JP2011132807A - Pump device - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To provide a pump device inhibiting enlargement of a pump by increasing flexibility in layout of liquid passages. <P>SOLUTION: Working fluid from a first external gear pump part is discharged from a first discharge port formed on a support plate provided at another side surface side of each gear of a second external gear pump part and supporting a drive shaft through a hollow shaft, and working fluid from the second external gear pump is discharged from a second discharge port formed on the support plate. <P>COPYRIGHT: (C)2011,JPO&amp;INPIT

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 tandem gear pump in which pump chambers are provided on both sides of a center plate.

JP 2009-215932 A

In the above prior art, the discharge port is provided in the side plate or the housing facing the high pressure chamber, so that the layout of the liquid path is limited, which may increase the size of the pump device.
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 that can increase the degree of freedom of layout of the liquid passages and suppress the enlargement of the pump.

In order to achieve the above object, in the first invention, the working fluid from the first circumscribed gear pump section is provided on the other side surface of each gear of the second circumscribed gear pump section through the hollow shaft and pivotally supports the drive shaft. It was made to discharge from the 1st discharge port formed in the support plate, and the working fluid from the 2nd external gear pump part was discharged from the 2nd discharge port formed in the support plate.
In the second invention, the discharge liquid passage is constituted by a hollow shaft fixed to at least one of the side plates and penetrating the side plate, and the working fluid is discharged through the hollow shaft.

  Since the working fluid can be guided to a position away from the high-pressure chamber of the pump by the hollow shaft, the degree of freedom of layout of the liquid passage is increased and the pump can be prevented from being enlarged.

FIG. 2 is a hydraulic circuit diagram of the brake hydraulic pressure control device according to the first embodiment. FIG. 3 is a skeleton diagram of a housing of the hydraulic control unit according to the first embodiment. FIG. 3 is a skeleton diagram of a housing of the hydraulic control unit 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. 3 is a perspective view of a housing according to Embodiment 1. FIG. It is an exploded view of the pump unit of Example 1. It is a perspective view of the pump unit of Example 1. It is a fragmentary sectional view of the state where the pump unit of Example 1 was stored in a housing. It is sectional drawing of the pump unit of Example 1. FIG.

[Example 1]
[Configuration of brake hydraulic circuit]
FIG. 1 is a hydraulic circuit diagram of the brake hydraulic pressure control device 32. The hydraulic circuit is formed in a hydraulic control unit 30 provided between the master cylinder M / C and the wheel cylinder W / C.
The brake fluid pressure control device 32 performs fluid pressure control according to the required fluid pressure of the vehicle dynamics control (VDC) and the anti-lock brake system (ABS) from the controller. The brake fluid pressure control device 32 has a piping structure called X piping, which is composed of two systems of a P system brake fluid pressure circuit 21P and an S system brake fluid pressure circuit 21S. 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. The brake fluid pressure control device 32 and each wheel cylinder W / C are connected to wheel cylinder ports 19RL, 19FR, 19FL, 19RR formed in an upper surface 31c of the housing 31 described later. The pump unit P drives a gear pump PP (second external gear pump unit) and a gear pump PS (first external gear pump unit), each of which is provided with a pair of external gears provided in the P system and S system, by a single motor M (drive source). It is a tandem gear pump.

The master cylinder M / C and the fluid pressure control unit 30 are connected in fluid passages 18P and 18S via master cylinder ports 20P and 20S drilled in a port connection surface 31a1 of the housing 31 described later. The liquid path 18 and the suction side of the pump unit P are connected by liquid paths 10P and 10S. On the liquid path 18P, a master cylinder pressure sensor 22 is provided between the master cylinder port 20P and a connection portion between the liquid path 10P. Check valves 5P and 5S are provided on the liquid passage 10 and between the master cylinder ports 20P and 20S and the pump unit P. The check valves 5 are connected to the pump unit from the master cylinder ports 20P and 20S. Allow the flow of brake fluid pressure in the direction toward P, and prohibit the flow in the opposite direction.
The discharge side of the pump unit P and each wheel cylinder W / C are connected by liquid paths 11P and 11S. On each of the liquid passages 11, pressure increasing valves 3FL, 3RR, 3FR, 3RL, which are normally open solenoid valves corresponding to the respective wheel cylinders W / C, are provided. Further, check valves 6P and 6S are provided on each liquid passage 11 and between each pressure increasing valve 3 and the pump unit P. Each check valve 6 allows the flow of the brake fluid pressure in the direction from the pump unit P toward the pressure increasing valve 3 and prohibits the flow in the opposite direction. Discharge pressure sensors 23P and 23S are provided between the pressure increasing valves 3 and the pump unit P on each liquid passage 11.

Furthermore, each fluid passage 11 is provided with fluid passages 16FL, 16RR, 16FR, and 16RL that bypass each pressure increasing valve 3, and the fluid passage 16 is provided with check valves 9FL, 9RR, 9FR, and 9RL. Yes. Each check valve 9 allows the flow of brake fluid pressure in the direction from the wheel cylinder W / C toward the pump unit P, and prohibits the flow in the opposite direction.
The master cylinder M / C and the liquid path 11 are connected by liquid paths 12P and 12S, and the liquid path 11 and the liquid path 12 merge between the pump unit P and the pressure increasing valve 3. On each liquid passage 12, gate-out valves 2P and 2S, which are normally open solenoid valves, are provided. Each liquid path 12 is provided with liquid paths 17P and 17S that bypass each gate-out valve 2, and the liquid path 17 is provided with check valves 8P and 8S. Each check valve 8 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 15P and 15S are provided on the suction side of the pump unit P, and the reservoir 15 and the pump unit P are connected by liquid passages 10P and 10S. Between the reservoir 15 and the pump unit P, check valves 7P and 7S are provided.
The wheel cylinder W / C and the liquid path 10 are connected by liquid paths 13 </ b> P and 13 </ b> S, and the liquid path 13 and the liquid path 10 merge between the check valve 7 and the reservoir 15. The liquid passages 13 are provided with pressure reducing valves 4FL, 4RR, 4FR, 4RL, which are normally closed solenoid valves.

[Housing configuration]
2 and 3 are skeleton diagrams of the housing 31 of the hydraulic control unit 30. FIG. 2 and 3 show a state in which each valve, control unit, and motor M are removed for easy understanding of the drawings. In the following description, in FIG. 2 and FIG. 3, the surface where the master cylinder port 20 is open is the front surface 31a, the back surface of the front surface 31a is the rear surface 31b, the surface where the wheel cylinder port 19 is open is the top surface 31c, and the top surface 31c. The rear surface is referred to as a lower surface 31d, the left side surface relative to the front surface 31a is referred to as a left side surface 31e, and the right side surface relative to the front surface 31a is referred to as a right side surface 31f. 2A is a view of the housing 31 viewed from the front surface 31a, FIG. 2B is a view of the housing 31 viewed from the upper surface 31c, and FIG. 2C is a view of the housing 31 viewed from the lower surface 31d. 3A is a view of the housing 31 as seen from the rear surface 31b, FIG. 3B is a view of the housing 31 as seen from the right side surface 31f,
FIG. 3C is a view of the housing 31 as viewed from the left side 31e.
4, 5, and 6 are perspective views of the housing 31. 4 is a view as seen from the rear face 31b, the upper face 31c, and the left face 31e, FIG. 5 is a view as seen from the front face 31a, the upper face 31c, and the left face 31e, and FIG. 6 is a view showing a state where the unit case 34 and the motor M are attached. It is.
The housing 31 is a substantially rectangular parallelepiped, and the motor M is attached to the front surface 31a side, the solenoid valve groups of the gate-out valve 2, the pressure increasing valve 3 and the pressure reducing valve 4 on the rear surface 31b 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 34. The housing 31 is formed with a power supply hole 24 penetrating the front surface 31a and the rear surface 31b, and the electric unit and the motor M are connected by inserting an electrode of the motor M into the power supply hole 24.
The housing 31 has a valve mounting hole in which each solenoid valve group is mounted by press-fitting or caulking, a plurality of liquid passages connecting between each port and each solenoid valve group, and each cylinder (wheel cylinder W / C). , A port (foil cylinder port 19, master cylinder port 20) connected to the master cylinder M / C) and a hole for arranging the reservoir 15 are formed. These holes, liquid passage holes and the like are drilled from the outside of the housing 31 to each surface by a drill or the like.
On the upper surface 31c side of the front surface 31a, a port connection surface 31a1 having a surface normal to the motor M side and substantially parallel to the front surface 31a is formed. The port connection surface 31a1 protrudes forward (motor drive axial direction motor side) with respect to the front surface 31a, and the master cylinder port 20 is formed in this portion.
The pump unit P is accommodated in a substantially cylindrical accommodating portion 41 that penetrates from the front surface 31 a to the rear surface 31 b of the housing 31. In the accommodating portion 41, the opening on the rear surface 31 b side is sealed by the end plate 35. Further, discharge portion accommodation holes 47P and 47S are formed so as to be substantially orthogonal to the accommodation portion 41 from the left side surface 31e to the right side surface 31f of the housing 31. Check valves 6P and 6S connected to the discharge liquid passages 56P and 56S (second and first discharge ports) of the pump unit P are inserted into the discharge portion accommodation holes 47P and 47S.

[Configuration of pump unit]
7 is an exploded view of the pump unit P, and FIG. 8 is a perspective view of the pump unit P. 9 is a partial cross-sectional view of the pump unit P accommodated in the housing 31 as viewed from the axial direction, and FIG. 10 is a radial cross-sectional view of the pump unit P.
The pump unit P includes a motor plate 36 (support plate), second side plates 39P and 39S, drive gears 46p and 46S (second and first drive gears), driven gears 65P and 65S (second and first driven gears). The first side plates 38P and 38S, the drive shaft 63, the driven shaft 66, the center plate 49, and the end plate 35 are provided.
(Composition of housing part)
The pump unit P is accommodated in the accommodating portion 41 that penetrates from the front surface 31 a to the rear surface 31 b of the housing 31. In the accommodating portion 41, the opening on the rear surface 31 b side is sealed by the end plate 35. Further, a discharge portion accommodation hole 47 is formed from the left side surface 31e to the right side surface 31f of the housing 31 so as to be substantially orthogonal to the accommodation portion 41, and check valves 6P connected to the discharge side of the pump unit P in the discharge portion accommodation hole 47, 6S is accommodated. The pump unit P is accommodated in the accommodating portion 41 that penetrates from the front surface 31 a to the rear surface 31 b of the housing 31. In the accommodating portion 41, the opening on the rear surface 31 b side is sealed by the end plate 35.
Low pressure chamber grooves 57 </ b> P and 57 </ b> S are formed on the inner periphery of the accommodating portion 41. A space isolated by the low-pressure chamber groove 57P, the radial side surface of the motor plate 36, and O-rings 45a and 45b described later is formed as a low-pressure chamber 40P. Further, a low-pressure chamber groove 57S, a radial side surface of the center plate 49, and a space isolated by O-rings 45b and 45c described later are formed as the low-pressure chamber 40S.

(Configuration of motor plate)
The outer shape of the motor plate 36 is formed in a substantially cylindrical shape. An O-ring groove 55a is formed on the outer periphery of the motor plate 36, and an O-ring 45a is attached. The motor plate 36 is formed with a through hole 36a penetrating in the axial direction. An oil seal 67 and a ball bearing 68 are inserted into the through-hole 36a so that the drive shaft 63 is pivotally supported. The motor plate 36 is formed with an intake liquid passage 42P and discharge liquid passages 43P and 43S that communicate the axial one end side surface and the radial side surface of the motor plate 36 with each other.
(Configuration of center plate)
The center plate 49 is made of an iron metal. The outer diameter of the center plate 49 is formed in a substantially columnar shape, and a bottomed hollow portion 49c that opens to the side surface on one end side in the axial direction is formed. An O-ring groove 55b is formed on the outer periphery of the center plate 49, and an O-ring 45b is attached. A gear pump PP is accommodated in the space between the hollow portion 49 c and the motor plate 36. A high pressure chamber 48P is formed by a space formed by the motor plate 36, the center plate 49, the first side plate 38P, and the second side plate 39P. A high pressure chamber 48P is formed by a space formed by the motor plate 36, the center plate 49, the first side plate 38P, and the second side plate 39P. The high pressure chamber 48P is connected to the check valve 6P via the discharge liquid path 56P of the motor plate 36.
The center plate 49 is formed with through holes 49a and 49b penetrating in the axial direction. The drive shaft 63 is rotatably inserted into the through hole 49a together with the oil seal 69. The driven shaft 66 is press-fitted into the through hole 49b and attached in a state in which it cannot rotate. The center plate 49 is formed with an inhalation liquid passage 42 </ b> S that communicates the other axial side surface and the radial side surface of the motor plate 36.

(Configuration of pump cover)
The end plate 35 has a flange portion 35a formed on the outer periphery of a substantially columnar outer diameter. The flange portion 35a is formed with a screw hole 35c for fixing the pump unit P to the housing 31 with a screw. The end plate 35 is formed with a bottomed hollow portion 35d that opens to one axial end side. The gear pump PS is accommodated in a space between the hollow portion 35d and the other axial end side of the center plate 49. Has been. The space formed by the end plate 35, the center plate 49, the first side plate 38S, and the second side plate 39S forms a high pressure chamber 48S. The high pressure chamber 48S is connected to the check valve 6S via a hollow portion 66a of a driven shaft 66 and a discharge liquid passage 56S of the motor plate 36, which will be described later.
An insertion hole 35 b is formed at the bottom of the end plate 35. A drive shaft 63 is inserted into the insertion hole 35b together with the needle bearing 70 so as to be supported.

(Configuration of the first side plate)
The first side plates 38P and 38S have two through holes 38a and 38b made of resin and are formed in the shape of glasses. One end sides of the first side plates 38P and 38S are in contact with the tooth portions of the drive gear 46 and the driven gear 65. An oil seal groove 38c is formed on the other end side of the first side plates 38P and 38S. The oil seals 72P and 72S are oil seals for the second side plates 39P and 39S in a state where the second side plates 39P and 39S, the drive gears 46P and 46S, the driven gears 65P and 65S, and the first side plates 38P and 38S are assembled. It is inserted into the groove 39d and the oil seal groove 38c of the first side plates 38P, 38S.
(Configuration of the second side plate)
The second side plates 39P and 39S are made of resin. The second side plates 39P and 39S are formed with a notch 39e in which a part of a substantially cylindrical shape is notched. One end side in the axial direction of the second side plates 39P and 39S is in contact with the meshing portion between the entire circumference of the tooth portion of the drive gear 46 and the drive gear 46 of the driven gear 65. That is, the notch 39e corresponds to a portion of the driven gear 65 excluding the meshed portion of the driven gear 65 and the drive gear 46.
The second side plates 39P and 39S are formed with a through hole 39a through which the drive shaft 63 passes and a suction port 39b which is a through hole for sucking hydraulic oil. On the other end side of the second side plates 39P, 39S, an oil seal groove 39c is formed by cutting the periphery of the through hole 39a and the suction port 39b into a gourd shape. The oil seals 71P, 71S are formed in the oil seal groove 39c. Is installed.
An oil seal groove 39d into which a part of oil seals 72P and 72S described later is inserted is formed on one end side of the second side plates 39P and 39S.
The second side plate 39P is disposed between the motor plate 36 and the center plate 49. The suction port 39b of the second side plate 39P communicates with the low pressure chamber 40P via the suction liquid path 42P of the motor plate 36. The second side plate 39S is disposed between the end plate 35 and the center plate 49. The suction port 39b of the second side plate 39S is communicated with the low pressure chamber 40S via the suction liquid passage 42S of the center plate 49.

(Configuration of drive shaft)
The outer diameter of the drive shaft 63 is a substantially round bar shape, and one end side is a flat plate portion 63a. Drive gears 46 </ b> P and 46 </ b> S are attached to the drive shaft 63 so as to rotate integrally with the drive shaft 63. The flat plate portion 63a is connected to the motor M.
(Configuration of driven shaft)
It is a hollow shaft of the driven shaft 66, and a hollow portion 66a is formed inside. The hollow portion 66a connects the high-pressure chamber 48S and the discharge liquid path 56S of the motor plate 36. A large-diameter portion 66 b is formed on the outer diameter of the driven shaft 66, and the large-diameter portion 66 b is press-fitted into the center plate 49.
Driven gears 65P and 65S are attached to the driven shaft 66 so as to be rotatable relative to the driven shaft 66. The driven gears 65P and 65S mesh with the drive gears 46P and 46S and are driven to rotate.
(Check valve configuration)
The check valves 6P and 6S are formed by communication members 44P and 44S, filters 50P and 50S, seat members 51P and 51S, balls 53P and 53S, springs 54P and 54S, and locking members 52P and 52S.
The communication members 44P and 44S have substantially cylindrical outer diameters, and have discharge liquid passages 43P and 43S formed of hollow through holes. One ends of the communication members 44P and 44S are inserted together with O-rings 59P and 59S into insertion holes 64P and 64S formed on the side surface of the center plate 49. The discharge liquid paths 43P and 43S of the communication members 44P and 44S are connected to the discharge liquid paths 56P and 56S of the motor plate 36. At this time, the communication members 44P and 44S pass through the low pressure chamber 40S. Filters 50P and 50S are provided in openings at the other ends of the communication members 44P and 44S.
The sheet members 51P and 51S have bottomed hollow portions. The communication members 44P and 44S and the filters 50P and 50S are accommodated in the hollow portions of the sheet members 51P and 51S. Through holes 60P and 60S penetrating between the hollow portion and the outside are formed at the bottom of the sheet members 51P and 51S. The locking members 52P and 52S have spring holes 61P and 61S larger in diameter than the balls 53P and 53S. In a state where the springs 54P, 54S and the balls 53P, 53S are inserted into the spring holes 61P, 61S, the discharge portion accommodation holes 47P, 47S so that the balls 53P, 53S are seated in the through holes 60P, 60S of the sheet members 51P, 51S. Are inserted into the discharge portion receiving holes 47P and 47S and locked by the caulking portions 62P and 62S.

[Action]
In the conventional pump device, it is necessary to provide a discharge port on the side plate or the housing facing the high-pressure chamber, so that the layout of the liquid path is limited, which may increase the size of the pump device.
Therefore, in the pump device 33 according to the first embodiment, the driven shaft 66 is configured by a hollow shaft fixed to the center plate 49. The working fluid from the gear pump PS is discharged from a discharge liquid passage 56S formed in the motor plate 36 through a hollow portion 66a formed in the driven shaft 66. Further, the working fluid from the gear pump PP is discharged from a discharge liquid passage 56P formed in the motor plate 36.
Since the check valves 6P and 6S are attached to the discharge liquid passages 56P and 56S, the member in which the discharge liquid passages 56P and 56S are formed needs to have an axial length for attaching the check valves 6P and 6S. Since the motor plate 36 supports the drive shaft 63, the motor plate 36 needs to have an axial length in which the oil seal 67 and the ball bearing 68 are inserted. On the other hand, the center plate 49 only needs to be able to separate the gear pump PP side and the gear pump PS side, and for that purpose, the axial length is not so large. In the first embodiment, the discharge fluid passages 56P and 56S are formed in a concentrated manner on the motor plate 36, whereby the check valves 6P and 6S are attached to the motor plate 36 that originally requires the axial length, and the axial direction of the center plate 49 The length can be shortened. Therefore, the axial length of the pump device 33 as a whole can be shortened.

[effect]
The effects of the pump device 33 of the first embodiment are listed below.
(1) Engage with a drive gear 46S (first drive gear) and a drive gear 46S, which are rotationally driven in conjunction with a drive shaft 63 driven by a motor M (drive source), and are supported by the driven shaft 66 and rotate. A gear pump PS (first external gear pump portion) composed of a driven gear 65S (first driven gear), a drive gear 46P (second drive gear) that rotates in conjunction with a drive shaft 63 driven by a motor M, and a drive Each gear is engaged between the gear pump PP (second external gear pump portion) including a driven gear 65S (second driven gear) that meshes with the gear 46P and is supported by the driven shaft 66 and rotates, and between the gear pump PP and the gear pump PS. 46, 65, and a center plate 49 provided on one side surface. The driven shaft 66 is a hollow shaft fixed to the center plate 49, and each driven gear 65P, 65S is driven. 66, the working fluid from the gear pump PS passes through the hollow shaft and is provided on the other side of the gears 46 and 65 of the gear pump PP to support the drive shaft 63 (support) The discharge fluid passage 56S (first discharge port) formed in the plate) is discharged, and the working fluid from the gear pump PP is discharged from the discharge fluid passage 56P (second discharge port) formed in the motor plate 36. did.
By concentrating and forming the discharge liquid passages 56P and 56S on the motor plate 36, the check valves 6P and 6S are attached to the motor plate 36 whose axial length cannot be shortened due to the ball bearing 68, and the center plate 49 The axial length of can be shortened. Therefore, the axial length of the pump device 33 as a whole can be shortened.

(2) a drive gear 46S that rotates in conjunction with a drive shaft 63 driven by a motor M (drive source); a driven gear 65S that meshes with the drive gear 46S and is supported by the driven shaft 66 and rotates; A second side plate 39S and a first side plate 38S (a pair of side plates) provided adjacent to both sides of the gears 46S and 65S and facing the side surfaces of the gears 46S and 65S. , 65S, the discharge fluid path 56S is fixed to at least one of the second side plate 39S and the first side plate 38S in the pump device 33 that pumps the working fluid sucked from outside through the discharge liquid path 56S. The second side plate 39S and the first side plate 38S (side plate) are constituted by a hollow shaft that passes through, and the working fluid is a hollow portion 66 of the hollow shaft. It was to be discharged through the inside.
Therefore, it is not necessary to form the discharge liquid passage 56S in the center plate 49, and the axial length can be shortened. Therefore, the axial length of the pump device 33 as a whole can be shortened.
(3) The hollow shaft is a driven shaft 66, and the driven gear 65S is supported so as to be rotatable relative to the hollow shaft.
Therefore, the hollow shaft and the driven shaft 66 can be used together, and the pump device 33 can be downsized.

[Other Examples]
As described above, the present invention has been described based on the first embodiment. However, the specific configuration of each invention is not limited to each embodiment, and even if there is a design change or the like without departing from the gist of the invention. Are included in the present invention.
For example, the pump device 33 according to the first embodiment uses a tandem gear pump that is a double gear pump, but may be a single gear pump.

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 1,
A side plate is provided facing the other side of each gear,
The pump device according to claim 1, wherein the side plate is in contact with an entire circumference of a tooth portion of the drive gear and a meshing portion of the drive gear and the driven gear.
Therefore, since the contact area between the side plate and the driven gear can be reduced, the friction between the side plate and the driven gear can be reduced, and the drive source can be downsized.
(B) In the pump device according to claim 1 or (a),
A first system brake fluid pressure circuit and a second system brake fluid pressure circuit;
The first external gear pump section is connected to the first system brake hydraulic circuit, and the second external gear pump section is connected to the second system brake hydraulic circuit.
Therefore, it is possible to pump the working fluid to the two brake fluid pressure circuits with one pump device, to reduce the friction and to reduce the size of the drive source.
(C) In the pump device according to claim 1 or (a) and (b) above,
A pump device comprising a side plate formed separately on both side surfaces of each gear.
Therefore, manufacturing cost can be suppressed while manufacturing accuracy is maintained when manufacturing each side plate.
(D) In the pump device according to claim 2 or claim 3,
The pump device according to claim 1, wherein the side plate is in contact with an entire circumference of a tooth portion of the drive gear and a meshing portion of the drive gear and the driven gear.
Therefore, since the contact area between the side plate and the driven gear can be reduced, the friction between the side plate and the driven gear can be reduced, and the drive source can be downsized.
(E) In the pump device according to claim 2 or claim 3 or (d) above,
A two-system brake device is provided with a first system brake fluid pressure circuit and a second system brake fluid pressure circuit,
The drive gear and the driven gear have two sets,
The working fluid pumped by one set of the driving gear and the driven gear is supplied to the first system brake hydraulic circuit, and the working fluid pumped by the other set of the driving gear and the driven gear is the second system. A pump device characterized by being supplied to a brake hydraulic circuit.
Therefore, it is possible to pump the working fluid to the two brake fluid pressure circuits with one pump device, to reduce the friction and to reduce the size of the drive source.

21P P system brake hydraulic circuit 21S S system brake hydraulic circuit 33 Pump device 35 End plate 36 Motor plate (support plate)
38P, 38S First side plate 39P, 39S Second side plate 46P Drive gear (second drive gear)
46S drive gear (first drive gear)
47P, 47S Discharge portion accommodating hole 49 Center plate 56P Discharge liquid passage (second discharge port)
56S Discharge liquid passage (first discharge port)
63 Drive shaft 65P driven gear (second driven gear)
65S driven gear (first driven gear)
66 Driven shaft (hollow shaft)
66a Hollow part M Motor (drive source)
PP gear pump (second external gear pump)
PS gear pump (first external gear pump part)

Claims (3)

A first external gear pump unit comprising a first drive gear that rotates in conjunction with a drive shaft driven by a drive source, and a first driven gear that meshes with the first drive gear and rotates while being supported by the driven shaft. When,
A second drive gear that rotates in conjunction with the drive shaft driven by the drive source, and a second driven gear that meshes with the second drive gear and is supported by the driven shaft and rotates. The external gear pump,
A center plate provided on one side of each gear between the first circumscribed gear pump portion and the second gear pump portion;
Have
The driven shaft is composed of a hollow shaft fixed to the center plate, and each driven gear is supported so as to be rotatable relative to the driven shaft,
The working fluid from the first external gear pump part passes through the hollow shaft and is provided on the other side of each gear of the second external gear pump part, and is formed on a first discharge plate formed on a support plate that supports the drive shaft. A pumping device characterized in that the working fluid discharged from the outlet and discharged from the second external gear pump unit is discharged from a second discharge port formed in the support plate. A drive gear that rotates in conjunction with a drive shaft driven by a drive source;
A driven gear that meshes with the drive gear and is supported by the driven shaft and rotates;
A pair of side plates provided adjacent to both sides of the gear and facing the side of the gear;
A pump device that pumps the working fluid sucked from the outside by rotation of each gear to the outside through a discharge liquid path,
The pump device according to claim 1, wherein the discharge liquid path is configured by a hollow shaft that is fixed to at least one of the side plates and penetrates the side plate, and the working fluid is discharged through the hollow shaft. The pump device according to claim 2,
The hollow shaft is the driven shaft, and the driven gear is supported so as to be rotatable relative to the hollow shaft.

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