JP2001080498A - Vehicular brake system - Google Patents

Abstract

PROBLEM TO BE SOLVED: To bleed pump devices in vehicular brake systems of air in appreciable fashion. SOLUTION: A drive shaft 54 is arranged in a horizontal position, and a plurality of rotary pumps 10 and 13 are disposed with their discharge openings 61 and 63 and suction openings 60 and 62 all opened upward. A housing 150 has lines 151 to 154 connected to the suction and discharge openings 60 to 63 and all opened upward. The upward opening of all the suction and discharge openings 60 to 63 of the rotary pumps 10 and 13 can evacuate air, if any in brake fluid, upward.

Description

DETAILED DESCRIPTION OF THE INVENTION

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a brake system for a vehicle which performs brake fluid pressure control using a rotary pump such as a trochoid pump.

[0002]

2. Description of the Related Art Conventionally, in a vehicle brake device having an ABS actuator, a plunger type pump has been used as a pump for the ABS actuator.

[0003] However, in order to meet the demand for miniaturization of the ABS actuator and improvement in volumetric efficiency, a plunger type pump has reached its limit. At present, a rotary pump, for example, a pump using a trochoid pump has been used. Attention has been focused.

[0004]

In a rotary pump such as a trochoid pump having a substantially circular shape, the suction side and the discharge side are arranged at symmetrical positions in the diameter direction of the substantially circular shape.
The suction port and the discharge port connected to each of the suction side and the discharge side are drawn out in symmetric directions.

However, with such a configuration,
Since at least one of the suction port and the discharge port is not formed facing upward, when air is mixed in the trochoid pump, there is a problem that the air cannot be removed.

SUMMARY OF THE INVENTION The present invention has been made in view of the above circumstances, and has as its object to satisfactorily remove air from a pump device provided in a vehicle brake device.

[0007]

In order to achieve the above object, according to the first aspect of the present invention, the drive shaft (54) is arranged horizontally, and the discharge ports (61, 63) are pulled out in the top direction. It is characterized by having.

Thus, a plurality of rotary pumps (10,
By making all the discharge ports of 13) drawn out in the upward direction, even if air has entered the brake fluid, the air can escape in the upward direction. In this case, for example, as shown in claim 10,
Pipes (151) connected to each of the suction port and the discharge port
To 154), and the pipe is preferably drawn upward.

More specifically, as shown in claim 2, a first annular shape formed on the end face of the both side plates (71a, 71b, 71c, 71d) on the rotating part side so as to surround the drive shaft. A groove (61a, 63a) is formed, and a seal member (171, 172) is provided so as to sandwich the inner rotor and the outer rotor in the first annular groove. When the brake fluid is disposed, the brake fluid can flow in the longitudinal direction of the first annular groove through the gap in the first annular groove, and at least one of the side plates has the first fluid. By forming the passages (61b, 63b) drawn upward from the uppermost part of the annular groove, the discharge port can be formed.

In this case, a region is formed in the first annular groove such that the entire outer periphery of the first annular groove is not in contact with the seal member. What is necessary is just to allow the brake fluid to flow.

In the invention described in claim 4, the side plate disposed between the plurality of rotary pumps is a plurality of members (71b, 71c) divided in a direction substantially perpendicular to the drive shaft. It is characterized by being constituted.

As described above, if the side plate is composed of a plurality of members, the positioning of the plurality of rotary pumps can be performed separately, so that the positioning can be easily performed at the optimum position.

According to the fifth aspect of the present invention, there is provided a housing (150) having a concave portion (150a) for accommodating the pump main body, and the pump main body is inserted into the concave portion in the axial direction of the drive shaft and inserted into the housing. A spring member (210) that presses the pump body in the direction opposite to the insertion direction is disposed between the tip of the pump body in the insertion direction and the bottom of the recess. Features.

Thus, by disposing the leaf spring between the tip of the pump body and the bottom of the concave portion, the axial force can be stabilized while securing the axial force of the pump body.

According to a sixth aspect of the present invention, a spring member (220) for pressing the pump body inserted in the concave portion in the insertion direction is disposed at the entrance of the concave portion. The effect of can be obtained.

A screw member (200) is screwed and fixed to the entrance of the recess formed in the housing, and the pump body is pressed by the screw member in the direction of insertion into the recess. In what is done,
Since it is difficult to stabilize the axial force, it can be said that the above effect is particularly obtained.

In the invention described in claim 8, the pump body and the concave portion have a substantially cylindrical shape, and a portion of the inner peripheral surface of the concave portion from which the suction port and the discharge port are drawn out has: A second annular groove (161 to 164) is formed so as to surround the circumferential direction of the pump body.

By forming the second annular groove on the inner peripheral surface of the recess at the portion from which the discharge port and the suction port are drawn out, even if air enters the second annular groove, the air flows in the top direction. Since it can be moved, air can be vented.

According to the ninth aspect of the present invention, the holder (11b) is provided on the surface of the housing where the concave portion is formed.
The motor shaft (11) is fixed through the motor shaft (11) so as to be in contact with both the inner periphery of the hole of the holder and the inner periphery of the entrance of the hole of the side plate.
a) or a bearing (180) for supporting at least one of the drive shafts is provided.

With this configuration, the bearing can prevent the motor shaft and the drive shaft from being misaligned.

[0021] The eleventh aspect of the present invention is characterized in that a stopper (213) is provided at the tip of the drive shaft.

By providing the stopper at the tip of the drive shaft, it is possible to prevent the drive shaft from coming off the pump body by the stopper.

According to the twelfth aspect of the present invention, the drive shaft has a slot (54) whose longitudinal direction is the axial direction of the drive shaft.
a) is formed, a key (54b) is provided in the elongated hole, and the inner rotor is driven by the drive shaft by torque transmission by the key.

As described above, if the key is arranged in the elongated hole,
Even if the drive shaft moves in the direction to come off from the pump body, it is possible to prevent the key from being pressed by the drive shaft due to the movement. Thereby, reliable torque transmission to the inner rotor can be performed.

The reference numerals in parentheses of the above means indicate the correspondence with specific means described in the embodiments described later.

[0026]

DETAILED DESCRIPTION OF THE PREFERRED EMBODIMENTS (First Embodiment) An embodiment of the present invention shown in the drawings will be described below.

FIG. 1 is a schematic diagram of a brake pipe of a brake device to which an internal gear pump (trochoid pump) is applied as a rotary pump. Hereinafter, a basic configuration of the brake device will be described with reference to FIG. Here, the front wheel drive 4
An example in which the brake device according to the present invention is applied to a vehicle that constitutes an X-pipe hydraulic circuit including respective pipe systems of a right front wheel-left rear wheel and a left front wheel-right rear wheel in a wheeled vehicle will be described.

As shown in FIG. 1, the brake pedal 1 is connected to a booster 2, and the booster 2 boosts the brake pedal force and the like.

The booster 2 has a bush rod or the like for transmitting the boosted treading force to the master cylinder 3, and this bush rod presses a master piston disposed on the master cylinder 3. As a result, a master cylinder pressure is generated. The brake pedal 1, the booster 2, and the master cylinder 3 correspond to brake fluid pressure generating means.

The master cylinder 3 supplies a brake fluid to the master cylinder 3 and a master reservoir 3a for storing excess brake fluid in the master cylinder 3.
Is connected.

The master cylinder pressure is transmitted to a wheel cylinder 4 for the right front wheel FR and a wheel cylinder 5 for the left rear wheel RL via an anti-lock brake device (hereinafter referred to as ABS). In the following description, the right front wheel FR and the left rear wheel RL will be described. However, the same applies to the left front wheel FL and the right rear wheel RR, which are the second piping system, and the description is omitted.

This brake device has a pipeline (main pipeline) A connected to the master cylinder 3, and this pipeline A is provided with a check valve 22a and a linear differential pressure control valve 22. The line A is divided into two parts by the linear differential pressure control valve 22. That is, the pipe A has a pipe A1 receiving the master cylinder pressure between the master cylinder 3 and the linear differential pressure control valve 22, and a pipe A2 between the linear differential pressure control valve 22 and each wheel cylinder 4, 5. Divided into

The linear differential pressure control valve 22 is normally in a communicating state. However, when the master cylinder pressure is lower than a predetermined pressure, when the wheel cylinders 4, 5 are suddenly braked, or during traction control, the master cylinder side And a predetermined differential pressure is generated between the wheel cylinder side. This linear differential pressure valve 22 can linearly adjust the set value of the differential pressure.

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

The pressure increase control valves 30 and 31 are configured as two-position valves that can control the communication and cutoff states by an electronic control unit for ABS (hereinafter referred to as ECU). When the two-position valve is controlled to communicate, the master cylinder pressure or the brake fluid pressure generated by the discharge of the pump can be applied to the wheel cylinders 4 and 5. These first and second pressure increase control valves 30 and 31
At the time of normal brake without BS control being executed,
It is controlled to be always in communication.

The pressure increase control valves 30 and 31 are provided with safety valves 30a and 31a in parallel, respectively. When the brake depression is stopped and the ABS control is completed, brake fluid is supplied from the wheel cylinders 4 and 5 side. Is to be eliminated.

The line B connecting the line A and the reservoir 40 between the first and second pressure increase control valves 30 and 31 and the wheel cylinders 4 and 5 is connected and disconnected by an ECU for ABS. Pressure reduction control valves 32 and 33 capable of controlling the state are provided, respectively. These pressure reduction control valves 32 and 33 are
In the normal brake state (when the ABS is not operated), the vehicle is always in a shut-off state.

A rotary pump 13 is provided in a pipe C connecting the linear differential pressure control valve 22 and the pressure increase control valves 30 and 31 in the pipe A with the reservoir 40. On the discharge port side of the rotary pump 13, a safety valve 13A is provided.
The brake fluid does not flow back. Further, a motor 11 is connected to the rotary pump 13, and the rotary pump 13 is driven by the motor 11.
The details of the rotary pump 13 will be described later.

Then, the reservoir 40 and the master cylinder 3
(Auxiliary pipeline) D is provided to connect A two-position valve 23 is disposed in the pipeline D, and the two-position valve 23 is normally shut off so that the pipeline D is shut off. The two-position valve 23 is set in a communication state at the time of brake assist, traction control, or the like.
Pumps the brake fluid in the pipe A1 through the pipe D, discharges the brake fluid to the pipe A2, and makes the wheel cylinder pressure in the wheel cylinders 4, 5 higher than the master cylinder pressure to increase the wheel braking force. I have. In this case, the differential pressure between the master cylinder pressure and the wheel cylinder pressure is held by the linear differential pressure control valve 22.

The reservoir 40 has a reservoir hole 40a connected to the pipe D for receiving the brake fluid from the master cylinder 3 side, and a brake fluid connected to the pipes B and C to escape from the wheel cylinders 4, 5. And a receiving reservoir hole 40b. A ball valve 41 is provided inside the reservoir hole 40a. The ball valve 41 is provided with a rod 43 having a predetermined stroke for moving the ball valve 41 up and down separately from the ball valve 41.

The rod 4 is provided in the reservoir chamber 40c.
The piston 44 is provided with a spring 44 that generates a force that pushes the piston 44 toward the ball valve 41 to push out the brake fluid in the reservoir chamber 40c.

In the reservoir 40 configured as described above, when a predetermined amount of the brake fluid is stored, the ball valve 41 is seated on the valve seat 42 so that the brake fluid does not flow into the reservoir 40. For this reason, more brake fluid than the suction capacity of the rotary pump 13 does not flow into the reservoir chamber 40c, and high pressure is not applied to the suction side of the rotary pump 13.

Next, FIG. 2 shows a sectional view of the pump body 100 including the rotary pumps 10 and 13. This figure shows that the pump body 100 is connected to the ABS actuator housing 150.
, And is installed such that the vertical direction of the drawing sheet is the vertical direction of the vehicle. Hereinafter, the overall configuration of the pump body 100 will be described with reference to FIG.

As described above, the brake device is composed of two systems, the first piping system and the second piping system. For this reason, the pump body 100 is provided with two rotary pumps 13 for the first piping system shown in FIGS. 1 and 2 and a rotary pump 10 for the second piping system shown in FIG. ing. The rotary pumps 10 and 13 are driven by one drive shaft 54.

The casing constituting the outer shape of the pump body 100 includes first, second, third, and fourth cylinders (side plates) 71a, 71b, 71c, 71d, and first and second cylindrical central plates 73a, 73a. 73b.

Then, the first cylinder 71a, the first center plate 73a, the second cylinder 71b, the third cylinder 71
c, the second center plate 73b and the fourth cylinder 71d are sequentially stacked, and the outer periphery of the overlapping portion is welded to form the pump body 100 having an integral structure. The pump body 100 having such an integrated structure is
It is inserted into a substantially cylindrical recess 150a formed in the housing 150 for the ABS actuator.

The ring-shaped male screw member 200 is screwed into the female screw groove 150b dug at the entrance of the concave portion 150a, and the pump body 100 is fixed to the housing 150.

Further, a leaf spring (disc spring) 210 is disposed between the distal end position of the pump body 100 in the insertion direction and the bottom of the recess 150a. The axial force of the pump body 100 (the force applied in the insertion direction of the pump body 100) is ensured by the leaf spring 210.

In order to fix the pump body 100 to the housing 150, in other words, to prevent the pump body 100 from rattling inside the housing 150 due to high brake fluid pressure when the pump body 100 sucks and discharges the brake fluid. , A large axial force must be secured.

However, if the above-mentioned axial force is obtained only by screwing the male screw member 200, a large variation may occur in the axial force. For this reason, by disposing the leaf spring 210, the axial force of the pump body 100 can be ensured while securing the axial force.
The axial force applied to the shaft is minimized without becoming excessive. Thereby, the deformation of the pump body 100 can be suppressed.

The case 211 disposed between the leaf spring 210 and the bottom of the recess 150a is configured such that one end of the leaf spring 210 is in contact with the case 211, and a large force is received from the end of the leaf spring 210. Is to convert a large force received from the end of the leaf spring 210 into a wide surface pressure so as not to locally touch the bottom of the concave portion 150a.

The first cylinder 7 of the pump body 100
The hollow circular plate 212 disposed between the plate spring 1a and the leaf spring 210 is configured so that one end of the leaf spring 210 is in contact with the pump body 100. So that it does not locally affect
This is for converting a large force received from the end of the leaf spring 210 into a wide surface pressure. The distal end of the drive shaft 54 is inserted into the hollow portion 212a of the plate 212. Then, the concave portion 150 of the drive shaft 54 is
On the bottom side of “a”, a ring-shaped stopper 213 fitted to the drive shaft 54 is provided. This stopper 213
Is larger than the diameter of the hollow portion 212a of the plate 212, so that the stopper 213 contacts the plate 212 to restrict the movement even when the drive shaft 54 moves to the right side of the drawing. Note that a groove 214 provided in the circumferential direction is formed at the tip of the drive shaft 54,
A C-ring 215 is arranged in the groove 214.
The C-ring 214 prevents the stopper 213 from coming off from the tip of the drive shaft 54 even if it comes to come off.

The first, second, third and fourth cylinders 7
1a, 71b, 71c, and 71d have first, second, third, and fourth center holes 72a, 72b, 72c, and 72d, respectively.
Is provided. The bearing 51 is provided on the inner periphery of the first center hole 72a formed in the first cylinder 71a, and the fourth center hole 72 formed in the fourth cylinder 71d is provided.
A bearing 52 is provided on the inner periphery of c. First to first
A drive shaft 54 is fitted in the fourth center holes 72a to 72d, and is supported by bearings 51 and 52. Thus, bearings 51 and 52 are arranged on both sides of rotary pumps 10 and 13.

FIG. 3 is a sectional view taken along line AA of FIG. 2, and the structure of the rotary pumps 10 and 13 will be described with reference to FIGS.

The rotary pump 10 is disposed in a rotor chamber 50a formed by sandwiching both sides of a first cylindrical central plate 73a between a first cylinder 71a and a second cylinder 71b. The rotary pump 10 is constituted by an internal gear pump driven by a drive shaft 54. The rotary pump 10 includes a rotating portion including an outer rotor 10a having an inner tooth portion formed on the inner circumference and an inner rotor 10b having an outer tooth portion formed on the outer circumference, and is driven in a hole of the inner rotor 10b. The configuration is such that the shaft 54 is inserted. A key 54b is fitted in a long hole 54a (see FIG. 2) formed in the drive shaft 54, the axial direction of which is the longitudinal direction.
0b is transmitted.

Outer rotor 10a and inner rotor 1
In the case of Ob, a plurality of gaps 10c are formed by meshing the internal teeth and the external teeth formed respectively. The rotation of the drive shaft 54 changes the size of the gap 10c so that the brake fluid can be sucked and discharged.

The rotary pump 13 is arranged in a pump chamber 50b formed by sandwiching both sides of a second cylindrical central plate 73b between a third cylinder 71c and a fourth cylinder 71d. The rotary pump 13 is also a rotary pump 1
0 and the outer rotor 13a and the inner rotor 1
3b (see FIG. 1), and is constituted by an internal gear pump provided with the rotary pump 10 around the drive shaft 54.
The arrangement is rotated by 80 °. By arranging in this manner, the gap 10c on the suction side and the gap 10c on the discharge side of each of the rotary pumps 10 and 13 are connected to the drive shaft 54.
And a symmetrical position with respect to the center, so that the high brake fluid pressure on the discharge side can offset the force applied to the drive shaft 54.

The first cylinder 71a has a rotary pump 10
, A suction port 60 communicating with the gap 10c on the suction side, and a discharge port 61 communicating with the gap 10c on the discharge side. The suction port 60 is formed so as to penetrate from the end face of the first cylinder 71a on the rotary pump 10 side to the end face on the opposite side, and is further drawn out from the end face on the opposite side to the outer peripheral face toward the top. The brake fluid is introduced with the outer peripheral surface side of the suction port 60 as an inlet.

The suction port 60 is connected to the housing 150
Is connected to a suction pipe 151 formed in the housing 150 via an annular groove 161 formed on the entire circumference of the inner peripheral surface of the concave portion facing the first cylinder 71a.

The discharge port 61 is connected to the first cylinder 71a.
And the second cylinder 71b extends from the end face on the rotating part side of the rotary pump 10 to the outer peripheral face. This discharge port 61 is specifically configured as follows.

The first cylinder 71a and the second cylinder 71
b, an annular groove (first annular groove) formed so as to surround the drive shaft 54 on the end face on the rotating portion side of the rotary pump 10.
61a are provided.

In the annular groove 61a, a ring-shaped seal member 171 is provided so as to sandwich the outer rotor 10a and the inner rotor 10b.
The seal member 171 is composed of a resin member 171a disposed on the rotating part side and a rubber member 171b pressing the resin member 171a on the rotating part side. The inner peripheral side of the seal member 171 includes a gap between the central plate 73a and the outer periphery of the outer rotor 10a opposed to the suction-side gap 10c and the suction-side gap 10c. The center plate 73a includes a gap 10c on the discharge side and a gap between the outer periphery of the outer rotor 10a facing the gap 10c on the discharge side and the center plate 73a. That is, the relatively low-pressure portion and the relatively high-pressure portion on the inner and outer circumferences of the seal member 171 are sealed by the seal member 171.

The sealing member 171 is provided with the annular groove 61a.
Is configured so as to be in contact with the inner periphery and not partially in contact with the outer periphery. Therefore, the sealing member 171 of the annular groove 61a
A part that is not in contact with a part of the outer periphery is a gap.
In other words, the entire circumference of the seal member 17 is
There is an area configured so as not to be in contact with 1, and the brake fluid can flow through this area. Further, a pipe line 61b is drawn from the uppermost position of the annular groove 61a to the first cylinder 71a in a ceiling direction. The discharge port 61 is constituted by the gap of the annular groove 61a configured as described above and the conduit 61b.

The discharge port 61 is connected to the housing 150
Through an annular groove 162 formed on the entire periphery of the inner peripheral surface of the concave portion where the distal end position of the pump body 100 is disposed,
It is connected to a discharge pipeline 152 formed in the housing 150.

On the other hand, the fourth cylinder 71d is provided with a suction port 62 that communicates with the gap on the suction side of the rotary pump 13 and a discharge port 63 that communicates with the gap on the discharge side.
The suction port 62 is connected to the rotary pump 13 of the fourth cylinder 71d.
It is formed so as to penetrate the end surface on the side and the outer peripheral surface. Specifically, the suction port 62 is configured to extend in the horizontal direction from a gap on the suction side and then be drawn out in the top direction. The suction port 62 is configured to communicate with a center hole 72d in which the drive shaft 54 is arranged. The brake fluid is introduced through the inlet 62 on the outer peripheral surface side of the fourth cylinder 71d. Further, the suction port 62 is formed in the housing 150 through an annular groove 164 formed on the entire inner peripheral surface of the recess 150 a of the housing 150 so as to include the inlet position of the suction port 62. It is connected to the road 153.

As described above, by making the suction port 62 communicate with the center hole 72d, the drive shaft 54 and the bearing 52
And the like, so that the rotation of the drive shaft 54 can be smoothly performed by supplying the brake fluid, and when the air enters from the outside through the center hole 72d, the air can escape by using the suction port 62 as an escape path. . The suction port 62 is connected to the discharge port 6
It is located closer to the motor 11 (outer side of the housing 150) than the motor 3 and the brake fluid pressure in a portion close to the outside of the housing 150 is reduced.

The discharge port 63 is formed so as to extend from the end face on the rotating part side of the rotary pump 13 of the third cylinder 71c and the fourth cylinder 71d to the outer peripheral face. The discharge port 63 has the same structure as the above-described discharge port 61, and has an annular groove 63a that accommodates a ring-shaped seal member 172 including a resin member 172a and a rubber member 172b.
And a conduit 63b drawn from the uppermost position of the annular groove 63a. This discharge port 63
Is connected to the discharge conduit 154 via an annular groove 163 formed in the entire inner peripheral surface of the concave portion 150a of the housing 150 facing the outer periphery of the central plate 73b.

As described above, since the suction ports 60 and 62 and the discharge ports 61 and 63 are drawn in the top direction, even if air enters the rotary pumps 10 and 13, the air escapes in the top direction. Can be done.

Then, the above-described suction pipes 151, 15
3 and the discharge pipelines 152 and 154 all extend upward from the pump main body 100 in the drawing, that is, toward the top. For this reason, even if air enters the inside of the rotary pumps 10 and 13, the air can be drawn out of the pump body 100 through the suction pipes 151 and 153 and the discharge pipes 152 and 154. The suction pipes 151 and 153 and the discharge pipes 152 and 154 are formed with annular grooves 161 to 164.
Through the inlets 60 and 62 or the outlets 61 and 63
Is connected to Further, in the ejection ports 61 and 63,
The pipe lines 61b and 63b are connected at the uppermost ends of the annular grooves 61a and 63a. Since there is no portion where air remains in the annular grooves 61a and 63a, the above-described air bleeding can be performed smoothly.

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

The diameter of the second central hole 72b of the second cylinder 71b and the diameter of the third central hole 72c of the third cylinder 71c are partially larger than that of the drive shaft 54. 1st rotary pump 10 and 2nd rotary pump 1
3 is housed. The seal member 80 is obtained by fitting an O-ring 81 which is a ring-shaped elastic member into a ring-shaped resin member 82 having a groove formed in a radial direction as a depth direction. The resin member 82 is pressed by the force and comes into contact with the drive shaft 54.

The resin member 82 and the third cylinder 71
The cross-sectional shape of the third center hole 72c of FIG. 3c is an arc shape with a circular cutout, and the resin member 82 is fitted into the third center hole 72c of the third cylinder 71c. Have been. Therefore, the notched portion of the resin member 82 functions as a key, and the sealing member 80
Are configured so that they cannot rotate relative to the third cylinder 71c.

The fourth cylinder 71d is concave on the surface opposite to the surface to be welded to the second center plate 73a,
The drive shaft 54 projects from this recess.
The drive shaft 54 has a connection portion 54c that is partially recessed at the protruding end, and the drive shaft 11a of the motor 11 is inserted into the connection portion 54c.
Then, one drive shaft 54 is rotated by the motor 11 via the drive shaft 11a, and the rotary pumps 10 and 13 are driven. Also, the fourth cylinder 71
The diameter of the entrance of the recessed part of d is equal to the hole formed in the holder of the motor 11, and the fourth cylinder 71d
The bearing 180 is disposed by reducing the gap between the recessed portion of the motor 11 and the hole of the holder 11b of the motor 11, and the drive shaft 1
1a is pivotally supported. Here, the example in which the drive shaft 11a is supported by the bearing 180 is described, but the drive shaft 54 may be supported by the drive shaft 11a.

As described above, the holder 11b of the motor 11
When the bearing 180 is disposed in the hole 11c formed in the motor and the concave portion of the fourth cylinder 71d, the motor 11 and the fourth
Since the positioning of the cylinder 71 in the radial direction is performed, the misalignment between the drive shaft 11a and the drive shaft 54 can be minimized.

In the recess formed in the fourth cylinder 71d, an oil seal 90 and an oil seal 91 are arranged and fitted in the axial direction of the drive shaft 54 so as to cover the outer periphery of the drive shaft 54. . Oil seal 90
Serves to seal the brake fluid leaking from the suction port 62 through the center hole 72d. The oil seal 91 serves to seal the brake fluid leaking when the oil seal 90 is broken.

Further, the first, second and fourth cylinders 71
O-rings 74a, 74
b, 74c and 74d are arranged. These O-rings 74 a to 74 d seal brake fluid in the suction pipes 151 and 153 and the discharge pipes 152 and 154 formed in the housing 150.
51 and the discharge line 152, between the discharge line 152 and the discharge line 154, and between the discharge line 154 and the suction line 15.
3 and between the suction pipe 153 and the outside of the housing 150.

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

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

The brake device is used during ABS control where the wheels tend to lock, or when a large braking force is required, for example, when a braking force corresponding to the brake depression force cannot be obtained or when the operation amount of the brake pedal 1 is large. At the same time, the pump body 100 is driven to suck and discharge the brake fluid in the reservoir 40. Then, the pressure of the wheel cylinders 4 and 5 is increased by the discharged brake fluid.

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

At this time, in the rotary pump, the pressure on the discharge side becomes extremely large. For this reason, the brake fluid pressure acts in the direction in which the pump body 100 comes out of the housing 150. However, as described above, the axial force of the pump body 100 is secured by the leaf spring 210 and the male screw member 200. 100 can be prevented from rattling in the housing 150.

Similarly to the pump body 100, the drive shaft 54 is also pulled out of the pump body 100 (rightward on the paper).
, And receives a force corresponding to the radial cross-sectional area of the drive shaft 54. However, as mentioned above,
A stopper 213 is disposed at the tip of the drive shaft 54, and the plate 2 is located at the tip of the first cylinder 71a in the insertion direction.
Since the 12 is disposed, the stopper 213 is in contact with the plate 212, and the movement of the drive shaft 54 in the direction in which the drive shaft 54 comes out of the pump body 100 can be restricted.

In this embodiment, the key 5 for transmitting torque to the inner rotor 10b formed on the drive shaft 54 is used.
4b is fitted to the stopper 213.
Is longer than a period until the plate contacts the plate 212. For this reason, even if the drive shaft 54 moves in the direction in which the drive cylinder 54 comes out of the pump body 100, the key 54 b does not receive an axial force by the drive shaft 54, so that the second cylinder 71.
The key 54b is not pressed against the second cylinder 71b or the fourth cylinder 71d, and the torque can be reliably transmitted to the rotating part. Further, in the present embodiment, a C-ring 215 is disposed at a position of the drive shaft 54 at a position more distal than the stopper 213. Therefore, even if the stopper 213 is about to come off the drive shaft 54, the stopper 213 is held by the C-ring 215, and the drive shaft 54 can be prevented from coming off the pump body 100.

(Second Embodiment) In the first embodiment,
The leaf spring 210 is disposed between the distal end of the pump body 100 in the insertion direction and the bottom of the recess 150a of the housing 150. As shown in the present embodiment, the cut portion of the fourth cylinder 71d and the male screw member 200 are provided. The leaf spring 220 may be arranged between the two.

Even with such a configuration, the male screw member 200
The force acting when the screw is tightened is balanced by the leaf spring 220, and the male screw member 20 is secured while maintaining a desired axial force.
The pump main body 100 can be reliably fixed to the housing 150 by the screw tightening of 0.

(Other Embodiments) In the above embodiment, the second and third cylinders 71b and 71c are divided into two members in a direction substantially perpendicular to the drive shaft 54. , And the third cylinders 71b and 71c can be formed by one member. However, the sealing member 8
In the case of 0, it is necessary to prevent the drive shaft 54 from rotating with this rotation even if it rotates. For this reason, as described above, the cross-sectional shape of the resin member 82 and the inner periphery of the third cylinder 71c are arc-shaped, but since the two members of the second cylinder 71b and the third cylinder 71c are used, the third cylinder 71c It is only necessary to form an arc-shaped recess from the end face of the first member, so that each member can be manufactured more easily than a single member. In the present embodiment, the seal member 80 is accommodated in the second and third cylinders 71b and 71c so that the seal member 80 does not contact the rotating parts of the rotary pumps 10 and 13. Therefore, it is possible to prevent the seal member 80 from being worn by each rotating part.

Further, the pump body 100 of the present embodiment
As described above, the first cylinder 71a, the first center plate 73a, the second cylinder 71b, the third cylinder 71c,
The second central plate 73b and the fourth cylinder 71d are sequentially stacked, and are integrated by welding the outer periphery of the overlapping portion. In such a case, each rotary pump 10, 1
In order to assemble the outer rotor 10 at the optimum position,
a, inner rotor 10b, center plates 73a, 73
b and the first to fourth cylinders 71a to 71d. However, the second, third
When the cylinders 71b and 71c are integrated, the rotary pumps 10 and 13 cannot be separately positioned. For this reason. It is difficult to align to the optimal position. Therefore, the second and third cylinders 71
By dividing into b and 71c, such a problem can be eliminated.

In the above embodiment, the stopper 213 and the C-ring 215 are disposed at the tip of the drive shaft 54, but only one of them may be provided. At this time, when the stopper 213 is eliminated, the C ring 215 comes into contact with the plate and plays a role as the stopper 213.

In the above embodiment, the housing 15
Male screw member 2 in female screw groove 150b formed in
Although the pump body 100 is fixed to the housing 150 by screwing 00, the pump body 100 may be fixed by another method, for example, by caulking the inner peripheral surface of the recess 150a.

[Brief description of the drawings]

FIG. 1 is a diagram showing a piping configuration of a brake device according to a first embodiment of the present invention.

FIG. 2 is a diagram showing a cross-sectional configuration near a pump body 100 of the brake device shown in FIG.

FIG. 3 is a sectional view taken along line AA of FIG. 2;

FIG. 4 is a diagram illustrating a cross-sectional configuration near a pump body of a brake device according to a second embodiment.

[Explanation of symbols]

100: pump body, 10a: outer rotor, 10b
... inner rotor, 10c ... gap, 54 ... drive shaft, 5
4a: long hole, 54b: key, 60, 62: suction port, 6
1, 63 ... discharge port, 61a, 63a ... annular groove, 61b,
63b: passage, 71a to 71d: first to fourth cylinders,
73a, 73b: central plate, 150a: concave portion, 15
0: housing, 151 to 154: conduit, 171, 17
2: seal member, 200: male screw part, 210: leaf spring,
213: Stopper.

Claims (12)

[Claims] An inner rotor (10b, 13b) having outer teeth formed on an outer periphery and an outer rotor (10a, 13a) formed with inner teeth on an inner periphery, wherein the inner teeth and the outer teeth are formed. A plurality of gaps (1
0c), a suction port (60, 62) for sucking brake fluid into the rotation section, and a discharge port (61, 63) for discharging the brake fluid from the rotation section. A plurality of rotary pumps (10, 13), and a pump body (100) configured to drive an inner rotor of each of the plurality of rotary pumps by one drive shaft (54); A vehicle brake device, wherein the drive shaft is disposed horizontally, and the discharge port is drawn out in a top direction. 2. The pump body according to claim 2, wherein each of the plurality of rotary pumps has a center plate (73a, 73b) having a hole for accommodating the rotating part, and a hole in which the drive shaft is fitted. Side plates (71a, 71b, 71c, 71) sandwiching the central plate from both sides
d), and a casing configured to accommodate the rotating portion, the casing comprising: a rotating portion side end face of the both side plates;
A first annular groove (61) formed so as to surround the drive shaft.
a, 63a) and seal members (171, 17) arranged to sandwich the inner rotor and the outer rotor in the first annular groove.
2) is provided, wherein the first annular groove is arranged such that when the seal member is disposed, the brake fluid extends in a longitudinal direction of the first annular groove through a gap in the first annular groove. The passages (61b, 63b) are formed in at least one of the side plates so as to be upwardly drawn from the uppermost portion of the first annular groove. The vehicle brake device according to claim 1, wherein the discharge port includes the first annular groove and the passage. 3. The first annular groove has a region configured such that the entire outer periphery of the first annular groove does not contact the seal member, and the brake fluid can flow through the region. The vehicular brake device according to claim 2, wherein: 4. The side plate, which is disposed between the plurality of rotary pumps, includes a plurality of members (71b, 71) divided in a direction substantially perpendicular to the drive shaft.
4. The method according to claim 2, wherein c) is performed.
The vehicle brake device according to any one of the preceding claims. 5. A recess (150) for accommodating the pump body.
a) having a housing (150) provided therein, wherein the pump body is inserted into the recess in the axial direction of the drive shaft and assembled to the housing; 5. A spring member (210) for pressing the pump body in a direction opposite to the insertion direction is disposed between a tip and a bottom of the recess. The vehicle brake device according to any one of the preceding claims. 6. A recess (150) for accommodating the pump body.
a) having a housing provided with the pump body, wherein the pump body is inserted into the recess in the axial direction of the drive shaft and is assembled to the housing; The vehicle brake device according to any one of claims 1 to 4, wherein a spring member (220) for pressing the pump body inserted into the recess in the insertion direction is disposed. 7. A screw member (200) is screwed and fixed to an entrance of a concave portion formed in the housing, and the pump member is pressed by the screw member in a direction of insertion into the concave portion. The vehicle brake device according to claim 5 or 6, wherein: 8. The pump body and the concave portion have a substantially cylindrical shape, and a portion of the inner peripheral surface of the concave portion from which the suction port and the discharge port are drawn out,
The vehicle brake device according to any one of claims 5 to 7, wherein a second annular groove (161 to 164) formed so as to surround a circumferential direction of the pump body. . 9. A motor having a holder (11b) having a hole and a motor (11) having a motor shaft (11a) at a center position of the hole of the holder. The motor is fixed to the formed surface via the holder, and the inner surface of the hole of the holder and the inner surface of the inlet of the hole of the side plate are both in contact with each other. The vehicle brake device according to any one of claims 5 to 8, wherein a bearing (180) that supports at least one of a motor shaft and the drive shaft is disposed. 10. A pipe (151 to 15) connected to each of the suction port and the discharge port is provided in the housing.
The vehicle brake device according to any one of claims 5 to 9, wherein 4) is formed, and the conduit is drawn out in a top direction. 11. A stopper (2) at the tip of the drive shaft.
13. The method according to claim 1, further comprising:
0. The vehicle brake device according to any one of 0. 12. The drive shaft is formed with a long hole (54a) whose longitudinal direction is the axial direction of the drive shaft, and a key (54b) is provided in the long hole. The vehicle brake device according to any one of claims 1 to 11, wherein the inner rotor is driven by the drive shaft by torque transmission by the motor.