JPH10299671A - Rotary pump and brake device provided with rotary pump - Google Patents

Abstract

PROBLEM TO BE SOLVED: To prevent an inconvenience that a contact part between an outer rotor and an inner rotor opens and a fluid flows reversely from a delivery port side to a suction port side. SOLUTION: A device is structured so that a distance L from the end of a suction port 60 to the end of a delivery port 61 in the rotating direction of an inner rotor 52 (also the rotating direction of an outer rotor 51) is set larger than a distance equivalent to two teeth. Also it is set so that there are two or more contact points (sealing points) always between the inner tooth part 511 of the outer rotor 51 and the outer tooth part 521 of the inner rotor 52. For example, they are brought in contact at two positions of the sealing points SP1 and SP2 (a). By increasing the sealing points like this, the counterflow of a brake fluid from the delivery port 61 to the suction port 60 can be prevented.

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 and discharging a fluid and a brake device using the rotary pump, and more particularly to an internal gear pump such as a trochoid pump and a pigot pump.

[0002]

2. Description of the Related Art Conventionally, an inscribed rotary pump has been known as described in JP-A-8-9129392. FIG. 6A is a schematic view of this conventional internal rotary pump. FIG. 6B is a sectional view taken along the line BB of FIG.
Shown in As shown in FIG. 6 (a), an outer rotor 151 and an inner rotor 152 are assembled and housed in a rotor chamber formed in a casing 150 of the internal rotary pump.

[0003] An outer rotor 151 has an inner tooth portion 151 on its inner periphery.
a, and the inner rotor 152 has external teeth 152a on the outer periphery. The outer teeth 152a have one less number of teeth than the inner teeth 151a, and only a part of the outer teeth 152a and the inner teeth 151 are engaged with each other. A plurality of tooth chambers 153 will be formed in the same. That is, the tooth chamber 153 is formed by the inner teeth 151a of the outer rotor 151 and the outer teeth 152a of the inner rotor 152.
Is formed, and there is no so-called partition plate (crescent).

[0006] As shown in FIG. 6 (b), a center hole 150 a is formed in the center of the casing 150, and a drive shaft 154 provided on an inner rotor 152 is fitted into the center hole 150 a. Have been. The outer rotor 151 is rotatably incorporated in the rotor chamber of the casing 150. Further, the casing 150
In the rotor chamber, a suction port 160 and a discharge port 161 are formed on both sides of the central axis of both rotors 151 and 152.

When the pump is driven, the inner rotor 152 rotates clockwise via the drive shaft 154 as shown by the arrow in FIG.
2a and the internal teeth 151a mesh with each other to form the outer rotor 15
1 also rotates in the same direction. At this time, the outer rotor 15
When the outer rotor 151 and the inner rotor 152 make one rotation, the volume of the tooth chamber 153 formed between the two rotors 151 and 152 due to the contact between the inner rotor 152 and the inner rotor 152 changes to a larger or smaller size. The oil is sucked in, and the oil is discharged at the discharge port 161.

When the pump is driven, the outer rotor 15 is used to perform a basic operation of sucking oil from the suction port 160 and discharging the oil from the discharge port 161.
A state occurs in which the tooth chamber 153 formed by the inner rotor 1 and the inner rotor 152 does not communicate with the suction port 160 or the discharge port 161. When the pressurized oil is trapped in the tooth chamber 153 in this state, the outer rotor 151 is pressed outward, and the outer rotor 151 and the inner rotor 152 are pressed.
There is a possibility that the part in contact with is opened.
When the contact portion between the rotors 151 and 152 is thus opened, the fluid moves from the discharge port 161 on the high pressure side to the suction port 160 on the low pressure side, and there is a possibility that high pressure discharge cannot be performed. That is, the oil is originally sucked from the low pressure side suction port 160 and the high pressure side
Even though it is necessary to discharge the oil in step 1, the basic operation is hindered.

In the state shown in FIG. 6A, for example, the internal teeth 151a of the outer rotor 151 are located between the suction port 160 and the discharge port 161 when viewed in the rotation direction of the inner rotor 152 indicated by the arrow. Inner rotor 1
52 external teeth 152a are two seal points SP
1, SP2, but both rotors 15
In FIG. 7, which shows a state in which the first and second rotations 152 are rotated,
The inner tooth part 151a and the outer tooth part 152a between 0 and the discharge port 161 are in contact at one seal point SP1. In particular, in the case where contact is made only at one seal point SP1 as shown in FIG.
High-pressure oil from 1 leaks to the suction hole 160 side.

SUMMARY OF THE INVENTION In view of the above problems, the present invention provides a rotary pump capable of preventing the inconvenience that a contact portion between an outer rotor and an inner rotor is opened and fluid leaks from a discharge port side to a suction port side. The first object is to provide It is a second object of the present invention to provide a brake device including the rotary pump and capable of preventing leakage of brake fluid from the discharge port side to the suction port side.

[0009]

In order to achieve the above object, the following technical means are employed. In order to achieve the first object, the invention according to claim 1 is directed to an outer rotor having an inner tooth portion on an inner periphery, a rotational motion given by a drive shaft, and an inner rotor having an inner tooth portion. An inner rotor having an external tooth portion meshing with the tooth portion, eccentrically by a predetermined amount, and a rotating portion configured to be assembled so as to form a tooth chamber with the internal tooth portion and the external tooth portion; and the outer rotor is rotatable. A casing having a rotor chamber for holding the drive shaft and an opening for fitting the drive shaft, and covering the rotating part; a suction port formed in the casing, for sucking fluid into the rotating part; and a casing formed in the casing. And a discharge port for discharging a fluid from the rotating unit, wherein the rotary pump sucks the fluid from the suction port by a rotational motion of the rotating unit, and discharges the fluid through the discharge port. The distance between the suction port end and the discharge port end in the rotation direction of the rolling portion is configured to be larger than two teeth so that there are always two or more contact points between the internal teeth and the external teeth. Features.

The rotary pump according to the present invention is an internal gear pump such as a trochoid pump or a pigot pump, and has a type in which a tooth chamber is formed by the internal teeth and the external teeth of both rotors. It is a rotary pump. That is, a type in which a partition plate (crescent) is interposed between both rotors is excluded. Then, the basic pump operation of sucking the fluid from the suction port by the rotation of the rotating unit and discharging the fluid through the discharge port can be performed.

Here, the suction port and the discharge port of the rotary pump have a distance from the end of the suction port to the end of the discharge port in the rotating direction of the rotating portion. It is configured to be larger than two teeth so that there are two or more teeth. As described above, by increasing the number of contact points, it is possible to prevent an inconvenience of undesired fluid leakage from the discharge port side to the suction port side. In other words, fluid leakage does not occur unless all contact points of two or more rotors are opened. In addition, the fact that the distance from the suction port end to the discharge port end is larger than two teeth means that the space is formed by the internal teeth portion and the external teeth portion and is not communicated with any of the suction port and the discharge port. 1 tooth chamber
There are two cases and two cases. When there is one non-communicating tooth chamber, the number of the contact points is two,
When there are two non-communicating tooth chambers, the number of the contact points is three.

By the way, the leakage of the fluid from the discharge port side to the suction port side may occur at the interval from the discharge port end to the suction port end in the rotation direction of the rotating unit. Therefore, the distance between the discharge port end and the suction port end in the rotation direction of the rotating portion is such that there are always two or more contact points between the internal teeth portion and the external teeth portion. It is conceivable that the configuration is made larger than two teeth.

With this configuration, the contact between the internal teeth and the external teeth in both the distance from the suction port end to the discharge port end and the distance from the discharge port end to the suction port end in the rotation direction of the rotating unit. This increases the number of locations and can prevent the inconvenience of fluid leakage from the discharge port side to the suction port side.

By increasing the distance between the end of the suction port and the end of the discharge port, the number of tooth chambers that are not communicated with both the suction port and the discharge port increases. It is possible that the part is open,
To cope with such a situation, a configuration as described in claim 3 may be adopted. That is, a conduction path is provided to connect the tooth chamber not communicating with the suction port and the discharge port to the outer periphery of the outer rotor.

[0015] By doing so, the fluid in the tooth chamber is guided to the outer periphery of the outer rotor via the conduction path before being excessively compressed. The fluid guided to the outer rotor outer periphery acts to press the outer rotor toward the inner rotor. In other words, while preventing excessive compression in the tooth chamber,
Opening of the contact portion between the two rotors is more firmly prevented.

When such a conduction path is provided, it is preferable to adopt the following configuration. That is, as shown in claim 4, a state in which two or more tooth chambers that are not connected to both the suction port and the discharge port are formed at a position between the suction port and the discharge port in the rotation direction of the rotating unit. Is present, and the volume of the two or more tooth chambers is configured to decrease relatively as going from the suction port end side to the discharge port end side, and the conduction path is formed between the two or more tooth chambers. The inside of the outer rotor is provided so as to communicate with the outer periphery of the outer rotor.

In this case, the volume of the two or more tooth chambers which are not communicated with both the suction port and the discharge port decreases from the suction port end side to the discharge port end side. Is more likely to occur. Therefore, by releasing the high-pressure fluid to the outer periphery of the outer rotor via the conduction path, it is effective in preventing excessive compression in the tooth chamber and opening of the contact portion between the two rotors.

Further, a seal member for preventing the fluid from leaking outside from the opening may be provided. Specifically, a seal member is attached to the inner rotor,
Alternatively, a seal member may be attached to the drive shaft itself. For example, an O-ring or the like can be applied to this seal member. As described above, since the fluid in the tooth chamber that is not communicated with any of the suction port and the discharge port is guided to the outer periphery of the outer rotor through the conduction path, the fluid flows through the gap between the rotating portion and the casing. May move to the opening side. Therefore, preventing the fluid from leaking outside from the opening by the seal member is also effective in improving the discharge efficiency.

On the other hand, in order to achieve the second object, the invention according to claim 5 provides a brake fluid pressure generating means for generating brake fluid pressure based on a pedaling force, A braking force generating means for generating a braking force, a main line connected to the brake fluid pressure generating means for transmitting the brake fluid pressure to the braking force generating means, and a braking force generating means connected to the brake fluid pressure generating means; A rotary pump according to any one of claims 1 to 4, wherein the rotary pump according to any one of claims 1 to 4, further comprising an auxiliary pipe for supplying brake fluid to a main pipe side to increase a braking force to be applied. The discharge port is provided in the auxiliary conduit with the discharge port facing the braking force generating means side.

In the present brake device, the brake fluid pressure in the auxiliary pipeline becomes high due to the brake fluid pressure generated based on the pedaling force. However, since the rotary pump according to any one of claims 1 to 4 is provided, the suction port provided toward the brake fluid pressure generating means from the discharge port provided toward the braking force generating means. Of the brake fluid can be suitably prevented. Therefore, suction and discharge can be performed efficiently, and the brake function is not impaired.

In this brake device, the rotary pump sucks the brake fluid of the first brake fluid pressure from the brake fluid pressure generating means side.
Pressure can be increased to a second brake fluid pressure that is higher than the first brake fluid pressure and can be discharged to the braking force generating means. The brake fluid pressure applied to the braking force generating means by the rotary pump is equal to the first brake fluid pressure. It is also conceivable to provide a differential pressure holding means for holding a differential pressure between the second brake fluid pressure on the side of the braking force generating means and the first brake fluid pressure on the side of the brake fluid pressure generating means when the pressure is made higher. Can be

As described above, the differential pressure when the second brake fluid pressure in the braking force generating means is increased to be higher than the first brake fluid pressure generated by the brake fluid pressure generating means is determined. High pressure discharge by a rotary pump is also required to adopt the holding configuration, but as described above, the rotary pump can prevent leakage of brake fluid from the discharge port to the suction port during high pressure discharge, and discharge efficiency It is very effective because it can improve.

The rotary pump of the present invention can be applied not only to a brake device but also to various devices using other rotary pumps.

[0024]

Embodiments of the present invention will be described below with reference to the drawings. FIG. 1 shows a schematic diagram of a brake pipe of a brake device to which a trochoid pump as a “rotary pump” is applied. Hereinafter, the basic configuration of the brake device is shown in FIG.
It will be described based on. In this example, an example in which a brake device according to the present invention is applied to a front-wheel-drive four-wheeled vehicle that constitutes an X-pipe hydraulic circuit including respective pipe systems of right front wheel-left rear wheel, left front wheel-right rear wheel. 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 "brake fluid pressure generating means".

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 as "braking force generating means" via an anti-lock brake device (hereinafter, referred to as ABS). ing. 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 A as a "main pipe" connected to the master cylinder 3, and this pipe A is provided with a proportional control valve (PV; proportioning valve) 22. I have. The pipe A is divided into two parts by the proportional control valve 22.
That is, the line A is connected from the master cylinder 3 to the proportional control valve 2.
Pipeline A1 receiving master cylinder pressure up to 2
And a pipeline A2 between the proportional control valve 22 and each of the wheel cylinders 4 and 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 line A2, the line 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 (hereinafter referred to as ECU) for ABS. When the two-position valve is controlled to be in communication, the master cylinder pressure or the brake fluid pressure generated by the discharge of the brake fluid from the pump can be applied to the wheel cylinders 4 and 5.

When the ABS is not being executed, the first and second pressure-increasing control valves 3 and 4 operate 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, 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 reduction control valves 32 and 33, which can control the communication / fast disconnection state by the ECU for BS, are provided respectively. These pressure reduction control valves 32 and 33 are in a normal brake state (ABS
(At the time of non-operation), it is always in a cutoff state. The first and second pressure increasing control valves 30, 31 and the pressure reducing control valve 32,
33 is a mechanism for adjusting the brake fluid pressure.

The rotary pump 10 is provided with two safety valves 10 in a pipe C connecting the proportional control valve 22 and the pressure increasing control valves 30 and 31 of the pipe A and the reservoir hole 20a of the reservoir 20.
a, 10b. 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,
A line D as an "auxiliary line" is provided so as to connect to the master cylinder 3, and the rotary pump 10 pumps up the brake fluid in the line A1 through the line D and moves to the line A2. By discharging, the wheel cylinder pressure in the wheel cylinders 4 and 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.

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 conduits C and D and the reservoir 2 are prevented from leaking from the conduit C to the reservoir 20 by the hydraulic pressure transmitted from the conduit D.
A check valve 21 is provided between the zero points.

The control valve 40 is normally in a communicating state. However, when the master cylinder pressure is lower than a predetermined pressure, when the wheel cylinders 4 and 5 are suddenly braked,
It is shut off at C and maintains the differential pressure between the master cylinder side and the wheel cylinder side. In this sense, the control valve 40 and the above-described proportional control valve 22 correspond to “differential pressure holding means”.

Next, an embodiment of the rotary pump 10 applied in such a configuration as a brake device will be described. FIG. 2A is a schematic view of the rotary pump 10 according to the embodiment. FIG. 2B shows FIG.
(A) is a cross-sectional view taken along the line AA. First, FIG.
The structure of the rotary pump 10 will be described based on FIG.

In the rotor chamber 50a of the casing 50 of the rotary pump 10, an outer rotor 51 and an inner rotor 52 are housed with their centers eccentric. Further, the outer rotor 51 has an inner tooth portion 511 on the inner periphery, and the inner rotor 52 has an outer tooth portion 521 on the outer periphery. The outer rotor 51 and the inner rotor 52 form a plurality of tooth chambers 53 and mesh with each other at the mesh surface S. As can be seen from FIG. 2A, the rotary pump according to the present embodiment includes the inner tooth portion 51 of the outer rotor 51.
This is a multi-tooth trochoid type pump without a partition plate (crescent), which forms a tooth chamber 53 with the outer tooth portion 521 of the inner rotor 52. 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.

The above-described casing 50 includes the two rotors 5.
A first side plate portion 71 and a second side plate portion 72 disposed so as to sandwich the first and second side plates 52 from both sides, and are disposed between the two side plate portions 71 and 72;
A central plate portion 73 provided with a hole 703 slightly larger than the outer periphery of the outer rotor 51;
These form a rotor chamber 50a.

Further, the first and second side plate portions 7
Center holes 701 and 702 communicating with the inside of the rotor chamber 50a are formed in the center portions of the center holes 70 and 72.
The drive shaft 54 fitted to the inner rotor 52 is fitted into the reference numeral 1 702. The outer rotor 51 is rotatably disposed in the hole 703 of the central plate 73. That is, the inner rotor 52 is meshed with the outer rotor 51, and the rotating portion formed by the outer rotor 51 and the inner rotor 52 is rotatably incorporated in the rotor chamber 50 a of the casing 50. Then, the first and second side plate portions 71 and 72 and the center plate portion 73 are screwed together by bolts 75 to form the casing 50.

Further, the first side plate portion 71 has a suction port 60 and a discharge port 61 communicating with the rotor chamber 50a on the left and right sides of the center line passing through the drive shaft 54 in the state shown in FIG. Are formed. The suction port 60 and the discharge port 61 are provided at positions communicating with a plurality of tooth chambers 53 formed by meshing the outer rotor 51 and the inner rotor 52, and allow the brake fluid from the outside to enter the suction port 6.
The brake fluid in the tooth chamber 53 can be discharged to the outside through the discharge port 61.

There is a characteristic in the position where the suction port 60 and the discharge port 61 are provided. That is, the distance L from the end of the suction port 60 to the end of the discharge port 61 in the rotation direction of the inner rotor 52 (that is, the rotation direction of the outer rotor 51) indicated by an arrow in FIG. Is also set large. This is for setting so that there are always two or more contact points (seal points) between the internal teeth 511 of the outer rotor 51 and the external teeth 521 of the inner rotor 52. For example, FIG. In the case shown, the two parts are in contact at the seal points SP1 and SP2. In addition, the above-described suction port 60 ends to the discharge port 6.
That the interval to one end is larger than two teeth means that the tooth space 53 formed by the internal teeth portion 511 and the external teeth portion 521 and not communicated with any of the suction port 60 and the discharge port 61 at that interval.
There is a case where one exists and a case where two exist.
Even if there is one non-communicating tooth chamber 53, the seal point is 2
There are two. This point will be supplemented with reference to FIG.

Further, the first side plate portion 71
In the case where there is a non-communicable tooth chamber 53 between the suction port 60 and the discharge port 61 between the end of the suction port 60 and the end of the discharge port 61 described above, the tooth chamber 53 and the outer rotor 51 are provided. There is provided a conduction path 90 that communicates with the outer periphery. In this embodiment, the rotor 51,
In the interval between the end of the outlet 60 and the end of the inlet 61 in the direction of rotation of 52, there is a state in which two or more tooth chambers 53 that are not connected to both the inlet 60 and the outlet 61 are formed.
Further, the volume of the two or more tooth chambers 53 is configured to decrease relatively from the end of the suction port 60 to the end of the discharge port 61. In addition, the above-described conduction path 90 is provided so as to communicate a relatively small volume of the two or more tooth chambers 53 with the outer periphery of the outer rotor 51.

Next, the operation of the brake device and the rotary pump 10 configured as described above will be described with reference to FIGS. However, regarding the operation of the brake device,
The case where pressure is applied to the suction port 60 of the rotary pump 10 will be described. The brake fluid pressure applied to the suction port 60 of the pump 10 is adjusted, and after the pressure is reduced, the suction port 60 is controlled.
In this case, the brake fluid having a brake fluid pressure lower than the master cylinder pressure can be suctioned by the pump.
This pressure adjustment can be performed by duty-driving the valve 34 or by adding a pressure-adjustable valve. When the master cylinder pressure or the adjusted pressure is applied to the suction port 60, Both have substantially the same effect on leakage from the discharge port 61 to the suction port 60.

As shown in FIG. 1, the control valve 34 provided in the brake device is used 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 increased. When the value is large, the communication state is appropriately set. On the other hand, in the rotary pump 10, the drive shaft 54 (see FIG. 2) is rotated by the driving of the motor 11, and the inner rotor 52 is rotated in accordance with the rotation. And
With the rotation of the inner rotor 52, the outer rotor 51 also rotates in the same direction due to the meshing of the internal teeth 511 and the external teeth 521. At this time, the volume of each tooth chamber 53 changes greatly during one rotation of the outer rotor 51 and the inner rotor 52 to suck the brake fluid from the suction port 60, and from the discharge port 61 to the pipeline A2 (see FIG. 1). Blow out the brake fluid toward). The wheel cylinder pressure is increased by the discharged brake fluid. In this rotation operation, the outer rotor 51 and the inner rotor 52 that rotate around the drive shaft 54 have positions where the rotation centers are eccentric to each other.

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 when the rotors 51 and 52 rotate. However, 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 is trapped in the tooth chamber 53, the outer rotor 51 is pressed outward, and the outer rotor 51 is pressed. There is a possibility that a part where the inner rotor 51 and the inner rotor 52 are in contact is opened. When the contact portion between the rotors 51 and 52 is opened, the fluid moves from the discharge port 61 on the high-pressure side to the suction port 60 on the low-pressure side, and high-pressure discharge may not be performed.

In this rotary pump 10, in order to prevent the leakage of the brake fluid, the distance L from the end of the suction port 60 to the end of the discharge port 61 in the rotation direction of the rotors 51 and 52 is set.
Was set larger than two teeth. As a result, FIG.
In the case shown in (a), the inner teeth 5 of the outer rotor 51
11 and the external teeth portion 521 of the inner rotor 52 come into contact (seal) at two points of the seal points SP1 and SP2. In this way, by increasing the number of locations to be sealed, it is possible to prevent the disadvantage that the brake fluid leaks from the undesired discharge port 61 side to the suction port 60 side. That is, FIG.
In the case shown in (a), two seal points SP1,
Unless both of SP2 are released, no leakage of brake fluid occurs.

By increasing the distance between the end of the suction port 60 and the end of the discharge port 61, the suction port 60 and the discharge port 6
1, the number of the tooth chambers 53 that are not communicated with each other increases, and the brake fluid in the tooth chambers 53 is over-compressed, and the contact portions, for example, the seal points SP1 and SP1 in FIG.
It is also conceivable that both SP2 may open. Therefore, in order to cope with such a situation, in the present embodiment, the above-described conduction path 90 is provided. That is, the inlet 6
The brake fluid teeth in the tooth chamber 53 that are not in communication with both the zero and the discharge port 61 are guided to the outer periphery of the outer rotor 51 via the conduction path 90 before being excessively compressed. The brake fluid guided to the outer periphery of the outer rotor 51 acts to press the outer rotor 51 toward the inner rotor 52. That is, the overcompression in the tooth chamber 53 is prevented, and the contact portion between the rotors 51 and 52 is more securely prevented from being opened.

In this embodiment, the rotor 5
1, 52 to the inlet 6 from the end of the outlet 60 in the rotation direction.
There may be a state where two or more non-communicating tooth chambers 53 are formed in both the suction port 60 and the discharge port 61 at intervals up to one end, and the volume of the two or more tooth chambers 53 is present. However, it is configured to decrease relatively from the end of the suction port 60 to the end of the discharge port 61. In addition, a conduction path 90 is provided so as to allow a relatively small one of the two or more tooth chambers 53 to communicate with the outer periphery of the outer rotor 51. Since the volumes of the two tooth chambers 53 that are not in communication with both the suction port 60 and the discharge port 61 decrease from the end of the suction port 60 toward the end of the discharge port 61, the above-described overcompression is more likely to occur. Therefore, by releasing the fluid of the brake fluid to the outer periphery of the outer rotor 51 via the conduction path 90, the over-compression in the tooth chamber 53 is prevented, and both rotors 5
This is effective in preventing the contact portion between the first and second members from being opened.

In order to clarify these points, a further explanation will be given with reference to FIGS. FIGS. 3 and 4 continuously show a state in which the inner rotor 51 and the outer rotor 52 rotate. Only the rotors 51 and 52, the suction hole 60, the discharge hole 61, and the conduction path 90 are shown. I do. Both rotors 51 and 52 are shown in FIG.
→ (b) → (c), and then (a) →
They rotate in the direction of the arrow in the figure in the order of (b) → (c).

For example, in the state shown in FIG. 3B, three seal points SP1 and SP are provided between the end of the discharge port 60 and the end of the suction port 61 in the rotation direction of the rotors 51 and 52.
2, SP3 does not leak from the discharge port 61 to the suction hole 60 unless all of them are opened. 3 (a), (c) or FIG. 4 (a),
In the states shown in (b) and (c), there are two seal points SP1 and SP2, respectively, and as long as both of them are not opened, leakage from the discharge port 61 to the suction hole 60 does not occur.

FIG. 3A, FIG. 3B or FIG.
In the state shown in (c), between the end of the discharge port 60 and the end of the suction port 61 in the rotation direction of the rotors 51 and 52, there is a tooth chamber 53 that is not communicated with any of the suction port 60 and the discharge port 61. Since there is provided a conduction path 90 for communicating the tooth chamber 53 with the outer periphery of the outer rotor 51, the tooth chamber 53
The brake fluid, which has become high pressure inside, moves to the outer periphery of the outer rotor 51 via the conduction path 90,
3 is prevented. Further, the outer rotor 5
The brake fluid guided to the outer periphery of 1 presses the outer rotor 51 toward the inner rotor 52.

In the brake device to which the rotary pump 10 is applied, the following effects are exhibited. That is, the brake fluid pressure in the pipeline D as the auxiliary pipeline becomes high due to the brake fluid pressure generated based on the pedaling force. However, since the rotary pump 10 described above is provided, the brake fluid pressure is directed toward the wheel cylinders 4 and 5. Of the brake fluid from the discharge port 61 provided to the master cylinder 3 side can be suitably prevented. Therefore, it is possible to discharge efficiently and without impairing the braking function, which is very effective.

Further, in the brake device of this embodiment, the differential pressure when the brake fluid pressure in the wheel cylinders 4 and 5 is increased to be higher than the brake fluid pressure generated in the master cylinder 3 is maintained. Configuration (control valve 4
Even when employing 0 or the proportional control valve 22), high pressure discharge by the rotary pump 10 is required. However, as described above, the rotary pump 10 prevents leakage of brake fluid from the discharge port 61 to the suction port 60. It can be suitably prevented. Therefore,
Efficient discharge, without damaging the brake function,
Very effective.

As described above, the present invention is not limited to such embodiments at all, and can be implemented in various forms without departing from the gist of the present invention. For example, in the above-described embodiment, the interval L from the end of the suction port 60 to the end of the discharge port 61 in the rotation direction of the rotors 51 and 52 is set to be larger than two teeth, but from the discharge port 61 side to the suction port 60 side. The leakage of the brake fluid may occur also in the interval from the end of the discharge port 61 to the end of the suction port 60 in the rotation direction of the rotors 51 and 52. Therefore, as shown in FIG. 5, the distance Lb from the end of the discharge port 61 to the end of the suction port 60 is also set to be larger than two teeth, and the internal tooth part 511 and the external tooth part 52 are set.
There are always two or more seal points with 1 (SP in FIG. 5)
3 and SP4).

In this way, the internal teeth 511 are formed at both the distance from the end of the suction port 60 to the end of the discharge port 61 and the distance from the end of the discharge port 61 to the end of the suction port 60 in the rotation direction of the rotors 51 and 52. Contact points between the outer teeth 521 and
That is, the seal points (SP1, SP2, SP3, SP
4) is increased, and the inconvenience of leakage of the brake fluid from the discharge port 61 side to the suction port 60 side can be more suitably prevented.

In this case, the effect is particularly effective when the master cylinder pressure is applied to the suction port 60. For example, if the pump discharge pressure is smaller than the master cylinder pressure, the seal points SP3 and SP4 Thus, leakage from the suction port 60 to the discharge port 61 can be prevented. Therefore, it is possible to provide a pump having high liquid-tightness on the surface between the inner rotor 52 and the outer rotor 51 together with the seal points SP1 and SP2.

Further, in the above-described embodiment, the case where the brake fluid is applied as the fluid has been described, but other fluids such as water may be applied. Further, in the above-described embodiment, the case where the rotary pump 10 is realized as a trochoid pump has been described. However, the rotary pump 10 may be configured as a piggot pump of the same internal gear pump.

The brake device shown as an application of the rotary pump of the above embodiment is an example, and is not limited to this brake device.

[Brief description of the drawings]

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

FIG. 2A is a schematic view of a rotary pump according to an embodiment, and FIG. 2B is a cross-sectional view taken along the line AA of FIG.

FIG. 3 is a schematic explanatory view continuously showing a state in which an inner rotor and an outer rotor in the embodiment rotate.

FIG. 4 is a schematic explanatory view continuously showing a state in which an inner rotor and an outer rotor in the embodiment rotate, continued from FIG. 3;

FIG. 5 is a schematic explanatory view of a rotary pump according to another embodiment, showing only rotors, suction holes, discharge holes, and conduction paths.

FIG. 6A is a schematic view of a conventional rotary pump, and FIG. 6B is a cross-sectional view of FIG.

FIG. 7 is a schematic view of a conventional rotary pump, showing only rotors, suction holes and discharge holes.

[Explanation of symbols]

DESCRIPTION OF SYMBOLS 10 ... Rotary pump 22 ... Proportional control valve 30, 31 ... Pressure increase control valve 32, 33 ... Pressure reduction control valve 34, 40 ... Control valve 50 ... Casing 50a ... Rotor room 51 ... Outer rotor 52 ... Inner rotor 53 ... Tooth room 54 Drive shaft 60 Suction port 61 Discharge port 71 First side plate 72 Second side plate 73 Central plate 90 Conduction path 511 Internal teeth 521 External teeth A Pipe Road (main pipeline) D ... pipeline (auxiliary pipeline) SP1, SP2, SP3, SP4 ... seal point

 ──────────────────────────────────────────────────の Continued on the front page (72) Inventor Tomio Harada 1-1-1, Showa-cho, Kariya-shi, Aichi Prefecture Inside DENSO Corporation

Claims (6)

[Claims] 1. An outer rotor having an inner tooth portion on an inner periphery thereof, and an inner rotor having an outer tooth portion provided with a rotational motion by a drive shaft and being engaged with the inner tooth portion of the outer rotor on an outer periphery. A rotating part configured to be fixedly eccentric and assembled so as to form a tooth chamber with the internal tooth part and the external tooth part; a rotor chamber that rotatably holds the outer rotor and an opening part that fits the drive shaft. A casing that covers the rotating part, a suction port formed in the casing and sucking fluid into the rotating part, and a discharge port formed in the casing and discharging fluid from the rotating part, 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; Rotary pump the interval between the discharge port end, characterized in that the contact point between the inner teeth and the outer teeth portion is always larger configuration than two teeth so that there exist two or more. The distance between the discharge port end and the suction port end in the rotation direction of the rotating section is set so that there are always two or more contact points between the internal teeth and the external teeth.
The rotary pump according to claim 1, wherein the rotary pump is configured to be larger than a tooth. 3. A tooth chamber that is not communicated with any of the suction port and the discharge port is formed at a position between the suction port and the discharge port. 3. A conductive path for communicating between the outer rotor and an outer periphery of the outer rotor is provided.
2. The rotary pump according to 1. 4. A state in which two or more tooth chambers that are not communicated with any of the suction port and the discharge port are formed at a position between the suction port and the discharge port in the rotation direction of the rotating unit. Is present, and the volume of the two or more tooth chambers is configured to decrease relatively as going from the suction port end side to the discharge port end side. 4. The rotary pump according to claim 3, wherein the rotary pump is provided so as to communicate a relatively small volume in the tooth chamber with the outer periphery of the outer rotor. 5. 5. A brake hydraulic pressure generating means for generating a brake hydraulic pressure based on a pedaling force; a braking force generating means for generating a braking force on wheels based on the brake hydraulic pressure; and a connection to the brake hydraulic pressure generating means. A main fluid line for transmitting the brake fluid pressure to the braking force generating means, and a brake fluid connected to the brake fluid pressure generating means for increasing a braking force generated by the braking force generating means. A rotary pump according to any one of claims 1 to 4, wherein the rotary pump directs the suction port toward the brake fluid pressure generating means, and the discharge port controls the discharge port. Toward the braking force generation means,
A brake device provided in the auxiliary pipeline. 6. The rotary pump sucks a brake fluid of the first brake fluid pressure from the brake fluid pressure generating means side to a second brake fluid pressure higher than the first brake fluid pressure. When the brake fluid pressure applied to the braking force generating means is higher than the first brake fluid pressure by the rotary pump, the braking force generating means can be pressurized and discharged to the braking force generating means side. 6. A pressure difference holding means for holding a pressure difference between the second brake fluid pressure on the side of the brake fluid and the first brake fluid pressure on the side of the brake fluid pressure generating means. The brake device as described.