JP2000179466A - Rotary pump and brake device provided with rotary pump - Google Patents

Abstract

PROBLEM TO BE SOLVED: To prevent an outer rotor and an inner rotor from being deviated in an axial direction of a driving shaft each other. SOLUTION: A seal member 100 (101) for sealing a high pressure side and a low pressure side in a gap between an axial end surface of an inner rotor 52 and an outer rotor and a casing 50 is provided. The seal member 100 (101) has wide portions 100A, 100B making coincident with a position of the inner rotor 52 and the outer rotor 51 in an axial direction of a driving shaft 54 at a portion different from a position through which closing portions 53a, 53b pass. Thus, a durability of a portion for sealing the closing portions 53a, 53b of the seal member 100 as a seal is enhanced by providing the wide portions making coincident with a position of the inner rotor 52 and the outer rotor 51 in an axial direction of the driving shaft 54 at a position different from the closing portions 53a, 53b requiring a seal.

Description

DETAILED DESCRIPTION OF THE INVENTION

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a rotary pump for sucking / discharging a fluid and a brake device using the rotary pump, and particularly suitable for an internal gear pump such as a trochoid pump.

[0002]

2. Description of the Related Art An internal gear type rotary pump such as a trochoid pump has an inner rotor having outer teeth on its outer periphery, an outer rotor having inner teeth on its inner periphery, and a combination of these outer and inner rotors. It is composed of a casing etc. to be stored. The inner rotor and the outer rotor are arranged in the casing in such a manner that the internal teeth and the external teeth mesh with each other, and a plurality of gaps are formed by these teeth.

[0003] Assuming that a line passing through both center axes of the inner rotor and the outer rotor is the center line of the pump, suction ports and discharge ports communicating with the plurality of gaps are provided on both sides of the center line. I have. At the time of driving the pump, the center axis of the inner rotor is used as a drive shaft, and the inner rotor rotates via this drive shaft, and accordingly, the outer rotor also rotates in the same direction due to the meshing of the external teeth and the internal teeth. At this time, the volume of each gap changes to a large or small value during one rotation of the outer rotor and the inner rotor, so that oil is sucked from the suction port and discharged from the discharge port.

[0004]

However, since the inner rotor and the outer rotor are configured to be able to move relative to each other in the axial direction of the drive shaft even if they are engaged in the rotational direction, The pump is driven in a state where the rotor and the outer rotor are displaced from each other in the axial direction of the drive shaft, and there is a problem that good pump performance cannot be obtained.

The present invention has been made in view of the above problems, and provides a rotary pump that prevents the outer rotor and the inner rotor from being mutually displaced in the axial direction of the drive shaft, and provides good pump performance. The purpose is to:

[0006]

By the way, conventionally, in a rotary pump, a pressure difference is generated between a high-pressure discharge port side and a low-pressure suction port side. There is a problem of oil leakage to the side.

For this reason, the present inventors, for example, as shown in FIG.
By disposing an annular seal member 200 (two-dot chain line in the figure) eccentric to the drive shaft 54 in the gap between the axial end surface of the first casing 1 and the casing 50, the seal member 200 discharges. It has been devised to separate the high pressure discharge port 61 side and the low pressure suction port 60 side so as to pass between the outlet 61 and the drive shaft 54.

When such a seal member 200 is provided, the seal member 200 presses the inner rotor 52 and the outer rotor 51 at the closing portions 53a and 53b located between the discharge port 61 and the suction port 60. Therefore, it is considered that the displacement between the inner rotor 52 and the outer rotor 51 can be suppressed.

However, the portion of the seal member 200 that covers the closing portions 53a and 53b is directed toward the low-pressure suction port 60 when the closing portions 53a and 53b communicate with the discharge port 61 to increase the pressure. The inner rotor 52 and the outer rotor 51 must be pressed at this portion to prevent the oil from leaking. The durability of the seal member 200 is degraded due to the wear caused by pressing the outer rotor 52 and the outer rotor 51.

Therefore, in order to achieve the above object, the following technical means are adopted.

[0011] In the first to seventh aspects of the present invention,
In a gap between the axial end surfaces of the inner rotor (52) and the outer rotor (51) and the casing (50), the space passes between the discharge port and the drive shaft and the first and second closing portions ( 53a, 53b), the inner rotor and the outer rotor are aligned in the axial direction of the drive shaft at a portion different from the portion that reaches the outer periphery of the outer rotor and passes through the first and second closing portions. Adjustment unit (100A, 101A, 100B, 101B)
(100, 101).

As described above, by providing the sealing means which passes between the discharge port and the drive shaft and extends to the outer periphery of the outer rotor through the first and second closing portions, the high pressure side and the low pressure side are separated. Can be sealed. Then, at a portion different from the first and second closing portions where the seal is required, an adjusting portion for matching the positions of the inner rotor and the outer rotor in the axial direction of the drive shaft is provided, so that It is possible to improve the durability of a portion for sealing the first and second closing portions as a seal.

Specifically, as set forth in claim 2, a central plate (73) having a hole for accommodating the rotating portion, and first and second side plates (7) sandwiching the central plate.
1, 72), the first and second side plates pass between the discharge port and the drive shaft, and pass through the first and second closing portions to form the outer rotor. Grooves (71b, 72b) extending from the inner rotor to the outer rotor are formed in a portion different from a portion reaching the outer periphery and passing through the first and second closing portions, and a sealing means is provided in the groove. Can be arranged.

According to the third aspect of the present invention, the sealing means includes a first sealing member (100a, 101a) which is made of an elastic body and is arranged on the bottom side of the groove.
A second seal member (100b, 101b) disposed on the opening side of the groove with respect to the first seal member, and the first seal member has an inner seal formed by the elastic force of the first seal member. It is characterized in that it comes into contact with the rotor and the outer rotor.

As described above, by pressing the second seal member with the first seal member made of an elastic body, the second seal member comes into contact with the inner rotor and the outer rotor, and the sealing function is provided. You can do it.

According to a fourth aspect of the present invention, the adjusting unit includes:
It can be configured by extending so as to overlap with a gap communicating with the discharge port or the suction port.

More specifically, in the seal member, the substantially annular ring portion of the seal member is arranged eccentrically with respect to the drive shaft, and the annular portion is partially formed. By making the width wider, it is possible to configure an adjusting portion that overlaps with a gap communicating with the discharge port or the suction port.

According to a seventh aspect of the present invention, an opening is formed in the adjusting portion, and a gap communicates with the outside of the adjusting portion through the opening. I have.

By forming the opening in the adjusting portion in this manner, the gap can be prevented from being completely covered.
Even if the adjusting portion is formed, the suction and discharge of the brake fluid can be performed when the gap changes in size.

The rotary pump according to the present invention is characterized in that the brake hydraulic pressure generating means (1 to 3)
Braking force generating means (4, 5)
A main line (A) for transmitting the brake fluid to the main line and an auxiliary line (D) for supplying the brake fluid to the main line side in order to increase the braking force generated by the braking force generating means. The brake fluid on the side of the brake fluid pressure generating means can be sucked through the pipeline, and the discharge port is arranged so that the brake fluid can be discharged toward the braking force generating means through the main pipeline.

[0021]

DETAILED DESCRIPTION OF THE PREFERRED EMBODIMENTS The embodiment shown in the drawings will be described below.

FIG. 1 is a schematic diagram of a brake pipe of a brake device to which a trochoid pump is applied as a rotary pump. Hereinafter, a basic configuration of the brake device will be described with reference to FIG. In this example, an example in which the brake device according to the present invention is applied to a vehicle that forms a hydraulic circuit of X pipes including a pipe system of right front wheel-left rear wheel and left front wheel-right rear wheel in a front wheel drive four-wheeled vehicle explain.

As shown in FIG. 1, the brake pedal 1 is connected to a booster 2, and the booster 2 boosts the brake depression 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 a brake fluid pressure generating unit.

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.

The brake device has a pipe (main pipe) A connected to the master cylinder 3, and this pipe A is provided with a proportional control valve (PV: proportioning valve) 22. And this proportional control valve 2
2, the pipe A is divided into two parts. That is, the pipe A is divided into a pipe A1 that receives the master cylinder pressure from the master cylinder 3 to the proportional control valve 22, and a pipe A2 from the proportional control valve 22 to each wheel cylinder 4, 5.

The proportional control valve 22 normally has the function of transmitting the reference pressure of the brake fluid to the downstream side at a predetermined damping ratio when the brake fluid flows in the forward direction. Then, as shown in FIG. 1, by connecting the proportional control valve 22 in reverse, the pipe line A2 side becomes the reference pressure.

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

The pressure increase control valves 30 and 31 are configured as two-position valves that can control the communication and cutoff states by an ABS electronic control unit (hereinafter referred to as ECU). When the two-position valve is controlled to be in communication, the master cylinder pressure or the brake fluid pressure due to the discharge of the brake fluid from the pump can be applied to each wheel cylinder 4,5.

When the ABS is not being executed, the first and second pressure increase control valves 3 and 4 are operated during normal braking.
0 and 31 are controlled to be always in communication. The pressure increase control valves 30 and 31 have safety valves 30a and 31a, respectively.
Are provided in parallel, and when the brake pedal is stopped, A
When the BS control ends, the wheel cylinder 4,
The brake fluid is removed from the fifth side.

The first and second pressure increase control valves 30 and 31
A pipe B connecting the pipe A between the wheel cylinders 4 and 5 and the reservoir hole 20a of the reservoir 20 has A
Pressure-reducing control valves 32 and 33, which can control the connection / disconnection state by the ECU for BS, are provided respectively. These pressure reduction control valves 32 and 33 are in the normal brake state (ABS
(At the time of non-operation), it is always in a cutoff state.

The proportional control valve 22 and the pressure increasing control valve 3 in the line A
The rotary pump 10 is disposed between the safety valves 10a and 10b in a pipe C connecting the reservoirs 0 and 31 and the reservoir hole 20a of the reservoir 20. Further, a motor 11 is connected to the rotary pump 10, and the rotary pump 10 is driven by the motor 11. A detailed description of the rotary pump 10 will be described later.

In order to reduce the pulsation of the brake fluid discharged from the rotary pump 10, a damper 12 is provided on the discharge side of the rotary pump 10 in the pipeline C. A pipe (auxiliary pipe) D is provided to connect between the reservoir 20 and the rotary pump 10 and the master cylinder 3, and the rotary pump 10 is connected to the pipe D via the pipe D. By pumping the brake fluid of A1 and discharging it to the pipeline A2, the wheel cylinder pressure in the wheel cylinders 4, 5 is made higher than the master cylinder pressure to increase the wheel braking force. The proportional control valve 22 holds the pressure difference between the master cylinder pressure and the wheel cylinder pressure at this time.

A control valve 34 is provided in the pipe D, and the control valve 34 is always shut off during normal braking.

At this time, a check valve 21 is provided between the reservoir 20 and the connection between the conduits C and D so that the hydraulic pressure transmitted from the conduit D at this time does not cause a backflow from the conduit C to the reservoir 20. Are arranged.

The control valve 40 is a two-position valve which is normally in a communicating state. The control valve 40 is closed when the master cylinder pressure is lower than a predetermined pressure, when the wheel cylinders 4 and 5 are suddenly braked, or when the TRC is performed. The differential pressure between the master cylinder side and the wheel cylinder side is maintained.

Next, FIG. 2 (a) shows a schematic view of the rotary pump 10, and FIG. 2 (b) shows a sectional view taken along the line AA of FIG. 2 (a). First, the structure of the rotary pump 10 will be described with reference to FIGS.

In the rotor chamber 50a of the casing 50 of the rotary pump 10, an outer rotor 51 and an inner rotor 52 are assembled with their central axes (points X and Y in the figure) eccentric. It is stored.
The outer rotor 51 has internal teeth 51a on the inner periphery, and the inner rotor 52 has external teeth 52a on the outer periphery. The outer rotor 51 and the inner rotor 52 are meshed with each other by forming a plurality of gaps 53 by the teeth 51a and 52a of each other. Note that FIG.
As can be seen from (a), the rotary pump 1 of the present embodiment
Numeral 0 is a multi-tooth trochoid type pump without a partition plate (crescent) in which a gap 53 is formed by the internal teeth 51a of the outer rotor 51 and the external teeth 52a of the inner rotor 52. In order to transmit the rotational torque of the inner rotor 52, the inner rotor 52 and the outer rotor 51 have a plurality of contact points.

As shown in FIG. 2B, the casing 50 includes a first side plate portion 71 and a second side plate portion 72 arranged so as to sandwich the rotors 51 and 52 from both sides. A central plate portion 73 is provided between the first and second side plate portions 71 and 72 and has a hole for accommodating the outer rotor 51 and the inner rotor 52. It is formed.

The first and second side plates 71,
Central holes 71a and 72a communicating with the inside of the rotor chamber 50a are formed at the center of the central hole 72.
The drive shaft 54 disposed on the inner rotor 52 is fitted into the shafts a and 72a. The outer rotor 51 and the inner rotor 52 are rotatably disposed in the hole of the central plate portion 73. In other words, the rotating part composed of the outer rotor 51 and the inner rotor 52 is rotatably incorporated in the rotor chamber 50a of the casing 50, the outer rotor 51 rotates about the point X, and the inner rotor 52 It will rotate as an axis.

Further, assuming that a line passing through points X and Y, which are rotation axes of the outer rotor 51 and the inner rotor 52, is the center line Z of the rotary pump 10, the center line of the first side plate portion 71 A suction port 60 and a discharge port 61 communicating with the rotor chamber 50a are formed on the left and right sides of Z. The suction port 60 and the discharge port 61 are provided at positions communicating with the plurality of gaps 53. And
Through the suction port 60, the brake fluid from the outside is
The brake fluid in the gap 53 can be discharged to the outside through the discharge port 61.

Of the plurality of voids 53, the closed portion 53 a having the largest volume and the closed portion 53 b having the smallest volume do not communicate with either the suction port 60 or the discharge port 61. The closing portions 53a, 53
b holds the differential pressure between the suction pressure at the suction port 60 and the discharge pressure at the discharge port 61.

The first side plate portion 71 has a conduction path 73 a for communicating the outer periphery of the outer rotor 51 with the suction port 60, and further has the outer periphery of the outer rotor 51 and the discharge port 61.
Are provided with conduction paths 73b and 73c that communicate with. The conduction path 73a is provided at a position about 90 degrees from the center line Z toward the suction port 60 with respect to a point X serving as the rotation axis of the outer rotor 51. Also, the conduction path 73b
Is formed so as to communicate with the gap 53 closest to the confined portion 53a and the outer periphery of the outer rotor 51 among a plurality of gaps 53 communicating with the discharge port 61.
The conduction path 73 c is formed so as to communicate the gap 53 closest to the closed portion 53 b and the outer periphery of the outer rotor 51 among the plurality of gaps 53 communicating with the discharge port 61. The conduction path 73b and the conduction path 73
c is a distance from the center line Z about the point X to the discharge port 6.
It is arranged at a position of about 22.5 degrees in one direction.

The suction port 60 extends from the center line Z about the point X, which is the rotation axis of the outer rotor 51, on the wall surface of the center plate 73 forming the hole of the center plate 73.
A concave portion 73d and a concave portion 73e are formed at approximately 45 degrees in the direction, respectively. Seal members 80 and 81 for suppressing the flow of brake fluid on the outer periphery of the outer rotor 51 are formed in the concave portions 73 and 73e. Provided. Specifically, the sealing members 80 and 81
1b and the conduction path 71d, and seals a portion where the brake fluid pressure becomes low and a portion where the brake fluid pressure becomes high on the outer periphery of the outer rotor 51.

The sealing member 80 includes a rubber member 80a having a substantially cylindrical shape and a resin member 8 made of Teflon having a rectangular parallelepiped shape.
0b. Then, the resin member 80b is pushed by the rubber member 80a, and the outer rotor 51 is pressed.
It comes in contact with. That is, since a slight error occurs in the size of the outer rotor 51 due to a manufacturing error or the like, the error can be absorbed by the rubber member 80a having elasticity.

The width of the resin member 80b is such that a gap is formed to some extent when the resin member 80b is disposed in the concave portion 73d. That is, the width of the resin member 80b is
When the resin member 80b is formed to have a width equal to the width of 3d, the resin member 80b is formed by the flow of the brake fluid pressure when the pump is driven.
Since it becomes difficult to come out when it enters the inside, the resin member 80b is formed to have a size such that a gap is slightly opened, so that the brake fluid enters the upper portion of the resin member 80b, and the pressure of the brake fluid causes the resin to enter. The member 80b is made to easily come out of the recess 73d. Since the configuration of the seal member 81 is the same as that of the seal member 80, the description is omitted.

Further, as shown in FIG. 2B, the first and second side plate portions 71 and 72 have groove portions 71.
b, 72b are formed. These grooves 71b, 72b
Is a drive shaft 5 as shown by a two-dot chain line in FIG.
4 and has a configuration in which the groove width is widened in a predetermined region. In particular,
The centers of the grooves 71b and 72b are eccentric to the suction port 60 side (left side in the drawing) with respect to the axis center of the drive shaft 54.

As a result, the grooves 71b and 72b pass between the discharge port 61 and the drive shaft 54, and are closed.
The arrangement is such that the sealing member 53b and the sealing members 80 and 81 pass through the portion sealing the outer rotor 51.

The shaft of the drive shaft 54 and the grooves 71b, 7
Assuming a line connecting the center of 2b and the groove 71 at a position where the line intersects the suction port 60 or the discharge port 61,
b and 72b are an inner rotor 51 and an outer rotor 52.
The groove width is made large so as to overlap with both. In addition, the groove width of the groove portions 71b and 72b is also increased in a portion overlapping with the closing portions 53a and 53b.

In the grooves 71b, 72b having such a structure, seal members 100, 101 having the same shape as the shapes of the grooves 71b, 72b are arranged. FIG. 3 is a schematic view of the seal members 100 and 101.
As shown in FIG. 3, the sealing members 100 and 101
A predetermined region of the annular member is formed to be wide.

Wide portions 100A, 101 formed wide
A is configured to overlap the outer rotor 51 and the inner rotor 52 at the position where the discharge port 61 is formed, and the wide portions 100B and 101B
It is configured to overlap the outer rotor 51 and the inner rotor 52 at the position where 0 is formed.
These wide portions 100A, 101A and wide portion 100B,
101B plays a role of suppressing the axial displacement between the outer rotor 51 and the inner rotor 52. The wide portions 100A and 101A and the wide portions 100B and 1
01B, that is, the area where the discharge port 61 and the suction port 60 are formed are areas that do not need to be sealed. These wide portions 100A and 101A and the wide portions 100B and 101B are The inner rotor 52 is disposed only for suppressing the axial displacement of the inner rotor 52.

The wide portions 100C and 101C and the wide portions 100D and 101D are configured to have a width capable of completely covering the closing portions 53a and 53b, respectively, and mainly include the closing portions 53a and 53b. It acts as a seal to prevent leakage of brake fluid inside. The wide portions 100C and 101C and the wide portion 100C
D and 101D also play a role in eliminating axial displacement of the outer rotor 51 and the inner rotor 52,
00A and 101A and the wide portions 100B and 101B play their roles.
It is not necessary to hold down the outer rotor 51 and the inner rotor 52 with 0C, 101C and the wide portions 100D, 101D.

The seal members 100 and 101 are composed of elastic members 100a and 101a made of an elastic body such as rubber and resin members 100b and 101b made of resin. The resin members 100b and 101b are formed of the inner rotor 52, the outer rotor 51, and the center plate 73.
And the resin members 100b and 101b
It is configured to be pressed by elastic members 100a and 101a disposed on the bottom side of the grooves 71b and 72b to perform a sealing function.

The sealing member 100 thus arranged,
101, the axial end faces of the inner rotor 52 and the outer rotor 51 and the first and second side plate portions 7
In the gap between 1 and 72, the high pressure discharge port 61
In addition, the gap between the low-pressure drive shaft 54 and the inner rotor 52 and the suction port 60 can be sealed.

In order to seal a high-pressure portion and a low-pressure portion in a gap between the axial end surfaces of the inner rotor 52 and the outer rotor 51 and the first and second side plate portions 71 and 72, Sealing member 100,
101 is between the discharge port 61 and the drive shaft 54 and the discharge port 6
1 and the suction port 60, and needs to reach the outer periphery of the outer rotor 51. On the other hand, in the present embodiment, the seal members 100, 101
Of these, the area from the seal member 80 to the seal member 81 after passing between the drive shaft 54 and the discharge port 61 is the area required to seal the high-pressure part and the low-pressure part. In other words, the portions in contact with the inner rotor 52 and the outer rotor 51 in other areas where no seal is required are negligibly small. Therefore, the contact resistance of the seal members 100 and 101 can be reduced, and the mechanical loss can be reduced.

Further, as described above, the wide portion 100
A, 101A and the wide portions 100B, 101B can eliminate axial displacement of the outer rotor 51 and the inner rotor 52. And, as described above, the wide portions 100A, 10A,
1A and the wide portions 100B and 101B serve to eliminate the axial displacement of the outer rotor 51 and the inner rotor 52.
Wear of the 1C and the wide portions 100D and 101D can be reduced. Thus, it is possible to suppress a decrease in the sealing function of the wide portions 100C and 101C and the wide portions 100D and 101D.

Openings are formed in the wide portions 100A and 101A and the wide portions 100B and 101B, and the wide portions 100A and 101A and the wide portions 100B and 101B are formed.
Does not cover any of the plurality of voids 53. This is because the gap 53 performs suction / discharge of the brake fluid according to a change in the size, and therefore it is preferable that the gap 53 be connected to the suction port 60 or the discharge port 61. The portion 53 is configured to be capable of sucking and discharging the brake fluid.

Next, the operation of the brake device and the rotary pump 10 configured as described above will be described.

The control valve 34 provided in the brake device is
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, the communication state is appropriately set. Then, the high-pressure master cylinder pressure generated by depressing the brake pedal 1 through the pipeline D is applied to the rotary pump 10.

On the other hand, the rotary pump 10 drives the inner rotor 5 according to the rotation of the drive shaft 54 by driving the motor 11.
2 rotates and the internal teeth 51a and the external teeth 5
The outer rotor 51 also rotates in the same direction due to the engagement of 2a. At this time, while the outer rotor 51 and the inner rotor 52 make one rotation, the volume of each of the gap portions 53 changes in size, so that the brake fluid is sucked from the suction port 60 and is directed from the discharge port 61 toward the pipeline A2. Exhale the brake fluid. The wheel cylinder pressure is increased by the discharged brake fluid.

As described above, the rotary pump 10 performs a basic pump operation in which the brake fluid is sucked from the suction port 60 and the brake fluid is discharged from the discharge port 61 by the rotation of the rotors 51 and 52. Can be.

During this pump operation, the suction port 60 of the outer periphery of the outer rotor 51 is set to the suction pressure by the brake fluid sucked through the conduction path 73a, and the discharge port 61 of the outer periphery of the outer rotor 51 is set to the conduction path. 7
The discharge pressure is set by the brake fluid sucked through 3b and 73c. Therefore, a low-pressure portion and a high-pressure portion are generated on the outer periphery of the outer rotor 51. The gap between the axial end faces of the inner rotor 52 and the outer rotor 51 and the first and second side plate portions 71 and 72 is also reduced by the gap between the low-pressure discharge port 60 and the drive shaft 54 and the inner rotor 52. And a high-pressure discharge port 61, a low-pressure portion and a high-pressure portion are generated.

However, as described above, since the low-pressure portion and the high-pressure portion on the outer periphery of the outer rotor 51 are sealed and separated by the sealing members 80 and 81,
No oil leaks from the high pressure portion on the discharge port 61 side to the low pressure portion on the suction port 50 side through the outer periphery of the outer rotor 51. Further, the seal members 100 and 101 seal the low-pressure portion and the high-pressure portion of the gap between the axial end surfaces of the inner rotor 52 and the outer rotor 51 and the first and second side plate portions 71 and 72. Therefore, no oil leaks from the high-pressure part to the low-pressure part. In FIG. 2, the sealing members 100 and 101 are used.
Is shown so as not to contact the outer rotor 51 and the inner rotor 52, but as the discharge port 61 becomes high pressure, the seal members 100 and 101 bend, and completely contact the outer rotor 51 and the inner rotor 52 to perform the sealing function. Fulfill.

Further, the axial displacement of the outer rotor 51 and the inner rotor 52 is made uniform by the wide portions 100A, 101A and the wide portions 100B, 101B.
Good pump performance is obtained. The wide portions 100A, 101A and the wide portions 100B, 101B, which do not need to serve as seals, eliminate the axial displacement of the outer rotor 51 and the inner rotor 52. 101C
In addition, wear of the wide portions 100D and 101D can be reduced.

Since the seal members 100 and 101 are formed so as to pass through the seal members 80 and 81,
Since there is no gap between the seal members 100 and 101 and the seal members 80 and 81, no oil leaks from between the gaps.

Further, due to the seal members 80 and 81, the pressure on the suction port 60 side of the outer circumference of the outer rotor 51 is reduced to the same pressure as the gap 53 communicating with the suction port 60, and the outer circumference of the outer rotor 51 is reduced. Outlet 61 of
The side has a high pressure, and has the same pressure as the gap 53 communicating with the discharge port 61. Therefore, the pressure balance between the inside and the outside of the outer rotor 51 is maintained, and the pump can be driven stably.

As described above, the wide portions 100C and 101C and the wide portions 100D and 101D serving as the sealing function are provided.
In addition, the wide portions 100A and 101A and the wide portions 100B and 101B that do not need to play the role of the sealing function serve to eliminate the axial displacement of the outer rotor 51 and the inner rotor 52. , 101C and the wide portions 100D, 101D as seals.

(Second Embodiment) In the present embodiment, the structure of the seal members 100 and 101 is changed from that of the first embodiment. FIG. 4 is an enlarged cross-sectional view of the seal member 100 according to the present embodiment. Note that the configuration of the seal member 101 is the same as that of the seal member 100, and a description thereof will be omitted.

In this embodiment, as shown in FIG.
The size of the elastic member 100a is smaller than the seal member 100 (see FIG. 2) in the embodiment, and the resin member 100c is disposed on the inner peripheral side of the elastic member 100a.

Thus, the area where the resin member 100b is pressed by the elastic member 100a can be reduced. For this reason, the resin member 100b is
2 and the area for pressing the outer rotor 51 are reduced, the contact resistance by the seal member 100 can be reduced, and the mechanical loss can be further reduced.

The resin member 100c and the resin member 1
00a is the distance between the first and second side plates 7
1, 72 and outer rotor 51 or inner rotor 52
Is smaller than the interval S2.

By the way, the outer rotor 51 and the inner rotor 52 move in the axial direction due to the production intersection of the elastic members 100a and 101a and the resin members 100b and 101b, and the axial force applied to the outer rotor 51 and the inner rotor 52. There are cases.

In such a case, the elastic members 100a, 10a
Since the first rotor 1a expands and contracts, the axial movement of the outer rotor 51 and the inner rotor 52 cannot be completely suppressed, and the outer rotor 51 and the inner rotor 52 both move in the axial direction, and the first and second side plates 71 move. , 72, which may cause a large contact resistance.

For this reason, in this embodiment, the resin member 10
0c, 101c, the resin members 100b, 101b
Restricts the outer rotor 51 and the inner rotor 52 from moving beyond the distance S1 between the first and second side plates 71 and 72 and the outer rotor 51 or the inner rotor 52. 7
1, 72 are not contacted. As a result, the outer rotor 51 and the inner rotor 52
Can be prevented from increasing the contact resistance due to contact with the side plates 71, 72, and mechanical loss can be reduced.

The sealing member 10 having the same configuration
Also for 1, the contact resistance by the seal member 101 can be reduced. Thereby, the mechanical loss can be further reduced.

In this embodiment, the resin member 100c
Is configured as a single member, but the resin member 100b
And may be formed integrally with the first and second side plate portions 71 and 72.

(Third Embodiment) The configuration of the seal members 100 and 101 may be changed from the first and second embodiments as in the present embodiment.

In the first and second embodiments, the wide portion 100
A and 101A have a width that can reach only the inside of the outer periphery of the outer rotor 51, but the width may be further increased so as to reach the center plate 73. By doing so, the sealing member 100,
101 is installed, the sealing member 10
The deflection of 0 and 101 can be reduced.

(Other Embodiment) In the second embodiment, the elastic members 100a, 100b are formed by the resin members 100c, 101c.
Although it has been shown that the pressing force by 101a is reduced, the resin members 100c, 101c and the elastic members 100a, 10a
By adjusting the shape of 1a, it is also possible to adjust the position to be strongly sealed. That is, the elastic member 1
At positions where the first and second elastic members 100a and 101a are disposed, the brake fluid pressure strongly presses the resin members 100c and 101c to perform sealing.
By adjusting the shapes of c and 101c, it is possible to adjust the position to be strongly sealed.

Here, consider the brake fluid pressure inside the closing portion 53a. The gap 53 is provided with the suction port 60.
It moves from the side and becomes the closing portion 53a. At this time, the brake fluid pressure inside the closing portion 53a is low. Thereafter, when the gap 53 moves further, the gap 53 communicates with the discharge port 61, so that the pressure of the brake fluid inside the gap 53 increases instantaneously.

For this reason, regarding the closing portion 53a,
The position at the moment when the high pressure side is reached is a position for distinguishing between the high pressure side and the low pressure side.
a and 101a may be arranged.

However, a change in the rotation behavior of the rotary pump 10 and a production intersection occur, so that it is not always easy to distinguish between the high-pressure side and the low-pressure side of the confined portion 53a. For this reason, the average value of the brake fluid pressure during the rotation of the rotary pump 10 may be determined, and the optimal position may be sealed based on the average value. For example, a position where the average value matches the intermediate value between the high pressure and the low pressure may be sealed.

The wide portions 100A and 101A and the wide portions 100B and 101B are not limited to the positions in the above-described embodiment but may be formed in other positions as long as they do not need to serve as a seal.

Further, as shown in FIG. 5, the seal member 100 may be arranged only on one side of the first side plate 71 side. At this time, due to the elasticity of the O-ring 100a of the seal member 100, the seal member 80b is pushed by the resin member 100b so that the seal member 100b comes into contact with the inner rotor 52 and the outer rotor 51, whereby the inner rotor 52 and the outer rotor 51 are pressed. Is moved toward the second side plate 72, the gap between the inner rotor 52 and the outer rotor 51 and the second side plate 72 is reduced as much as possible. Therefore, the inner rotor 52 and the outer rotor 5 are also provided on the second side plate 72 on the side where the seal member 100 does not exist.
The gap between the first and second side plates 72 is on the order of several microns, and substantially the same sealing performance as when the sealing member 101 described in the above-described embodiment (for example, FIG. 2) is present. With the inner rotor 52
The displacement of the outer rotor 51 in the axial direction is substantially eliminated.

[Brief description of the drawings]

FIG. 1 is a pipeline configuration diagram of a brake device including a rotary pump according to an embodiment of the present invention.

FIG. 2 is a diagram showing a specific configuration of the rotary pump in FIG.

FIG. 3 is a schematic view of a seal member 100 (101) shown in FIG.

FIG. 4 is an enlarged view of a seal member according to a second embodiment.

FIG. 5 is a diagram showing a cross-sectional configuration of a rotary pump according to another embodiment.

FIG. 6 is a diagram for explaining a configuration of a rotary pump according to studies by the present inventors.

[Explanation of symbols]

51: outer rotor, 51a: internal teeth, 52: inner rotor, 52a: external teeth, 53: gap, 53a, 5
3b: closing portion, 54: drive shaft, 60: suction port, 61
... Discharge port, 71 ... First side plate, 72 ... Second side plate, 71a, 72a ... Center hole, 71b, 7
2b: groove, 73: central plate, 73a, 73b, 7
3c: communication passage, 80, 81: seal member, 100, 1
01: seal member, 100a, 101a: elastic member, 1
00b, 101b: resin member, 100c, 101c: resin member. 100A, 101A ... wide part, 100B, 10
1B: Wide part.

Continuing from the front page (72) Inventor Taku Sato 1-1-1, Showa-cho, Kariya-shi, Aichi, Japan Denso Co., Ltd. 72) Inventor Hiroyuki Shinkai 1-1-1, Showa-cho, Kariya-shi, Aichi Prefecture, Denso Corporation (72) Inventor Toshiya Morikawa 1-1-1, Showa-cho, Kariya-shi, Aichi Prefecture, Denso Corporation

Claims (8)

[Claims] 1. An outer rotor (51) having an inner tooth portion (51a) on an inner periphery, and an inner rotor (52) having an outer tooth portion (52a) and rotating about a drive shaft (54). A rotating part, which is assembled by engaging the internal tooth part and the external tooth part to form a plurality of voids (53); and an opening (71a, 72a) into which the drive shaft is fitted. And a suction port (60) for sucking fluid into the rotating part.
And a discharge port (61) for discharging the fluid from the rotating part.
A casing (50) that covers the rotating part; a first confinement part (53a) having a maximum volume and a second confinement part having a minimum volume among the plurality of gaps; (53b) a rotary pump that sucks the fluid from the suction port by the rotational motion of the rotating unit and discharges the fluid through the discharge port while maintaining the pressure difference between the suction port and the discharge port at (53b). In the gap between the axial end faces of the inner rotor and the outer rotor, and the casing, the gap passes between the discharge port and the drive shaft, and passes through the first and second closing portions. At a position different from a portion that reaches the outer periphery of the outer rotor and passes through the first and second closing portions, the position of the inner rotor and the outer rotor in the axial direction of the drive shaft. Adjustment unit to match (100A, 101A, 100B, 101B)
The sealing means (100, 101) is provided, wherein the sealing means communicates through the gap with the outer periphery of the outer rotor located on the discharge port side and the gap communicating with the discharge port, A rotary pump having a shape in which a space between a drive shaft and the inner rotor and the gap communicating with the suction port communicate with each other. 2. A central plate (73) having a hole for accommodating the rotating part.
And holes (71a, 72a) into which the drive shafts are fitted,
First and second side plates (71, 72) sandwiching the center plate, wherein the first and second side plates pass between the discharge port and the drive shaft, The outer rotor or the outer rotor or a part that passes through the first and second confined portions and reaches the outer periphery of the outer rotor and is different from a part that passes through the first and second confined parts. A groove (71b,
72. The rotary pump according to claim 1, wherein the sealing means is arranged in the groove. 3. The first sealing member (100a, 101a), which is formed of an elastic body and is disposed on the bottom side of the groove, and the sealing member is formed of a sealing member. A second seal member (100b, 101b) arranged on the opening side, and the first seal member contacts the inner rotor and the outer rotor by the elastic force of the first seal member. 3. The method according to claim 2, wherein
2. The rotary pump according to 1. 4. The air conditioner according to claim 1, wherein the adjusting portion extends so as to overlap with the gap communicating with the discharge port or the suction port. The rotary pump according to any one of the first to third aspects. 5. The seal member has a substantially annular annular portion, and the annular portion is arranged eccentrically with respect to the drive shaft. 4. The method according to claim 1, wherein the annular portion is partially widened so as to overlap with the gap communicating with the discharge port or the suction port. A rotary pump according to any one of the preceding claims. 6. The rotary pump according to claim 1, wherein a plurality of the adjusting portions are formed, and are arranged at symmetrical positions around the drive shaft. . 7. The adjusting section has an opening formed therein, and the gap communicates with the outside of the adjusting section through the opening. The rotary pump according to any one of the above. 8. A brake fluid pressure generating means (1 to 3) for generating a brake fluid pressure based on a pedaling force, and a braking force generating means (4, 5) for generating a braking force on a wheel based on the brake fluid pressure. A main line (A) connected to the brake fluid pressure generating means and transmitting the brake fluid pressure to the braking force generating means; and a main pipeline (A) connected to the brake fluid pressure generating means to generate the braking force. An auxiliary pipeline for supplying a brake fluid to the main pipeline side to increase a braking force, wherein the rotary pump according to any one of claims 1 to 7, wherein the suction port is provided through the auxiliary pipeline. The rotation is characterized in that the brake fluid on the side of the brake fluid pressure generating means can be sucked, and the discharge port is arranged so as to be able to discharge the brake fluid toward the braking force generating means through the main conduit. Brake device equipped with a pump.