JPH11117876A - Rotary pump and brake device using rotary pump - Google Patents

Abstract

PROBLEM TO BE SOLVED: To eliminate the leakage of fluid through tip gaps between an outer rotor and an inner rotor by reducing the tip gaps. SOLUTION: In this device, the outer periphery of an outer rotor 51 on the intake port 60 side is made to communicate with the intake port 60 through conduit passages 71b, 71c. Further, the outer periphery of the outer rotor 51 on the discharge port 61 side is made to communicate with the discharge port 61 through a conduit passage 71d. In this arrangement, the distance between the conduit passage 71b and the conduit passage 71b is shorter than that between the conduit passage 71c and the conduit passage 71d. That is, since the distance between the conduit passage 71b and 71d is shorter, the pressure exerted to the outer periphery of the outer rotor 51 becomes higher therebetween than that between the conduit passage 71c and 71d. Thus, the outer rotor produces such a force that an inner tooth part 51a holds an outer tooth part 52a, thereby making it possible to eliminate tip gaps.

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 a state in which the internal teeth and the external teeth mesh with each other, and a plurality of gaps are formed by the mutual 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. When the pump is driven, the center axis of the inner rotor is used as a drive shaft, and the inner rotor rotates through the drive shaft, whereby 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 of the gaps changes greatly during one rotation of the outer rotor and the inner rotor, so that oil is sucked in from the suction port and discharged from the discharge port.

When the pump is driven, the pressure of the discharge port (hereinafter, referred to as discharge pressure) is changed to the pressure of the suction port (hereinafter, referred to as discharge pressure).
(Referred to as suction pressure), a pressure difference is generated between the gap on the discharge port side and the gap on the suction port side. Due to this differential pressure, the outer rotor moves relatively to the inner rotor, and the outer rotor is strongly pressed against the casing, resulting in a problem that the durability of the pump is deteriorated.

[0005] To solve this problem, Japanese Patent Laid-Open No. 9-3 is disclosed.
34092. Specifically, by making the portion on the discharge port side of the outer periphery of the outer rotor communicate with the discharge port, the pressure inside and outside of the outer rotor on the discharge port side is made to be the discharge pressure and balanced, and further, the outer periphery of the outer rotor is The suction port side is communicated with the suction port, so that the pressure inside and outside the outer rotor on the suction port side is both suction pressure and balanced. This prevents the outer rotor from moving in the direction perpendicular to the center line, that is, prevents the outer rotor from being strongly pressed against the casing.

[0006]

Among the plurality of gaps formed by the inner rotor and the outer rotor meshing with each other, the portion having the largest volume is formed by a confined portion not communicating with any of the suction port and the discharge port. Has become. The confining portion holds the pressure difference between the suction pressure and the discharge pressure, and plays an important role in smoothly performing the suction and discharge operations by the pump.

However, in the above-described conventional method, the movement of the outer rotor in the direction perpendicular to the center line is restricted, but the movement of the outer rotor in the direction parallel to the center line is not restricted. For this reason, the gap between the inner teeth portion of the inner rotor and the outer teeth portion of the outer rotor that are in contact with each other at the closing portion is expanded by the pressure difference between the suction pressure and the discharge pressure. There is a problem that oil leakage occurs from the following (hereinafter referred to as tooth gap).

[0008] In view of the above, the present invention eliminates the tooth gap between the outer rotor and the inner rotor while preventing the outer rotor from being pressed against the casing, thereby eliminating fluid leakage from the tooth gap. A first object is to provide a rotary pump. It is a second object of the present invention to provide a brake device capable of performing a favorable braking operation by applying the rotary pump.

[0009]

In order to achieve the above object, the following technical means are employed. According to the first aspect of the present invention, the low pressure side conduction path (71b, 7
1c) and a high-pressure side conduction path (71d) for communicating the outer periphery of the outer rotor (51) on the discharge port (61) side with the discharge port (61) in the casing (50). The conduction paths (71b to 71d) are arranged such that the inner teeth (51a) forming the closing portion (53a) push the outer teeth (52a) forming the closing portion (53a) in the direction in which the outer rotor (51) is pressed. ) Is formed at a position where the position is moved.

The outer rotor (51) can be moved in a direction in which the inner teeth (51a) forming the closing part (53a) push the outer teeth (52a) forming the closing part (53a). In this case, the internal tooth portion (51a) and the external tooth portion (52a) are not spread even by the pressure difference between the suction port (60) and the discharge port (61). Thus, like this:
The formation position of the low-pressure side and high-pressure side conduction paths (71b to 71d) is changed to the internal tooth portion (51a) forming the closing portion (53a).
Are the internal teeth (52a) forming the confinement (53a)
If the outer rotor (51) can be moved in the direction in which the outer rotor (51) is moved in the direction in which the outer rotor (51) is pushed, the tooth gap between the outer rotor (51) and the inner rotor (52) can be eliminated, and fluid leakage from the tooth gap can be prevented. Can be prevented.

According to a second aspect of the present invention, the suction port (6
0), the suction port (60) itself is selected as a part having a pressure equivalent to the pressure of (0), and the low-pressure side conduction path (71b, 71) is selected.
c) the outer circumference of the outer rotor (51) and the suction port (60)
Can be configured by communicating the above. Further, as a specific position of the low-pressure side communication path (71b, 71c), when the suction port (60) communicates with a plurality of gaps, the low-pressure side communication path is the second position. 1
And the second conduction path (71c), the first conduction path (71b) is closed by the closing portion (5) of the plurality of voids to which the suction port (60) communicates.
3a) is formed at a position where the gap near the outer rotor (51) communicates with the outer periphery of the outer rotor (51), and the second conduction path (71c) is closed at the closed portion () of the plurality of gaps where the suction port (60) communicates. What is necessary is just to form in the position where the space | gap part remote from 53a) and the outer periphery of the outer rotor (51) communicate.

On the other hand, a specific high-pressure side communication path (71d)
As for the position of the discharge port (6),
In the case where 1) communicates with a plurality of gaps, the high-pressure-side conduction paths (71b, 71c) are close to the closing portion (53a) among the plurality of gaps with which the discharge port (61) communicates. What is necessary is just to form in the position where the outer periphery of the outer rotor (51) communicates.

According to the invention described in claim 5, the braking force generating means (4,
5) a main pipe (A) for transmitting the brake fluid pressure and an auxiliary pipe for supplying the brake fluid from the brake fluid pressure generating means (1 to 3) to the braking force generating means (4, 5) in order to increase the braking force. A brake device having a path (D), wherein the rotary pump according to any one of claims 1 to 4 directs the suction port (60) toward the brake fluid pressure generating means (1 to 3).
The discharge port (61) is provided in the auxiliary pipe (D) with the discharge port (61) facing the braking force generating means (4, 5).

In this brake device, the brake fluid pressure in the holding pipe becomes high due to the brake fluid pressure generated based on the pedaling force. Accordingly, the pressure difference between the pressure applied to the suction port (60) and the pressure applied to the discharge port (61) increases, so that the brake fluid easily leaks from the tooth gap in the rotary pump. However, since the rotary pump according to any one of claims 1 to 4 is provided, it is possible to suitably prevent the brake fluid from leaking from the tooth gap. This makes it possible to provide a brake device that can perform a favorable braking operation using the rotary pump.

In this brake device, the rotary pump sucks the brake fluid of the first brake fluid pressure from the brake fluid pressure generating means (1 to 3). It is possible to pressurize to the second brake fluid pressure larger than the first brake fluid pressure and discharge it to the braking force generating means (4, 5) side, and to apply to the braking force generating means (4, 5) by the rotary pump When the brake fluid pressure is higher than the first brake fluid pressure, the second brake fluid pressure on the braking force generating means (4, 5) side and the brake fluid pressure generating means (1 to 1)
It is also conceivable to provide a differential pressure holding means (22) for holding a differential pressure from the first brake fluid pressure on the 3) side.

As described above, the brake fluid pressure generating means (1 to 1)
A configuration is employed in which the pressure difference is maintained when the second brake fluid pressure in the braking force generating means (4, 5) is increased to be higher than the first brake fluid pressure generated in 3). In this case, high-pressure discharge by a rotary pump is necessary. However, as described above, the rotary pump can prevent leakage of brake fluid from the discharge port (61) to the suction port (60) during high-pressure discharge, and This is very effective because the efficiency can be improved.

[0017]

DETAILED DESCRIPTION OF THE PREFERRED EMBODIMENTS The embodiment shown in the drawings will be described below. FIG. 1 shows 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-wheel 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 the bush rod presses a master piston disposed on the master cylinder 3 so that the master cylinder 3 is pressed. Pressure develops. The brake pedal 1, the booster 2, and the master cylinder 3 correspond to a brake fluid pressure generating unit.

The master cylinder 3 is provided with a master reservoir 3a for supplying brake fluid into the master cylinder 3 or 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). The following description is
The right front wheel FR and the left rear wheel RL will be described.
The same applies to the left front wheel FL and the right rear wheel RR side, which are the piping systems described above, 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. Also,
In the pipe A2, the pipe A is branched into two, one of which is provided with a pressure increasing control valve 30 for controlling the pressure increase of the brake fluid pressure to the wheel cylinder 4, and the other is provided with a wheel cylinder. 5 is provided with a pressure increase control valve 31 for controlling the pressure increase of the brake fluid pressure.

Each of the pressure increase control valves 30 and 31 is configured as a two-position valve which can control a communication state and a cutoff state by an electronic control unit for an ABS (hereinafter referred to as an 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 increasing 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.

To reduce the pulsation of the brake fluid discharged from the rotary pump 10, an accumulator 12 is disposed on the discharge side of the rotary pump 10 in the pipeline C. And, between the reservoir 20 and the rotary pump 10,
Pipe (auxiliary pipe) to connect to master cylinder 3
D is provided, and the rotary pump 10 pumps the brake fluid in the pipeline A1 through the pipeline D and discharges the brake fluid to the pipeline A2, thereby increasing the wheel cylinder pressure in the wheel cylinders 4 and 5 from 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.

The pipe D is provided with a control valve 34, which is normally shut off during normal braking. At this time, the connection between the pipe C and the pipe D and the reservoir 2 are prevented from flowing back from the pipe C to the reservoir 20 by the hydraulic pressure transmitted from the pipe D.
A check valve 21 is provided between the zero points.

The control valve 40 is normally in a communication state. However, when the master cylinder pressure is lower than a predetermined pressure, when the wheel cylinders 4, 5 are suddenly braked, or when the TR
It is shut off at the time of C to maintain the differential pressure between the master cylinder side and the wheel cylinder side. Next, FIG. 2A shows a schematic diagram of the rotary pump 10, and FIG. 2B shows a cross-sectional view taken along the line AOB of FIG. 2A. First, FIG.
The structure of the rotary pump 10 will be described based on (a) and (b).

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.
Further, the outer rotor 51 has an inner tooth portion 51a on the inner periphery, and the inner rotor 52 has an outer tooth portion 52a on the outer periphery. The outer rotor 51 and the inner rotor 52 form a plurality of gaps 53 with their teeth, and mesh with each other at the mesh surface S. In addition, as can be seen from FIG. 2A, in the rotary pump 10 of the present embodiment, a gap 53 is formed by the inner teeth 51 a of the outer rotor 51 and the outer teeth 52 a of the inner rotor 52.
This is a multi-tooth trochoid type pump without a partition plate (crescent). Further, 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 on the meshing surface S.

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.

Also, 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 inner rotor 52 rotates around the point Y, and the outer rotor 51 It will rotate as an axis.

Further, assuming that a line passing through the points X and Y, which are the respective 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 gaps 53, the closed portion 53a having the largest volume is not communicated with either the suction port 60 or the discharge port 61. Pressure and discharge port 61
Is maintained at a pressure difference from the discharge pressure at The first side plate portion 71 is provided with conduction paths 71b and 71c that communicate the outer periphery of the outer rotor 51 and the suction port 60, and a conduction path 71d that communicates the outer periphery of the outer rotor 51 and the discharge port 61. I have. The conduction path 71b and the conduction path 71c are respectively disposed at positions about 45 degrees from the center line Z toward the suction port 60 around the point X which is the rotation axis of the outer rotor. The outer circumference of the outer rotor 51 between 71c is set to a low suction pressure. In addition, the conduction path 71
d is a plurality of voids 53 communicating with the discharge port 61,
The gap 53 closest to the confined portion 53a is formed so as to communicate with the outer periphery of the outer rotor 51.
Is disposed at a position of about 30 degrees from the center line Z toward the discharge port 61 with respect to the center.

Next, the operation of the brake device and the rotary pump 10 configured as described above will be described. However,
The operation of the brake device will be described only when the high pressure is applied to the suction port 60 side of the rotary pump 10.
The control valve 34 provided in the brake device is set to an appropriate communication state 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. You. 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, the volume of each of the gaps 53 changes to a large or small value during one rotation of the outer rotor 51 and the inner rotor 52, so that the brake fluid is sucked from the suction port 60 and the brake fluid is discharged from the discharge port 61 toward the pipeline A2. Spit the liquid. 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 the operation of the pump, particularly at the time of high-pressure discharge of the brake fluid to the discharge port 61, if the high-pressure brake fluid pressure is confined in the gap 53, the internal teeth 51a and the external teeth 52a
The gap between them is pushed apart, which may cause a tooth gap. In such a case, the brake fluid may leak from the tooth gap, and high pressure discharge may not be performed.

However, in the rotary pump 10, since the communication paths 71b to 71d are provided, it is possible to prevent the external teeth 51a and the internal teeth 51b from being pushed and expanded in the closing portion 53a. FIG. 3 shows a pressure distribution of the brake hydraulic pressure applied to the outer periphery of the outer rotor 51 of the rotary pump 10.
The reason why 1b cannot be spread will be described. In FIG. 3, the pressure distribution is indicated by oblique lines, and the radial length of the outer rotor 51 is represented as the magnitude of the pressure applied to the outer periphery of the outer rotor 51.

As described above, the conduction paths 71b, 71c
Are connected to the suction port 60, and thus the conduction paths 71b and 7
A suction pressure, that is, a low pressure, is provided between 1c and the conduction paths 71b, 71c. The conduction path 71d is connected to the discharge port 6
1, the discharge pressure, that is, the high pressure. Therefore, the highest pressure is applied to the portion of the outer periphery of the outer rotor 51 where the conduction path 71d is located, and the lowest pressure is applied between the conduction paths 71b and 71c.

Therefore, the conduction path 71d and the conduction path 71b
And between the conduction path 71d and the conduction path 71c, a pressure distribution having a predetermined pressure gradient from a portion where the highest pressure is applied to a portion where the lowest pressure is applied, that is, a pressure distribution as shown in FIG. Become. More specifically, since the distance between the conduction path 71d and the conduction path 71b is short,
During this time, a pressure gradient is applied such that a relatively high pressure is applied to the entire outer periphery of the outer rotor 51, and the conduction path 71d
Because the distance between the outer rotor 51 and the conduction path 71c is long, a pressure gradient is applied such that a relatively low pressure is applied to the entire outer periphery of the outer rotor 51 therebetween. Therefore, a higher pressure is applied to the upper part of the outer rotor 51 than to the lower part of the paper.

For this reason, a force acts on the outer rotor 51 so as to press the outer rotor 51 downward. For this reason,
In the closing portion 53a, the internal teeth 51a of the outer rotor 51 are pressed against the external teeth 52a of the inner rotor 52, and the internal teeth 51a are caused by a pressure difference between the suction pressure and the discharge pressure.
a and the external teeth 52a are not pushed apart. Thereby, it is possible to prevent the brake fluid from leaking due to the tooth gap.

The pressure balance of the rotary pump 10 will be examined. The gap 53 communicating with the suction port 60 has a low suction pressure, and the outer circumference of the outer rotor 51 between the conduction path 71b and the conduction path 71c also has a low suction pressure. On the other hand, the gap 53 communicating with the discharge port 61 has a high discharge pressure, and the outer periphery of the outer rotor 51 between the conduction path 71d and the conduction path 71b or the conduction path 71c also has a high pressure having the above-described predetermined gradient. It becomes high pressure and almost balances. Then, as described above, the outer rotor 51
Exerts such a force as to be pressed down on the paper surface.

Accordingly, in the closing portion 53a, the internal and external pressures of the outer rotor 51 are balanced while preventing the internal teeth 51a and the external teeth 52a from being spread, so that the pump can be smoothly driven. It has become.
As described above, since the pressure inside and outside the outer rotor 51 is balanced while preventing the brake fluid from leaking due to the tooth gap, the pump efficiency can be improved.

Also, in the brake device requiring high-pressure discharge as in the present embodiment, by applying the rotary pump 10, it is possible to prevent the brake fluid from leaking from the gap between the tooth tips, so that the brake operation is performed. Can be performed well. As described above, a force is exerted on the outer rotor 51 so as to be pressed down on the lower side of the sheet. However, the pressure applied to the upper portion of the outer rotor 51 and the pressure applied to the lower portion of the outer side of the sheet. Is not so large that the outer rotor 51 is strongly pressed against the center plate portion 73, so that the durability of the rotary pump 10 can be sufficiently improved by the force acting on the outer rotor 51.

In the present embodiment, the conduction paths 71b to 71b
By forming 1d at a predetermined position, the external teeth 51a and the internal teeth 52a in the closing portion are prevented from being expanded, but the positions of the conduction paths 71b to 71d are set to the positions shown in the present embodiment. The position is not limited, and any position may be used as long as a force is applied to the outer rotor 51 in the direction in which the inner teeth 51a of the outer rotor 51 presses the outer teeth 52a of the inner rotor 52 at the closing portion. .

Further, as shown in FIG. 2A, the conduction paths 71b to 71d are formed with substantially the same width, but the shapes of the conduction paths 71a to 71d are not limited to the above embodiment. For example, the conduction paths 71a to 71d may be formed so as to form a wide shape on the outer periphery of the outer rotor 51. Furthermore, in the present embodiment, the conduction path 7
1b and 71c are the outer periphery of the outer rotor 51 and the suction port 6;
0, and these conduction paths 71b,
Although the outer circumference of the outer rotor 51 is set at a low suction pressure by the 71c, the conduction paths 71b and 71c are
A similar effect can be obtained even when a portion having a low pressure similar to that described above, for example, a portion in which the low pressure reservoir or the like communicates with the outer periphery of the outer rotor 51. The conduction path 71d connects the outer circumference of the outer rotor 51 to the discharge port 61. The outer circumference of the outer rotor 51 is set to a high discharge pressure by the conduction path 71d.
The same effect can be obtained even if 1d is made to communicate a high pressure portion similar to that of the suction port 60 with the outer periphery of the outer rotor 51.

[Brief description of the drawings]

FIG. 1 is a schematic diagram of a brake device to which a rotary pump 10 is applied.

FIG. 2A is a schematic view of a rotary pump 10,
(B) is a sectional view taken along the line AOB in (a).

FIG. 3 is a schematic diagram showing a state of brake hydraulic pressure applied to the outer periphery of an outer rotor 10;

[Explanation of symbols]

Reference numeral 10: rotary pump, 11: motor, 50: casing, 51: outer rotor, 52: inner rotor, 5
Reference numeral 3 denotes a gap, 54 denotes a drive shaft, 60 denotes a suction port, 61 denotes a discharge port, 71, 72 ..., first and second side plates, 71a.
... Center hole, 71b-71c ... Conduction path.

Claims (7)

[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 so as to form a plurality of gaps (53) by meshing the internal teeth (51a) and the external teeth (52a), and the drive shaft (54). ), And an inlet (60) for sucking a fluid into the rotating parts (51, 52) and an outlet (61) for discharging the fluid from the rotating parts (51, 52). ), A casing (50) covering the rotating part, and the suction port (60) and the discharge port at a closed part (53a) having a maximum volume among the plurality of voids (53). (61) While maintaining the respective pressures, A rotary pump that sucks the fluid from the suction port (60) by the rotation of the turning part and discharges the fluid through the discharge port (61). The casing (50) includes the suction port (60). At least one low-pressure side conduction path (71b, 71c) that connects the outer periphery of the outer rotor (51) on the side with a portion having a pressure equal to the pressure of the suction port (60).
And at least one high-pressure side conduction path (71d) that communicates the outer periphery of the outer rotor (51) on the discharge port (61) side with a portion having a pressure equivalent to the pressure of the discharge port (61). The low-pressure side and high-pressure side conduction paths (71b to 71d) are formed with the internal teeth (51) forming the closing portion (53a).
a) pushes the outer rotor portion (51) in a direction in which the outer tooth portion (52a) forming the closing portion (53a) is pushed.
A rotary pump formed at a position for moving the rotary pump. 2. The low-voltage conduction path (71b, 71c).
The outer circumference of the outer rotor (51) communicates with the suction port (60). The high-pressure side conduction path (71d) is connected to the outer circumference of the outer rotor (51) and the discharge port (61). 2. The rotary pump according to claim 1, wherein the rotary pump is connected to the rotary pump. 3. The suction port (60) communicates with a plurality of voids forming a part of the plurality of voids (53), and the low-pressure-side conductive path includes a first conductive path (71b). ) And a second conduction path (71c), and the first conduction path (71b) is connected to the suction port (60).
Among the plurality of voids communicating with each other, the closed portion (53
a space close to a) and the outer periphery of the outer rotor (51) are formed in communication with each other, and the second conduction path (71c) is formed in the suction port (60).
Among the plurality of voids communicating with each other, the closed portion (53
3. The rotary pump according to claim 1, wherein the rotary pump is formed at a position where a gap far from a) communicates with an outer periphery of the outer rotor. 4. The discharge port (61) communicates with a plurality of voids forming a part of the plurality of voids (53), and the high-pressure side conduction path (71d) communicates with the discharge port (71). 61)
Among the plurality of voids communicating with each other, the closed portion (53
The rotary pump according to any one of claims 1 to 3, wherein a gap close to a) is formed at a position where the outer periphery of the outer rotor (51) communicates with the gap. 5. 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 (1 to 3) and transmitting the brake fluid pressure to the braking force generating means (4, 5); And an auxiliary pipe (D) for supplying brake fluid to the main pipe (A) side to increase the braking force generated by the braking force generating means (4, 5). In the brake device, the rotary pump according to any one of claims 1 to 4, wherein the suction port (60) faces the brake fluid pressure generating means (1 to 3), and the discharge port (61). Toward the braking force generating means (4, 5), and Brake system, characterized in that provided in D). 6. The rotary pump according to claim 1, wherein the rotary pump is configured to supply the brake fluid having a first brake fluid pressure to the brake fluid pressure generating means.
Side, and can be pressurized to a second brake fluid pressure greater than the first brake fluid pressure, and can be discharged to the braking force generating means (4, 5) side. Power generation means (4,
When the brake fluid pressure applied to 5) is higher than the first brake fluid pressure, the second brake fluid pressure on the braking force generating means (4, 5) side and the brake fluid pressure generating means ( The brake device according to claim 5, further comprising a differential pressure holding means (22) for holding a differential pressure between the first brake fluid pressure and the first to third brake fluid pressures. 7. An outer rotor (51) having inner teeth (51a) on the inner periphery, and an inner rotor (52) having outer teeth (52a) and rotating about a drive shaft (54). A rotating part, which is assembled so as to form a plurality of gaps (53) by meshing the internal teeth (51a) and the external teeth (52a), and the drive shaft (54). ), And an inlet (60) for sucking a fluid into the rotating parts (51, 52) and an outlet (61) for discharging the fluid from the rotating parts (51, 52). ), A casing (50) covering the rotating part, and the suction port (60) and the discharge port at a closed part (53a) having a maximum volume among the plurality of voids (53). (61) While maintaining the respective pressures, A rotary pump that sucks the fluid from the suction port (60) by the rotation of the turning part and discharges the fluid through the discharge port (61). The casing (50) includes the suction port (60). At least one low-pressure side conduction path (71b, 71c) that connects the outer periphery of the outer rotor (51) on the side with a portion having a pressure equal to the pressure of the suction port (60).
And at least one high-pressure side conduction path (71d) communicating the outer periphery of the outer rotor (51) on the discharge port (61) side and the discharge port (61) is formed. The high-pressure-side conduction paths (71b to 71d) are connected to the internal teeth (51) forming the confined portion (53a).
a) pushes the outer rotor portion (51) in a direction in which the outer tooth portion (52a) forming the closing portion (53a) is pushed.
A rotary pump formed at a position for moving the rotary pump.