JPH10205459A - Rotary type pump and brake device using rotary type pump - Google Patents

Abstract

PROBLEM TO BE SOLVED: To provide a rotary type pump to prevent the occurrence of leakage to an external part even when high pressure fluid is sucked from a suction port. SOLUTION: A drive shaft 54 is arranged at the central hole 50a of a casing 50 to cover a rotary part consisting of an outer rotor 51 and an inner rotor 52. Through rotational movement by the rotary part brake liquid is sucked and discharged through a suction port 60 and a discharge port 61, formed in the casing 50. An O-ring 70 rotated togetherwith the drive shaft 54 is arranged in a state to be positioned eccentrically from the drive shaft 54. This constitution prevents brake liquid from leakage through the central hole 50a to an external part.

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 is particularly suitable for an internal oil pump rotor.

[0002]

2. Description of the Related Art FIG. 5 (a) shows a schematic view of a conventional inscribed rotary pump. FIG. 5B is a cross-sectional view taken along the line CC of FIG. 5A. As shown in FIG. 5 (a), an outer rotor 51 and an inner rotor 5 are provided in a rotor chamber of a casing 50 in an inscribed rotary pump.
2 is assembled.

[0003] The outer rotor 51 has internal teeth 51a on the inner periphery, and the inner rotor 52 has external teeth 5a on the outer periphery.
2a. And these outer rotors 51
And the inner rotor 52 are meshed with each other to form a plurality of gaps 53. As shown in FIG. 5B, a center hole 50a is formed in the center of the casing 50, and a drive shaft 54 provided in the inner rotor 52 is fitted into the center hole 50a. . The outer rotor 51 is rotatably incorporated in the rotor chamber of the casing 50. Further, a suction port 60 and a discharge port 61 are formed on both sides of the center axis of both rotors 51 and 52 in the rotor chamber of the casing 50.

[0004] When the pump is driven, the inner rotor 52 rotates via the drive shaft 54, and the external teeth 5
The outer rotor 51 also rotates in the same direction due to the engagement between the inner teeth 2a and the internal teeth 51a. At this time, the volume of each gap 53 is set such that the outer rotor 51 and the inner rotor 52
During the rotation, the oil changes in size to suck the oil from the suction port 60 and discharge the oil at the discharge port 61.

When the pump is driven, a predetermined gap 1 is provided between the casing 50 and the outer rotor 51, the inner rotor 52, and the drive shaft 54 in order to smoothly rotate the outer rotor 51 and the inner rotor 52.
00 is provided. However, these gaps 1
Since oil leakage occurs from 00, the center hole 50a is sealed with an oil seal 110 in order to prevent the oil leakage, and a return pipe G for returning oil in the gap 100 to the suction port 60 is connected to the casing 50. It is provided within.

That is, although the oil leaking through the gap 100 is reduced in pressure by the flow resistance in the gap 100, if there is no escape of the oil from the gap 100,
The pressure inside the gap 100 is increased by the accumulated oil. As a result, the allowable pressure of the oil seal 110 is exceeded, and external leakage of oil occurs. For this reason, by returning the leaked oil from the return pipe G to the suction port 60, it is possible to prevent the pressure in the gap 100 from increasing, and to prevent the oil from leaking outside.

[0007]

The oil flows from the high pressure side to the low pressure side. Therefore, when the pressure of the oil sucked from the suction port 60 is higher than the pressure in the gap 100, the leaked oil is not returned through the return line G, and the pressure in the gap 100 is increased. When the pressure increases and exceeds the allowable pressure of the oil seal 110, there is a problem that external leakage occurs.

In view of the above, it is a first object of the present invention to provide a rotary pump capable of preventing external leakage even when a high-pressure fluid is sucked from a suction port. A second object of the present invention is to prevent a brake fluid from leaking in a brake device to which a rotary pump is applied.

[0009]

In order to achieve the above object, the following technical means are employed. According to the first aspect of the present invention, the drive shaft (54) is disposed in the opening (50a) of the casing (50) that covers the rotating parts (51, 52), and the driving shaft (54) is rotated by the rotating parts (51, 52). In a rotary pump that sucks and discharges fluid through a suction port (60) and a discharge port (61) provided in a casing (50), the rotary pump rotates together with a drive shaft (54) to move the fluid from the opening (50a) to the outside. A seal member (70) for preventing leakage is provided eccentrically with respect to the drive shaft (54).

As described above, since the seal member (70) is provided, it is possible to prevent the fluid from leaking from the opening (50a). Since the seal member (70) and the drive shaft (54) are eccentric with each other, when the seal member (70) rotates, the fluid adheres to the seal member (70) and further lubricates the rotational movement. To Thereby, the durability of the sealing member (70) can be improved.

More specifically, as in the second aspect, the outer rotor (51) and the inner rotor (52)
The inner rotor (52) of the rotating part constituted by
A seal member (70) can be attached to the second member. According to the third aspect of the present invention, the rotating plate () that rotates together with the rotating parts (51, 52) is closer to the opening (50a) than the rotating parts (51, 52) of the drive shaft (54). 8
0), and a seal member (7) is attached to the rotating plate (80).
0) can be attached.

According to the present invention, the seal member (70) for preventing the fluid from leaking to the outside of the opening (50a) is inclined with respect to a plane perpendicular to the drive shaft (54). And is provided on the drive shaft (54). Thus, the seal member (70) is connected to the drive shaft (5).
The same effect as that of the first aspect can be obtained even if the third aspect is mounted.

[0013] As described in claim 5, an O-ring (70) can be applied to the seal member. In the invention described in claim 6, the brake fluid pressure generating means (1
-3) to the braking force generating means (4, 5) and the main pipeline (A) for transmitting the brake fluid pressure;
In a brake device having an auxiliary pipe (D) for supplying brake fluid from 3) to the braking force generating means (4, 5),
The rotary pump according to any one of claims 1 to 5, wherein the suction port (60) is provided with brake hydraulic pressure generating means (1 to 3).
The discharge port (61) to the braking force generating means (4, 5)
It is characterized in that it is provided in the auxiliary pipeline (D) toward the side.

The brake fluid pressure in the auxiliary pipeline (D) becomes high due to the brake fluid pressure generated based on the pedaling force. However, in the rotary pump according to any one of claims 1 to 5, even when a high pressure is applied to the suction port (60), it is possible to prevent the fluid from leaking to the outside. Even if the brake fluid pressure in 3) is high, external leakage of fluid can be prevented.

[0015]

DESCRIPTION OF THE PREFERRED EMBODIMENTS (First Embodiment) FIG. 1 shows a schematic diagram of a brake piping of a brake device to which an inscribed rotary pump (trochoid 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 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 pedal force and the like. The booster 2 has a bush rod or the like for transmitting the boosted treading force to the master cylinder 3, and the bush rod presses a master piston disposed on the master cylinder 3 so that the master cylinder 3 is pressed. Pressure develops.

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 the pipe A is provided with a proportional control valve 22. The pipe A is divided into two parts by the proportional control valve 22. That is, the pipe A includes a pipe A1 that receives the master cylinder pressure between the master cylinder 3 and the proportional control valve 22;
It is divided into pipes A2 of up to 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.

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 due to the discharge of the brake fluid from the pump can be applied to each wheel cylinder 4,5.

When the ABS control is not performed, 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 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 pipe 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 provided in the pipeline C on the discharge side of the rotary pump 10. 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 C and maintains the differential pressure between the master cylinder side and the wheel cylinder side. Next, FIG.
FIG. 2B is a schematic diagram of FIG. 2A, and FIG.
FIG. First, the structure of the rotary pump 10 will be described with reference to FIGS.

In the rotor chamber of the casing 50 of the rotary pump 10, an outer rotor 51 and an inner rotor 52 are assembled with their respective centers being eccentric. 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 and mesh with each other at the mesh surface S. 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.

A central hole 50a communicating with the rotor chamber is formed at the center of the casing 50.
A drive shaft 54 disposed on the inner rotor 52 is fitted into Oa. The outer rotor 51 is rotatably incorporated in the rotor chamber of the casing 50. When the pump is driven, predetermined gaps 100a and 100b are provided between the casing 50 and the outer rotor 51, the inner rotor 52, and the drive shaft 54 to smoothly rotate the outer rotor 51 and the inner rotor 52. I have.

Further, in the rotor chamber of the casing 50,
A suction port 60 and a discharge port 61 are formed on the left and right (left and right in FIG. 2A) across a center line passing through the drive shaft 54. An O-ring 70 is mounted inside the suction port 60 and the discharge port 61 so as to be eccentric with respect to the drive shaft 54. Specifically, the inner rotor 52 includes
A groove formed eccentrically with respect to the drive shaft 54 is formed, and an O-ring 70 is mounted in the groove.

The O-ring 70 maintains the liquid tightness of the gap 100a and the gap 100b. O-ring 7
0 indicates that the allowable pressure is higher than that of the oil seal and the gap 100a
And the gap 100b can be kept sufficiently liquid-tight.
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 of the rotary pump 10.

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, 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. Note that the outer rotor 51 and the inner rotor 52 that rotate about the drive shaft 54 have positions where the rotation centers are eccentric to each other.

At this time, the gap 10 is
Since the liquid tightness of the gap 0b and the gap 100b is maintained, the brake fluid does not leak out of the casing 50 even when the pressure of the suction port 60 becomes high. The O-ring 70 also rotates with the rotation of the inner rotor 52. At this time, with the O-ring 70 eccentric with respect to the drive shaft 54, the inner rotor 5
2, the gap 100 during this rotation.
The brake fluid in a adheres to the O-ring 70. The rotation of the O-ring 70 can be smoothly performed by the attached brake fluid, and the durability of the O-ring 70 can be improved.

As described above, by attaching the O-ring 70 to the inner rotor 52 in an eccentric state with respect to the drive shaft 54, it is possible to prevent the brake fluid from leaking outside without any problem in durability of the O-ring 70. The center hole 5
0a may be oil-sealed and lubricating oil may be sealed in the gap 100b. Thereby, the rotation of the O-ring 70 can be further lubricated, and the durability of the O-ring 70 can be improved.

(Second Embodiment) FIG. 3A is a schematic view of a rotary pump 10 according to this embodiment. FIG. 3B is a cross-sectional view taken along the line BB of FIG. The description of the same configuration as that of the first embodiment will be omitted. As shown in FIGS. 3A and 3B, a rotating plate chamber is provided in the casing 50 separately from the rotor chamber, and a rotating plate 80 is built in the rotating plate chamber. The center of the rotating plate 80 is connected to the drive shaft 54 and is disposed closer to the motor 11 than the inner rotor 52 is.

There is a gap between the rotating plate 80 and the rotating plate chamber so that the rotating plate 80 can rotate smoothly. An O-ring 70 is attached to the rotating plate 80 in a state where the O-ring 70 is eccentric with respect to the drive shaft 54, so that liquid tightness between the gap 100a and the gap 100b is maintained. Thus, the rotating plate 80 provided separately from the inner rotor 52
O-ring 70 is attached to the inner rotor 5
The O-ring 70 can be attached regardless of the size of the O-ring 70. For example, a relatively small inner rotor 52
May be applied to the rotary pump 10, and in such a case, it is difficult to attach the O-ring 70 to the inner rotor 52. However, since the O-ring 70 can be attached to the rotating plate 80, such a problem can be avoided.

A pipe H is formed between the inner rotor 52 and the rotary plate 80 in the casing 50 to communicate the gap 100a with a low-pressure place (not shown).
Thereby, the brake fluid leaked into the gap 100a can escape to the low-pressure place through the pipeline H, so that the O-ring 70 can be prevented from being applied with a high pressure.

(Third Embodiment) FIG. 4 is a schematic view of a rotary pump 10 according to the present embodiment. The description of the same configuration as that of the first embodiment will be omitted. As shown in FIG. 4, an O-ring 70 is attached to the drive shaft 54 in a state where the O-ring 70 is inclined with respect to a plane perpendicular to the drive shaft 54.

As described above, since the O-ring 70 is attached to the drive shaft 54, the O-ring 70 is not affected by the size of the inner rotor 52, and does not require the rotating plate 80 as shown in the second embodiment. Can be prevented from leaking outside. Note that the same effect as in the second embodiment can be obtained by forming a conduit in the casing 50 for communicating the gap 100 (a) with a low-pressure place (not shown).

Further, although the O-ring 70 is fixed to the shaft side, it may be fixed to the casing 50 side. (Other Embodiments) In the second embodiment, the O-ring 70 is attached to the inner rotor 52 side of the rotating plate 80, but the O-ring 70 may be attached to the opposite side. Although the O-ring 70 is attached as a seal member, other seal members may be used, for example, a D-ring may be attached.

In the first to third embodiments, the case where the brake fluid is applied as a fluid has been described. However, other fluids, such as water, may be applied. In addition, in the first to third embodiments, the rotary pump 10 in which the inscribed rotary pump 10 is applied is shown. However, other rotary pumps, for example, the circumscribed rotary pump and the vane pump are used. The present invention can be applied to a rotary plunger pump or the like.

3 and 4, the center hole 50a is also provided.
Oil seal, the oil seal and the O-ring 70
Lubricating oil may be sealed in the gap between them. Also, the first
The brake device shown in the embodiment is an example, and is not limited to this brake device.
2 and 3, an O-ring 70 as a seal member may be arranged in the casing 50 so as to slide between the O-ring 70 and the inner rotor 52. In this case, the O-ring 70 does not rotate, but the brake fluid can adhere to the O-ring 70 by rotating the drive shaft 54. That is, since the O-ring 70 rotates relatively to the drive shaft 54, the O-ring 7
The same effect as when 0 is provided on the inner rotor 52 side can be obtained.

[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, and FIG.
FIG. 3 is a sectional view taken along the line AA of FIG.

FIG. 3A is a schematic view of a rotary pump, and FIG.
FIG. 3A is a sectional view taken along the line BB in FIG.

FIG. 4 is a schematic view of a rotary pump according to a third embodiment.

FIG. 5A is a schematic view of a conventional rotary pump, and FIG. 5B is a cross-sectional view of FIG.

[Explanation of symbols]

Reference numeral 10: rotary pump, 11: motor, 50: casing, 51: outer rotor, 52: inner rotor, 5
Reference numeral 3 represents a gap, 54 represents a drive shaft, 60 represents a suction port, 62 represents a discharge port, 70 represents an O-ring, 80 represents a rotating plate, 100a, 100.
b: gap.

Claims (7)

[Claims] A rotary part (51, 52) that rotates around a drive shaft (54), and an opening (50a) into which the drive shaft (54) is fitted, and the rotary part (51, 52). ) Casing (5)
0), and formed on the casing (50) and the rotating part (5).
A suction port (60) for sucking a fluid into the casing (50);
1, 52), and a discharge port (61) for discharging the fluid from the suction port (60) by a rotational motion of the rotating unit (51, 52). And a seal member (70) that rotates relative to the drive shaft (54) to prevent the fluid from leaking outside through the opening (50a), The rotary pump according to claim 1, wherein the seal member (70) is provided eccentrically with respect to the drive shaft (54). 2. An outer rotor (5) having an inner tooth portion (51a) on an inner periphery thereof.
1) and an inner rotor (52) formed inside the outer rotor (51) and having external teeth (52a) on the outer periphery. The seal member (70) includes the inner rotor (52). 5
2. The rotary pump according to claim 1, wherein the rotary pump is attached to 2). 3. A rotating plate (80) that rotates together with the rotating parts (51, 52) on a side of the drive shaft (54) closer to the opening (50a) than the rotating parts (51, 52).
The rotary pump according to claim 1, wherein the seal member (70) is attached to the rotary plate (80). 4. A rotary part (51, 52) that rotates around a drive shaft (54), and an opening (50a) into which the drive shaft (54) is fitted. ) Casing (5)
0), and formed on the casing (50) and the rotating part (5).
A suction port (60) for sucking a fluid into the casing (50);
1, 52), and a discharge port (61) for discharging the fluid from the suction port (60) by a rotational motion of the rotating unit (51, 52). ), Wherein the seal member is provided between the drive shaft (54) and the casing (50) to prevent the fluid from leaking outside the opening (50a). 70), wherein the seal member (70) is provided so as to be inclined with respect to a plane perpendicular to the drive shaft (54). 5. An oil seal is provided in the opening (50a), and lubricating oil is provided between the oil seal and the seal member (70).
The rotary pump according to any one of the above. 6. The rotary pump according to claim 1, wherein the sealing member is an O-ring (70). 7. A brake hydraulic pressure generating means (1 to 3) for generating a brake hydraulic pressure based on a pedaling force, and a braking force generating means (4, 5) for generating a braking force on wheels based on the brake hydraulic 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 6, 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).