, the operation of the first embodiment configured as described above will be described.

Here, a case where a coil spring is used as a biasing member that biases the valve body of the discharge valve 15 to the valve seat portion will be considered.
Even when a load is applied in the compressing direction, the cylindrical coil spring becomes longer by the overlapping amount of the wire even in the most contracted state because the wire and the wire overlap each other. A conical coil spring can be used to avoid the overlap between the wire and the wire, but when a load is applied to the coil spring, a shearing force acts on the cross section of the wire. It is necessary to increase the diameter. For this reason, a load in the compression direction acts on the coil spring, and the coil spring becomes longer by the diameter of the wire even in the most contracted state.
Therefore, when a coil spring is used as a biasing member that biases the valve body of the discharge valve 15 to the valve seat portion, it is necessary to ensure the length of the oil passage 5 in which the discharge valve mounting hole 37 is formed. However, there was a problem that would increase the size.

  Therefore, in the first embodiment, the discharge valve 15 is made up of the socket member 50 provided in the oil passage 5, the valve body 52 seated on the valve seat portion 50a provided in the socket member 50, and the valve body 52 as the valve seat portion 50a. And a leaf spring 51 urging the spring.

  By adopting this configuration, the axial length of the discharge valve 15 can be shortened, and the oil passage 5 provided with the discharge valve 15 can be formed short, so that the housing 2 can be downsized. be able to.

  Similarly to the discharge valve 15, when a coil spring is used as the urging member in the intake valve 14, it is necessary to secure the length of the oil passage 13 in which the intake valve mounting hole 36 is formed, and the housing 2 is increased in size. There was a problem.

  Therefore, in the first embodiment, the intake valve 14 is made up of a socket member 50 provided in the oil passage 13, a valve body 52 seated on a valve seat portion 50 a provided in the socket member 50, and the valve body 52 as the valve seat portion. It is formed by a leaf spring 51 that biases 50a.

  By acting this configuration, the axial length of the suction valve 14 can be shortened, and the oil passage 13 provided with the suction valve 14 can be formed short, so that the housing 2 can be downsized. be able to.

  Further, since the suction valve 14 is press-fitted into a suction valve mounting hole 36 provided in the oil passage 13 and the discharge valve 15 is press-fitted into a discharge valve mounting hole 37 provided in the oil passage 5, the suction valve 14 and the discharge valve 15 are sucked. It was difficult to assemble within the valve mounting hole 36 and the discharge valve mounting hole 37.

Therefore, in the first embodiment, the outer end of the leaf spring 51 is engaged with the socket member 50 and the central portion is brought into contact with the valve body 52, so that the valve body 52 is connected to the valve seat portion 50 a and the central portion of the leaf spring 51. Between them.
By adopting this configuration, the suction valve 14 or the discharge valve 15 can be formed as an assembly, and mounting to the suction valve mounting hole 36 or the discharge valve mounting hole 37 is facilitated.

In the first embodiment, the oil passage 5 and the oil passage 13 are formed so as to intersect with the piston accommodation hole 40, specifically, to be substantially orthogonal.
By acting this configuration, the housing 2 can be downsized in the axial direction of the piston pump P.

  Further, in the first embodiment, the intake valve 14 and the discharge valve 15 are arranged at positions sandwiching the piston accommodation hole 40, the socket member 50 mounted on the housing 2, and the valve seat portion 50 a provided on the socket member 50. And a thin plate spring 51 that biases the valve body 52 toward the valve seat portion 50a.

  By adopting this configuration, since the leaf spring 51 is used as a member for urging the valve body 52 to the valve seat portion 50a, the axial length of the discharge valve 15 can be shortened, and the discharge valve 15 is provided. Since the oil passage 5 can be formed short, the housing 2 can be downsized.

(Effect of Example 1)
Next, effects of Example 1 are listed below.

  (1) Piston 17 that reciprocates in the piston housing hole 40 formed in the housing 2 in the axial direction, an eccentric cam 18 and a motor M that drive the piston 17, and oil that is formed in communication with the piston housing hole 40. Oil that is provided in the passage 13 (suction passage), opens as the piston 17 reciprocates, and sucks the working fluid into the piston accommodation hole 40, and is formed in communication with the piston accommodation hole 40. In the piston pump P, which is provided in the passage 5 (discharge passage) and opens with the reciprocation of the piston 17, and discharges the hydraulic fluid in the piston accommodation hole 40 to the oil passage 5, The valve 15 includes a socket member 50 provided in the oil passage 5, a valve body 52 that is seated on a valve seat portion 50a provided in the socket member 50, and a leaf spring 51 that biases the valve body 52 toward the valve seat portion 50a. And formed by

  Since the leaf spring 51 is used as a member for urging the valve body 52 to the valve seat portion 50a, the axial length of the discharge valve 15 can be shortened, and the oil passage 5 provided with the discharge valve 15 is formed short. Therefore, the housing 2 can be downsized.

  (2) In addition to the configuration of (1) above, the intake valve 14 includes a socket member 50 provided in the oil passage 13, a valve body 52 seated on a valve seat portion 50 a provided in the socket member 50, and a valve The body 52 is formed by a leaf spring 51 that urges the valve seat portion 50a.

  Since the leaf spring 51 is used as a member for biasing the valve body 52 to the valve seat portion 50a, the axial length of the suction valve 14 can be shortened, and the oil passage 13 provided with the suction valve 14 is formed short. Therefore, the housing 2 can be downsized.

(3) In addition to the configuration of the above (1) or (2), the outer end of the leaf spring 51 is engaged with the socket member 50 and the center is brought into contact with the valve body 52, so that the valve body 52 is seated on the valve seat. It was decided to be sandwiched between the portion 50 a and the central portion of the leaf spring 51.
The suction valve 14 or the discharge valve 15 can be formed as an assembly, and the mounting to the suction valve mounting hole 36 or the discharge valve mounting hole 37 is facilitated.

(4) In addition to the configuration of (1), (2) or (3) above, the oil passage 5 and the oil passage 13 are formed so as to be substantially orthogonal to the piston accommodation hole 40.
Therefore, the housing 2 can be downsized in the axial direction of the piston pump P.

  (5) Housing 2 having a passage formed therein, reservoir 12 for storing hydraulic fluid flowing in from wheel cylinder W / C, and hydraulic oil stored in reservoir 12 is circulated to the master cylinder M / C side for suction A piston pump P having a valve 14 and a discharge valve 15, a piston accommodation hole 40 that is drilled in the housing 2 and accommodates the piston 17 of the piston pump P, and is connected to the piston accommodation hole 40 to connect the piston pump P The through hole 41 provided with the suction valve 14 and the discharge valve 15, the suction valve 14 and the discharge valve 15 are arranged at positions sandwiching the piston accommodation hole 40, and the socket member 50 mounted on the housing 2 and the socket The valve body 52 is configured to be seated on a valve seat portion 50a provided on the member 50, and the thin plate spring 51 biases the valve body 52 toward the valve seat portion 50a.

  Since the leaf spring 51 is used as a member for urging the valve body 52 to the valve seat portion 50a, the axial length of the discharge valve 15 can be shortened, and the oil passage 5 provided with the discharge valve 15 is formed short. Therefore, the housing 2 can be downsized.

[Example 2]
Next, Example 2 will be described. The same components as those in the first embodiment are denoted by the same reference numerals and description thereof is omitted. In the first embodiment, the suction valve 14 is press-fitted into the suction valve mounting hole 36 provided in the oil passage 13, but in the second embodiment, the suction valve 14 is provided in the piston 17 of the piston pump P.

(Structure of intake valve)
7 is a cross-sectional view taken along the line AA in FIG. FIG. 8 is an enlarged view of the suction valve 14.
The intake valve 14 includes a socket member 56, a valve body 53, a coil spring 57, and a valve seat portion 55 a formed on the piston 17.

  The piston 17 is formed therein with oil passages 55f and 55r communicating with the oil passage 13 and the piston accommodation hole 40. One ends of the oil passages 55f and 55r open in the axial direction of the piston housing hole 40, and a valve seat portion 55a of the valve body 53 of the intake valve 14 is formed by the opening.

  The socket member 56 is formed in a cup shape with a bottom, and the opening side is bent outward to form a flange portion 56a. Moreover, the opening part 56b is formed in the bottom part of the socket member 56, and the inside and the exterior of the socket member 56 are connected.

The suction valve 14 has the valve body 53 mounted on the valve seat portion 55a, and the opening side of the socket member 56 is engaged with the piston 17 while the coil spring 57 biases the valve body 53 toward the valve seat portion 55a. Thereafter, the flange portion 56 a of the socket member 56 and the piston 17 are attached by being biased toward the eccentric cam 18 by the coil spring 20.
By adopting the above configuration, it is not necessary to provide a suction valve mounting portion in the oil passage 13, the oil passage 13 can be formed short, and the housing 2 can be reduced in size.

[Other embodiments]
As described above, the best mode for carrying out the first and second inventions has been described based on the first and second embodiments. However, the specific configuration of each invention is limited to the first embodiment. However, the present invention includes any design changes that do not depart from the spirit of the invention.

  FIG. 9 is an enlarged view of the intake valve 14 and the discharge valve 15 for explaining another embodiment. 9A is a view seen from the upper surface 2c when the suction valve 14 and the discharge valve 15 are mounted in the suction valve mounting hole 36 and the discharge valve mounting hole 37, and FIG. 6 is a partial cross-sectional view seen from the front surface 2a when the valve is mounted in the suction valve mounting hole 36 and the discharge valve mounting hole 37. FIG.

  FIG. 10 is an enlarged view of the intake valve 14 and the discharge valve 15 for explaining another embodiment. 10A is a view seen from the upper surface 2c when the intake valve 14 and the discharge valve 15 are mounted in the intake valve mounting hole 36 and the discharge valve mounting hole 37, and FIG. 10B is the intake valve 14 and the discharge valve 15 6 is a partial cross-sectional view seen from the front surface 2a when the valve is mounted in the suction valve mounting hole 36 and the discharge valve mounting hole 37. FIG.

  In the suction valve 14 and the discharge valve 15 of the first embodiment, the leaf spring 51 formed in a cross shape is used in the discharge valve 15 of the second embodiment, but an enlarged view of the suction valve 14 and the discharge valve 15 shown in FIG. A leaf spring 51 formed in the shape of a rice mark as shown in FIG. 10 may be used, or a leaf spring 51 formed in a spiral shape as shown in the enlarged view of the suction valve 14 and the discharge valve 15 shown in FIG. There is no particular limitation.

It is a piping diagram of the brake system of Example 1. 3 is a perspective view of a housing according to Embodiment 1. FIG. FIG. 3 is a skeleton diagram viewed from the front surface of the housing according to the first embodiment. It is the skeleton figure seen from the side of the housing of Example 1. It is an enlarged view of the intake valve and discharge valve of Example 1. 2 is a cross-sectional view of a housing according to Embodiment 1. FIG. 6 is a cross-sectional view of a housing according to Embodiment 2. FIG. 6 is an enlarged view of a suction valve according to Embodiment 2. FIG. It is an enlarged view of the suction valve and discharge valve of another Example. It is an enlarged view of the suction valve and discharge valve of another Example.

Explanation of symbols

1 Hydraulic unit 2 Housing 14 Suction valve 15 Discharge valve 16 Cylinder 17 Piston 18 Eccentric cam 36 Suction valve mounting hole 37 Discharge valve mounting hole 40 Piston accommodation hole (piston hole)
41 Through-hole 50 Socket member 50a Valve seat part 50b Opening part 50c Engagement part 51 Leaf spring 52 Valve body
M / C master cylinder
W / C wheel cylinder

Claims (5)

A piston that reciprocates in the axial direction in a piston hole formed in the housing;
A piston drive member for driving the piston;
A suction valve that is provided in a suction passage formed in communication with the piston hole, opens as the piston reciprocates, and sucks hydraulic fluid into the piston hole;
A discharge valve that is provided in a discharge passage formed in communication with the piston hole, opens as the piston reciprocates, and discharges hydraulic fluid in the piston hole to the discharge passage;
In a piston pump having
The discharge valve includes a socket member provided in the discharge passage, a valve body seated on a valve seat portion provided in the socket member, and a biasing member that biases the valve body to the valve seat portion. And the urging member is configured by a leaf spring. The piston pump according to claim 1, wherein
The suction valve includes a socket member provided in the suction passage, a valve body seated on a valve seat portion provided in the socket member, and an urging member that biases the valve body to the valve seat portion. And the urging member is configured by a leaf spring. The piston pump according to claim 1 or 2,
The leaf spring has an outer end engaged with the socket member and a central portion abutted against the valve body, and the valve body is sandwiched between the valve seat portion and the central portion of the leaf spring. A piston pump characterized by that. The piston pump according to any one of claims 1 to 3,
The piston pump, wherein the suction passage and the discharge passage are formed so as to intersect the piston hole. A housing having a passage formed therein;
A reservoir for storing hydraulic fluid flowing from the wheel cylinder;
Recirculating the hydraulic oil stored in the reservoir to the master cylinder side, and a piston pump provided with a suction valve and a discharge valve;
A piston receiving hole that is drilled in the housing and receives a piston of the piston pump;
A through hole provided with the suction valve and the discharge valve of the piston pump connected to the piston accommodation hole;
The suction valve and the discharge valve are disposed at positions sandwiching the piston accommodation hole, a socket member mounted on the housing, a valve body seated on a valve seat portion provided on the socket member, A hydraulic unit comprising a thin plate spring member that biases the valve body toward the valve seat portion.

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