JP5755113B2 - Pump device - Google Patents

Description

  The present invention relates to a pump device.

  As this type of technology, the technology described in Patent Document 1 below is disclosed. This publication discloses a pump provided with a check valve, a buffer chamber, and a throttle on the discharge side of the pump.

JP 2008-56205 A

In the technique described in Patent Document 1, since the throttle (orifice passage) is formed by a member different from the check valve, there is a problem that the number of parts increases.
The present invention has been made paying attention to the above problems, and an object of the present invention is to provide a pump device capable of reducing the number of parts when an orifice is provided on the discharge side of the pump.

In the present invention for achieving the above object, a discharge valve structure provided between the electromagnetic valve a liquid path and the rotary pump, a valve body, the seat surface and the fluid valve body is seated flows A seat member provided with a seat hole, an elastic body that urges the valve body against the seat member, and a socket member provided with an accommodation hole for accommodating the valve body and the elastic body therein, The socket member is provided with an orifice passage communicating from the accommodation hole to the outside.

  According to the present invention, since the orifice passage can be integrated with the discharge valve structure, the number of parts can be reduced.

FIG. 2 is a hydraulic circuit diagram of the brake hydraulic pressure control device according to the first embodiment. 3 is a perspective view of a housing according to Embodiment 1. FIG. 3 is a perspective view of a housing according to Embodiment 1. FIG. FIG. 3 is a front view of the housing according to the first embodiment. It is a perspective view of the pump unit and discharge valve structure of Example 1. It is sectional drawing of the state which accommodated the pump unit and discharge valve structure of Example 1 in the housing. FIG. 3 is an enlarged cross-sectional view in the vicinity of an orifice passage according to the first embodiment. It is sectional drawing of the state which accommodated the pump unit and discharge valve structure of Example 2 in the housing. It is a front view of the housing of another Example. It is a front view of the housing of another Example.

[Example 1]
[Configuration of brake hydraulic circuit]
FIG. 1 is a hydraulic circuit diagram of the brake hydraulic pressure control device 1. The hydraulic circuit is formed in a hydraulic control unit 2 provided between the master cylinder M / C and the wheel cylinder W / C.
The brake fluid pressure control device 1 performs fluid pressure control according to the required fluid pressure of the vehicle dynamics control (hereinafter referred to as VDC) and the anti-lock brake system (hereinafter referred to as ABS) from the controller. The brake fluid pressure control device 1 has a piping structure called X piping, which includes two systems, a P system brake fluid pressure circuit 3P and an S system brake fluid pressure circuit 3S. The left front wheel cylinder W / C (FL) and the right rear wheel wheel cylinder W / C (RR) are connected to the P system, and the right front wheel wheel cylinder W / C (FR) is connected to the S system. ), Wheel cylinder W / C (RL) for the left rear wheel is connected. Each wheel cylinder W / C is connected to a wheel cylinder port 4FL, 4FR, 4RL, 4RR. The pump unit 25 is a tandem gear pump in which a rotary gear pump PP and a gear pump PS are provided in each of the P system and the S system.
The master cylinder M / C is connected to the liquid passages 17P and 17S via the master cylinder ports 5P and 5S. The liquid path 17 and the suction side of the pump unit 25 are connected by liquid paths 23P and 23S. A master cylinder pressure sensor 15 is provided on the liquid path 17P and between the master cylinder port 5P and the connection portion of the liquid path 23P.

The discharge side of the pump unit 25 and each wheel cylinder W / C are connected by liquid passages 20P and 20S. On each liquid path 20, pressure increase valves 7FL, 7FR, 7RL, 7RR which are normally open solenoid valves corresponding to the respective wheel cylinders W / C are provided. Also, check valves 11P and 11S and orifice passages 64P and 64S are provided on each liquid passage 20 and between each pressure increasing valve 7 and the pump unit 25. Each check valve 11 allows the flow of brake fluid pressure in the direction from the pump unit 25 toward the pressure increasing valve 7 and prohibits the flow in the opposite direction. Discharge pressure sensors 16P and 16S are provided on each liquid path 20 and between each pressure increasing valve 7 and the pump unit 25.
Furthermore, each fluid passage 20 is provided with fluid passages 22FL, 22FR, 22RL, 22RR that bypass each pressure increasing valve 7, and the fluid passage 22 is provided with check valves 10FL, 10FR, 10RL, 10RR. Yes. Each check valve 10 allows the flow of brake fluid pressure in the direction from the wheel cylinder W / C toward the pump unit 25, and prohibits the flow in the opposite direction.

The master cylinder M / C and the liquid path 20 are connected by liquid paths 19P and 19S, and the liquid path 20 and the liquid path 19 merge between the pump unit 25 and the pressure increasing valve 7. On each liquid path 19, gate-out valves 6P and 6S, which are normally open solenoid valves, are provided. In addition, each liquid path 19 is provided with liquid paths 18P and 18S that bypass each gate-out valve 6, and in this liquid path 18, check valves 9P and 9S are provided. Each check valve 9 allows the flow of brake fluid pressure in the direction from the master cylinder M / C side toward the wheel cylinder W / C, and prohibits the flow in the opposite direction.
Reservoirs 13P and 13S are provided on the suction side of the pump unit 25, and the reservoir 13 and the pump unit 25 are connected by liquid passages 21P and 21S. Check valves 14P and 14S are provided at the entrance and exit of the reservoir 13.
The wheel cylinder W / C and the reservoir 13 are connected by liquid paths 24P and 24S, and pressure reducing valves 8FL, 8FR, 8RL, and 8RR, which are normally closed solenoid valves, are provided in the liquid paths 24, respectively. .

[Housing configuration]
The fluid path of the fluid pressure control unit 2 is formed in the housing 26, and valves, pump units, and the like are accommodated in the housing 26. 2 and 3 are perspective views of the housing 26. FIG. FIG. 2 is a view showing a state where the motor M is attached to the housing 26, and FIG. 3 is a view where the motor M is removed from the housing 26. FIG. 4 is a front view of the housing 26. FIG. 4 is a view in which the motor M is removed from the housing 26.
In the following description, the surface where the master cylinder port 5 is opened in FIGS. 2, 3 and 4 is the front surface 26a, the rear surface of the front surface 26a is the rear surface 26b, and the surface where the wheel cylinder port 4 is opened is the upper surface 26c. The rear surface of the upper surface 26c is referred to as a lower surface 26d, the left side surface with respect to the front surface 26a is referred to as a left side surface 26e, and the right side surface with respect to the front surface 26a is referred to as a right side surface 26f.
The housing 26 is a substantially rectangular parallelepiped, and a motor M is attached to the front surface 26a side. The solenoid valve groups of the gate-out valve 6, the pressure increasing valve 7, and the pressure reducing valve 8 on the rear surface 26b side, and the electric for driving these solenoid valve groups. The unit is installed. The electric unit includes a board that performs a predetermined calculation in accordance with an input signal from a wheel speed sensor or the like attached to the vehicle. A predetermined electric signal is supplied to a solenoid attached to a solenoid valve or a motor M. Output. This electric unit is accommodated in the unit case 27. The housing 26 is formed with a power supply hole 28 penetrating the front surface 26a and the rear surface 26b, and the electric unit and the motor M are connected by inserting the electrode of the motor M into the power supply hole 28.

The housing 26 has a valve mounting hole in which each solenoid valve group is mounted by press-fitting or caulking, a plurality of fluid paths connecting each port and each solenoid valve group, a wheel cylinder W / C, and a master cylinder. A wheel cylinder port 4 connected to the M / C, a hole for disposing the master cylinder port 5 and the reservoir 13 are formed. These holes, liquid passage holes and the like are drilled from the outside of the housing 26 to each surface by a drill or the like.
A master cylinder port 5 is formed on the upper surface 26c side of the front surface 26a.
The pump unit 25 is accommodated in a substantially cylindrical accommodation hole 30 that penetrates from the front surface 26a to the rear surface 26b of the housing 26. A pump cover 29 (see FIG. 5) is screwed to the housing 26 on the rear surface 26b side of the accommodated pump unit 25, and the front surface 26a side is formed by a caulking portion 31 in which the entire circumference of the opening portion of the accommodation hole 30 is deformed. It is fixed.
Also, a discharge valve mounting hole 32 is formed from the left side surface 26e to the right side surface 26f of the housing 26 so as to be substantially orthogonal to the accommodation hole 30, and the discharge valve structure that connects to the discharge side of the pump unit 25 in the discharge valve mounting hole 32 33 are housed.

[Configuration of pump unit]
FIG. 5 is a perspective view of the pump unit 25 and the discharge valve constituting body 33. FIG. 6 is a cross-sectional view showing a state in which the pump unit 25 and the discharge valve constituting body 33 are accommodated in the housing 26.
The pump unit 25 includes a pump housing 34, a center plate 35, and a pump cover 36. The pump housing 34, the center plate 35, and the pump cover 36 are all formed in a substantially cylindrical shape. The pump housing 34, the center plate 35, and the pump cover 36 are combined in the axial direction in this order.
The pump housing 34 is formed with a bottomed hollow portion, and the gear pump PP is accommodated in a space between the hollow portion and the center plate 35. The pump cover 36 is also formed with a bottomed hollow portion, and the gear pump PS is accommodated in a space between the hollow portion and the center plate 35. The gear pump P is an external gear pump in which a pair of gears mesh with each other, and pumps brake fluid by rotating the pair of gears.

An O-ring groove 37 a and an O-ring groove 37 b are formed on the outer periphery of the pump housing 34, and an O-ring groove 37 c is formed on the outer periphery of the pump cover 36. Each O-ring groove 37 is formed separately from the axial direction of the pump unit 25, and O-rings 38a, 38b, and 38c are attached thereto.
A low pressure chamber groove 39P is formed on the circumference between the O ring 38a and the O ring 38b of the pump housing 34. Further, when the pump unit 25 is accommodated in the accommodation hole 30 of the housing 26, the low pressure chamber groove 40P is formed at a position facing the low pressure chamber groove 39P on the inner periphery of the accommodation hole 30. A space isolated by the low pressure chamber groove 39P of the pump housing 34, the low pressure chamber groove 40P of the accommodation hole 30, the O-ring 38a, and the O-ring 38b is formed as a suction chamber 41P.
On the outer periphery of the center plate 35, a low pressure chamber groove 39S is formed on the circumference. Further, when the pump unit 25 is accommodated in the housing hole 30 of the housing 26, the low pressure chamber groove 40S is formed at a position on the inner periphery of the housing hole 30 and facing the low pressure chamber groove 39S. A space isolated by the low pressure chamber groove 39S of the center plate 35, the low pressure chamber groove 40S of the accommodation hole 30, the O-ring 38b, and the O-ring 38c is formed as the suction chamber 41S. In addition, discharge passages 56P and 56S are formed in the center plate 35. The discharge passage 56P opens to a discharge space 49P described later, and the discharge passage 56S opens to a discharge space 49S described later.

The gear pumps PP and PS have side plates 42P and 42S, seal blocks 43P and 43S, and a pair of driving and driven external gears 44P and 44S. Suction portions 45P and 45S are formed between the side plates 42P and 42S and the seal blocks 43P and 43S. An O-ring 46P is provided between the seal block 43P and the pump housing 34. An O-ring 46S is provided between the seal block 43S and the center plate 35.
The drive side of the external gears 44P and 44S is connected to the drive shaft 47. The drive shaft 47 passes through the side plates 42P and 42S, the seal blocks 43P and 43S, the center plate 35, and the pump housing 34, and is connected to the rotation shaft of the motor M.
A discharge chamber 49P is formed by a space formed by the pump housing 34, the center plate 35, the side plate 42P, and the seal block 43P. Further, a discharge chamber 49S is formed by a space formed by the pump cover 36, the center plate 35, the side plate 42S, and the seal block 43S.
The pump housing 34 is formed with a suction passage 48P that connects the suction portion 45P of the gear pump PP and the suction chamber 41P. The center plate 35 is formed with a suction passage 48S that connects the suction portion 45S of the gear pump PS and the suction chamber 41S.

[Discharge valve structure]
The discharge valve constituting bodies 33P and 33S incorporate check valves 11P and 11S and orifice passages 64P and 64S. The discharge valve constituting bodies 33P and 33S are accommodated in discharge valve mounting holes 32P and 32S formed so as to be substantially orthogonal to the accommodation hole 30 from the left side surface 26e to the right side surface 26f of the housing 26.
The discharge valve constituting body 33 is formed of communication members 50P and 50S, socket members 51P and 51S, valve bodies 52P and 52S, seat members 53P and 53S, and coil springs 54P and 54S.
The communication member 50 is formed with through passages 55P and 55S penetrating the inside in the axial direction. One end side of the communication member 50 is inserted into the center plate 35, and the through passage 55 communicates with the discharge passage 56. O-rings 57P and 57S are attached to the outer periphery on one end side of the communication member 50. The other end side of the communication member 50 is inserted into the discharge valve mounting hole 32 of the housing 26. O-rings 58P and 58S are attached to the outer periphery on the other end side of the communication member 50.

The socket member 51 is formed with receiving holes 59P and 59S that are open at one end, and the outer periphery of the receiving hole 59 forms cylindrical walls 63P and 63S. A coil spring 54 and a valve body 52 are sequentially accommodated in the accommodation hole 59, and a seat member 53 is press-fitted. The sheet member 53 is formed with sheet holes 60P and 60S penetrating the sheet member 53 in the axial direction, and the other end side opening of the sheet hole 60 constitutes sheet surfaces 65P and 65S. The coil spring 54 is contracted between the bottom 66 of the accommodation hole 59 and the valve body 52, and urges the valve body 52 in the direction of seating on the seat surface 65.
The socket member 51 is inserted into the discharge valve mounting hole 32 of the housing 26 and fixed by crimping portions 61P and 61S in which the hole edge of the opening on the outer peripheral side of the housing 26 of the discharge valve mounting hole 32 is crimped. In a state where the socket member 51 to which the sheet member 53 is attached and the communication member 50 are inserted into the discharge valve mounting hole 32, the sheet hole 60 of the sheet member 53 and the through hole 55 of the communication member 50 communicate with each other.
Orifice passages 64P and 64S are formed in the cylindrical wall 63 of the socket member 51. The orifice passage 64 is formed in the cylindrical wall 63 in the radial direction of the seat surface 65. FIG. 7 is an enlarged sectional view of the vicinity of the orifice passage 64. The orifice passage 64 is formed continuously with the large diameter portion 64a formed on the outer peripheral side of the cylindrical wall 63 and the large diameter portion 64a on the inner peripheral side of the cylindrical wall 63, and has a small diameter portion 64b having a smaller diameter than the large diameter portion 64a. Formed from. The small diameter portion 64b has a diameter of 0.5 [mm] and an axial length of 0.3 [mm].
One end side of the cylindrical wall 63 of the socket member 51 is formed to have a larger diameter than the portion where the orifice passage 64 is formed, and O-rings 62P and 62S are mounted on the outer periphery thereof.
Here, the communication member 50 and the socket member 51 are formed separately. By forming the communication member 50 and the socket member 51 separately, it is possible to absorb backlash due to an error in the axial length of the accommodation hole 59. However, even if the communication member 50 and the socket member 51 are integrated, if the play can be sufficiently absorbed, the communication member 50 and the socket member 51 may be formed integrally. That is, the communication member 50 may be regarded as a part of the socket member 51.

[Action]
(Brake fluid flow when driving the gear pump)
When the gear pump P is driven, brake fluid is supplied from the suction passage 48 to the suction portion 45. The brake fluid supplied to the suction part 45 is pumped by the pair of gears of the gear pump P and discharged into the discharge chamber 49. The discharge chamber 49 functions as a damper chamber that suppresses the pulsation of the discharge pressure. The brake fluid discharged into the discharge chamber 49 is sent to the valve body 52 through the discharge passage 56, the through hole 55 (communication member 50), and the seat hole 60 (sheet member 53). The brake fluid opens the valve body 52 against the coil spring 54 and passes through the orifice passage 64. The orifice passage 64 suppresses the pulsation of the discharge pressure.
(Integration of discharge valve structure and orifice passage)
Conventionally, the discharge valve structure and the orifice passage are formed separately. Therefore, there is a problem that the number of parts increases.
Therefore, in the first embodiment, the orifice passage 64 is provided in the socket member 51 of the discharge valve constituting body 33. Therefore, since the orifice passage 64 can be integrated with the discharge valve constituting body 33, the number of parts can be reduced.

(Miniaturization of housing)
In the first embodiment, the orifice passage 64 is formed in the cylindrical wall 63 of the socket member 51.
The discharge valve constituting body 33 is mounted in a discharge valve mounting hole 32 formed so as to be substantially orthogonal to the housing hole 30 that houses the pump unit 25. The thickness of the housing 26 in the left-right direction is determined by the diameter of the pump unit 25 and the axial length of the discharge valve component 33. That is, the thickness of the housing 26 has no margin in the left-right direction with respect to the discharge valve constituting body 33.
Although the orifice passage 64 can be formed in the bottom 66 of the socket member 51, it is necessary to form a liquid path on the outer side in the axial direction of the socket member 51, and it is necessary to increase the thickness of the housing 26 in the left-right direction. In the first embodiment, since the orifice passage 64 is formed in the cylindrical wall 63 of the socket member 51, a liquid path may be formed on the radially outer side of the socket member 51, and the thickness of the housing 26 does not need to be increased. Therefore, an increase in the size of the housing 26 can be avoided.
(Discharge passage shortening)
In the first embodiment, the orifice passage 64 is formed at a radial position of the seat surface 65. Therefore, the brake fluid that has passed through the seat surface 65 can immediately flow into the orifice passage 64.
(The quietness of the pump)
In Example 1, a circumscribed gear pump P was used. The gear pump P can be quieter than the plunger pump.
(Pulsation suppression)
In the first embodiment, the brake fluid discharged from the gear pump P flows through the discharge chamber 49 to the discharge valve constituting body 33. Therefore, since the discharge chamber 49 acts as a damper chamber, the pulsation of the hydraulic pressure can be suppressed.

〔effect〕
The effects of Example 1 are listed below.
(1) A housing 26 having a built-in rotary gear pump P, a discharge valve mounting hole 32 formed in the housing 26, and a discharge valve mounting hole 32 for mounting the fluid discharged from the gear pump P to the outside. The discharge valve constituting body 33 includes a valve member 52, a seat member including the seat surface 65 on which the valve body 52 is seated, and a seat hole 60 through which fluid flows, and the valve body. A coil spring 54 (elastic body) that biases the sheet member 53, and a socket member 51 provided with an accommodating hole 59 for accommodating the valve body 52 and the coil spring 54 therein. Is provided with an orifice passage 64 communicating from the accommodation hole 59 to the outside.
Therefore, since the orifice passage 64 can be integrated with the discharge valve constituting body 33, the number of parts can be reduced.
(2) The socket member 51 includes a cylindrical wall 63, and an orifice passage 64 is formed in the cylindrical wall 63.
Therefore, an increase in the size of the housing 26 can be avoided.
(3) The orifice passage 64 is formed at the radial position of the seat surface 65.
Therefore, the brake fluid that has passed through the seat surface 65 can immediately flow into the orifice passage 64.
(4) The gear pump P is an external gear pump.
Therefore, silence can be improved.
(5) The gear pump P includes the discharge chamber 49 into which the fluid pumped from the pair of gears flows, and the fluid flows from the discharge chamber 49 to the discharge valve constituting body 33.
Therefore, since the discharge chamber 49 acts as a damper chamber, the pulsation of the hydraulic pressure can be suppressed.

[Example 2]
In the first embodiment, the orifice passage 64 is formed in the cylindrical wall 63 of the socket member 51, but in the second embodiment, the orifice passage 64 is formed in the communication member 50.
In the following description, the same components as those in the first embodiment are denoted by the same reference numerals, the description thereof is omitted, and only portions different from those in the first embodiment are described.
FIG. 8 is a cross-sectional view showing a state in which the pump unit 25 and the discharge valve constituting body 33 are accommodated in the housing 26. As shown in FIG. 8, an orifice passage 64 is formed at one end of the communication member 50. Thereby, an orifice passage 64 can be formed between the discharge space 49 of the gear pump P and the valve body 52.
〔effect〕
The effect of Example 2 will be described below.
(6) In the communication passage 50 (socket member), an orifice passage 64 is provided between the gear pump P (rotary pump) and the valve body 52.
Therefore, since the orifice passage 64 can be integrated with the communication passage 50, the number of parts can be reduced.

[Other Examples]
The present invention has been described based on the first to third embodiments. However, the specific configuration of each invention is not limited to each embodiment, and the design can be changed within the scope not departing from the gist of the invention. Is included in the present invention.
9 and 10 are front views of the housing 26. FIG. In Example 1 and Example 2, in order to fix the pump unit 25 to the housing 26, the caulking part 31 in which the entire circumference of the opening part of the accommodation hole 30 is deformed is formed. For example, two crimping portions 31 may be formed as shown in FIG. 9, or three crimping portions 31 may be formed as shown in FIG.

[Technical thought other than claims]
Further, technical ideas other than the claims that can be grasped from the above embodiments will be described below together with the effects thereof.
(A) In the pump device according to claim 2,
The pump device according to claim 1, wherein the seat member is press-fitted into an inner periphery of a cylindrical wall of the socket member.
Therefore, the sheet member can be fixed to the socket member without using a fastening member.
(B) In the pump device according to claim 6,
The pump device according to claim 1, wherein the socket member is fixed by compositionally deforming a hole edge of the discharge valve mounting hole of the housing.
Therefore, the discharge valve component can be fixed to the housing without using a fastening member.
(C) In the pump device according to claim 7,
The cylindrical wall is provided with a seal groove mounting portion having a diameter larger than a diameter of a portion where the orifice passage is formed, and a seal ring for making the socket member liquid-tight to the discharge valve mounting hole is mounted. A pump device characterized by.
Therefore, a fluid passage through which the brake fluid flows can be formed between the orifice passage and the housing.
(D) In the pump device according to claim 2,
The orifice passage is composed of a large-diameter passage having a large diameter and a small-diameter passage that is continuous with the large-diameter passage and has a smaller diameter than the large-diameter passage.
Therefore, by making a part of the orifice passage a small-diameter passage, it is possible to suppress the pulsation of the hydraulic pressure while suppressing a decrease in the hydraulic pressure of the brake fluid passing through the orifice passage.

(E) In the pump device according to claim 9,
The diameter of the said small diameter channel | path is larger than the axial direction length, The pump apparatus characterized by the above-mentioned.
Therefore, by shortening the axial length of the small diameter passage, it is possible to suppress the pulsation of the hydraulic pressure while suppressing a decrease in the hydraulic pressure of the brake fluid passing through the orifice passage.
(F) In the pump device according to claim 10,
A pump device characterized in that the diameter of the small-diameter passage is 0.5 [mm] and the axial length is 0.3 [mm].
Therefore, by shortening the axial length of the small diameter passage, it is possible to suppress the pulsation of the hydraulic pressure while suppressing a decrease in the hydraulic pressure of the brake fluid passing through the orifice passage.
(G) a housing with a built-in rotary pump;
A discharge valve component mounting hole formed in the housing and mounted with a discharge valve component discharging the brake fluid pumped from the rotary pump;
With
The discharge valve component includes a valve body, a seat surface on which the valve body is seated and a seat member through which fluid flows, a coil spring that biases the valve body toward the seat member, A socket member having an accommodating hole for accommodating the valve body and the coil spring;
A path that communicates from the inside of the accommodation hole to the outside is provided in the socket member,
A pump device characterized in that an orifice is formed in the passage.
Therefore, since the orifice passage can be integrated with the discharge valve constituting body, the number of parts can be reduced.

(H) In the pump device according to claim 12,
The socket member comprises a cylindrical wall;
The pump device according to claim 1, wherein the passage is formed along a radial direction of the cylindrical wall.
Therefore, the brake fluid that has passed through the seat surface can immediately flow into the passage.
(Li) In the pump device according to claim 12,
The pump device characterized in that the passage is formed at a radial position of the seat surface.
Therefore, the brake fluid that has passed through the seat surface can immediately flow into the passage.
(Nu) In the pump device according to claim 12,
The accommodation hole is bottomed, and the coil spring is contracted between the bottom of the accommodation hole and the discharge valve,
The pump device according to claim 1, wherein the seat member is press-fitted into an inner periphery of a cylindrical wall of the socket member.
Therefore, the sheet member can be fixed to the socket member without using a fastening member.

(L) In the pump device according to claim 12,
The rotary pump is an external gear pump, and includes a discharge chamber into which fluid pumped from a pair of gears flows, and the fluid flows from the discharge chamber to the discharge valve structure.
Therefore, since the discharge chamber acts as a damper chamber, the pulsation of the hydraulic pressure can be suppressed.
(W) In the pump device according to claim 16,
A pump device characterized in that a damper chamber is constituted by the discharge chamber.
Therefore, since the discharge chamber acts as a damper chamber, the pulsation of the hydraulic pressure can be suppressed.
(W) In the pump device according to claim 12,
2. The pump apparatus according to claim 1, wherein the passage includes a large-diameter passage having a large diameter and a small-diameter passage that is continuous with the large-diameter passage and has a smaller diameter than the large-diameter passage serving as the orifice.
Therefore, by making a part of the orifice passage a small-diameter passage, it is possible to suppress the pulsation of the hydraulic pressure while suppressing a decrease in the hydraulic pressure of the brake fluid passing through the orifice passage.

(F) a housing with a built-in external gear pump;
A discharge valve component mounting hole formed in the housing and mounted with a discharge valve component discharging the brake fluid pumped from the rotary pump;
With
The discharge valve component includes a valve body, a seat member on which the valve body is seated and a seat member through which fluid flows, a coil spring that biases the valve body toward the seat member, A socket member having a valve body and an accommodation hole for accommodating the coil spring, and a cylindrical wall;
A pump device comprising a cylindrical wall of the socket member provided with a passage communicating from the inside of the accommodation hole to the outside, and an orifice portion formed in the passage.
Therefore, since the orifice passage can be integrated with the discharge valve constituting body, the number of parts can be reduced.
(Yo) In the pump device according to claim 19,
The external gear pump includes a discharge chamber into which fluid pumped from a pair of gears flows, and the fluid flows from the discharge chamber to the discharge valve structure.
Therefore, since the discharge chamber acts as a damper chamber, the pulsation of the hydraulic pressure can be suppressed.
(T) a housing with a built-in rotary pump;
A discharge valve mounting hole formed in the housing;
A discharge valve assembly that is mounted in the discharge valve mounting hole and discharges fluid discharged from the pump to the outside;
With
The discharge valve component includes a valve body, a seat member on which the valve body is seated and a seat member through which a fluid flows, an elastic body that biases the valve body toward the seat member, A socket member having an accommodation hole for accommodating the valve body and the elastic body,
The pump device according to claim 1, wherein an orifice passage is provided between the rotary pump and the valve body.
Therefore, since the orifice passage can be integrated with the discharge valve constituting body, the number of parts can be reduced.

26 Housing
32 Discharge valve mounting hole
33 Discharge valve assembly
49 Discharge chamber
50 communication path (socket member)
51 Socket material
52 Disc
54 Coil spring (elastic body)
59 receiving hole
60 Seat hole
64 Orifice passage
65 Seat surface
PP, PS gear pump

Claims (5)

A housing with a built-in rotary pump;
A liquid passage through which a fluid formed in the housing and pumped from the rotary pump flows;
A solenoid valve provided on the liquid path;
A discharge valve structure on the liquid path and provided between the electromagnetic valve and the rotary pump;
A discharge valve mounting hole in which the discharge valve structure is formed in the housing is mounted,
With
The discharge valve component includes a valve body, a seat member on which the valve body is seated and a seat member through which fluid flows, an elastic body that biases the valve body toward the seat member, A socket member having an accommodation hole for accommodating the valve body and the elastic body,
2. A pump device according to claim 1, wherein the socket member is provided with an orifice passage communicating from the accommodation hole to the outside. In the pump device according to claim 1,
The socket member comprises a cylindrical wall;
The pump device according to claim 1, wherein the orifice passage is formed in the cylindrical wall. In the pump device according to claim 1 ,
2. The pump device according to claim 1, wherein the orifice passage is formed at a radial position on the seat surface. In the pump device according to claim 1 ,
The rotary pump is a circumscribed gear pump. In the pump device according to claim 4,
The external gear pump includes a discharge chamber into which fluid pumped from a pair of gears flows, and the fluid flows from the discharge chamber to the discharge valve structure.

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