JP2001310730A - Pump device and brake device - Google Patents

Abstract

PROBLEM TO BE SOLVED: To provide a pump device and a brake device with a simple structure capable of adequately performing various control such as anti-skid control. SOLUTION: The pump device 47 comprises a motor 45 fixed to one end of a cylinder block 61, and a pair of reciprocating piston pumps as returning pumps 41a and 41b and one rotary pump as a pressing pump 43 disposed inside the cylinder block 61. In an inner hole 63 in the cylinder block 61, the reciprocating piston pumps 41a and 41b for returning brake oil sequentially from the motor 45 side to a master cylinder 1 side and circulating it, a second rolling shaft seal member 65 for fluid-tightly preventing the brake oil from leaking, and a rotary pump 43 for supplying the brake oil to a liquid chamber 1a of the master cylinder 1 to increase master cylinder pressure are provided in this order from the motor 45 side.

Description

DETAILED DESCRIPTION OF THE INVENTION

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a pump device for sucking and discharging a fluid and a brake device using the pump device.

[0002]

2. Description of the Related Art Conventionally, various types of pumps, solenoid valves, and the like have been used as brake devices for controlling anti-skid control (ABS control), brake assist control (BA control), traction control (TRC control), and the like. Equipped brake hydraulic circuits have been developed.

[0003] For example, Japanese Patent Application Laid-Open No. Hei 9-39765 discloses that when the slip of the drive wheel becomes excessive, a low hydraulic pump is driven to raise the pressure of the suction passage of the hydraulic pump to a level higher than the atmospheric pressure. A technique for increasing a rising speed of a hydraulic pressure of a wheel brake is described. However, in the case of this technique, there is a problem of the sound of the pressurizing pump in pressurizing control during the brake operation.

In order to control the pressurization during the brake operation, pressurization by a negative pressure booster control and pressurization by introducing a pressurization control hydraulic pressure to the master cylinder are considered to increase the hydraulic pressure. However, the latter is advantageous in that the device is simple.

[0005]

However, when the pressurizing assist control in the normal brake area is performed, the system in which the master cylinder side is pressurized by the piston pump does not generate sound or noise during operation.
There is a problem that vibration occurs.

In a brake hydraulic circuit having both a reciprocating piston pump and a quiet rotary pump, a motor and a motor driving device (having a relay, a transistor, and the like) for driving each pump are respectively provided. Required, and the equipment becomes complicated. Therefore, there is a problem that the number of manufacturing steps increases and the manufacturing cost increases.

SUMMARY OF THE INVENTION The present invention has been made to solve the above-mentioned problems, and an object of the present invention is to provide a pump device and a brake device which are capable of suitably performing various controls such as anti-skid control, and which have simple configurations. Is to provide.

[0008]

Means for Solving the Problems and Effects of the Invention (1) According to the first aspect of the present invention, the brake device recirculates brake fluid supplied to braking force generating means (for example, a wheel cylinder) for generating a braking force on wheels. A return pump for releasing the brake fluid and a pressure pump for supplying the brake fluid for increasing the brake fluid pressure are provided to a brake fluid pressure generating means (for example, a master cylinder) for generating a brake fluid pressure in accordance with the driver's pedaling force. .

In particular, in the present invention, since the return pump and the pressing pump are driven by one motor, the number of motors and motor driving devices to be used is reduced as compared with the related art.
The device configuration can be simplified. Thereby, the manufacturing process can be simplified and the manufacturing cost can be greatly reduced.

(2) According to the second aspect of the present invention, a return pump is provided for each of the two brake hydraulic circuits, so that the brake fluid can be recirculated for each system. (3) The invention of claim 3 shows an application of the return pump. Here, the return pump returns the brake fluid released to the reservoir to the master cylinder due to, for example, depressurization of the wheel cylinder, and returns the brake fluid to the master cylinder. Used to perform skid control.

(4) In the invention of claim 4, the return pump is a non-self-priming pump. The non-self-priming pump can operate the pump in a state where there is a back pressure, and can be manufactured at low cost. (5) In the invention of claim 5, the pressing pump is a self-priming pump. This self-priming pump can operate the pump without back pressure (atmospheric pressure).

(6) In the invention of claim 6, the return pump is a reciprocating piston pump. Since the reciprocating piston pump has a simple structure, it has a necessary function for circulating the brake fluid and has an advantage that the manufacturing cost is low. In particular, when emergency braking control such as anti-skid control is performed, there is no problem even if there is some pulsation, so it is desirable to use this reciprocating piston pump.

(7) According to a seventh aspect of the present invention, the pressing pump is a rotary pump. This rotary pump has the advantage that pulsation of brake fluid is small and quietness is high.
Therefore, when increasing the master cylinder pressure, it is preferable to use this rotary pump, because if there is pulsation, the driver tends to feel uncomfortable.

(8) The invention of claim 8 exemplifies a rotary pump. As the rotary pump, a well-known trochoid pump, internal gear pump, external gear pump, or vane pump can be used. The trochoid pump has a small number of parts and is low in cost. In addition, high output can be achieved by pressure balance,
Excellent quietness.

The internal gear pump has a small number of parts, is easy to process gears, and is inexpensive. In addition, high output can be achieved by pressure balance, and the quietness is excellent. The external gear pump can be reduced in axial length, and is excellent in quietness. The vane pump does not require high-precision gear machining and is excellent in quietness.

(9) According to the ninth aspect of the present invention, since the return pump and the pressing pump are integrally assembled in one block, the configuration of the pump device becomes compact. (10) The invention of claim 10 exemplifies the arrangement of each component. Here, on one side of the motor in the axial direction, that is, on one side of the motor in the axial direction of the motor,
From the motor side, a return pump and a pressing pump are arranged in this order.

In this configuration, since both pumps are arranged on one side of the motor, the housing such as the cylinder block is one.
It only needs one. (11) The invention of claim 11 exemplifies the arrangement of each component, and here, on one side as viewed in the axial direction of the motor, that is, on one side of the motor in the axial direction of the motor,
From the motor side, a pressing pump and a return pump are arranged in this order.

In this configuration, since both pumps are arranged on one side of the motor, the housing such as the cylinder block can be mounted on one side.
It only needs one. Also, assembly from one side is possible, and the manufacturing operation can be simplified. (12) The twelfth aspect of the invention exemplifies the arrangement of each component. Here, one side of the motor in the axial direction of the motor, that is, one side of the motor in the axial direction of the motor,
A return pump is arranged, and a pressing pump is arranged on the other side.

In the present invention, the configuration can be easily changed, for example, by adding a pressing pump to the motor and the return pump. (13) According to the thirteenth aspect, the arrangement of the first rotary shaft sealing member for sealing the brake fluid is shown.

Here, since the first rotary shaft sealing member for liquid tightness is arranged between the motor and the pressing pump, the brake fluid does not leak from the suction side of the pressing pump to the motor side. (14) In the fourteenth aspect, the arrangement of the first rotary shaft sealing member for sealing the brake fluid is shown.

In this case, the liquid-tight second rotary shaft sealing member is disposed between the return pump and the pressing pump. Therefore, the suction side of the pressing pump is connected to the motor side via the return pump. No leakage of brake fluid to (15) In the invention of claim 15, the rotary shaft of the return pump and the rotary shaft of the pressing pump are coaxially arranged, so that the configuration of the pump device can be simplified.

(16) In the invention of claim 15, since the rotating shaft of the return pump and the rotating shaft of the pressing pump are integrated, a connecting mechanism for both rotating shafts is unnecessary, and the number of bearings can be reduced. In addition, there is an advantage that the rotating shaft is strong. (17) According to the seventeenth aspect, the rotary shaft of the return pump and the rotary shaft of the pressing pump are separate bodies, and both rotary shafts are connected by a connecting mechanism and rotate integrally. Therefore, it is easy to assemble the pump device.

(18) According to the eighteenth aspect of the invention, the two rotating shafts are connected by a connecting mechanism (for example, a spline shaft or a two-plane width) that can move in the axial direction, so that the degree of freedom of connection is high.
When the load applied to both rotating shafts is large or when the load is applied from an unexpected direction, there is an advantage that it is difficult to break down.

(19) According to the nineteenth aspect, since the eccentric portion is provided on the rotating shaft of the return pump, the eccentric portion (having a different length from the center of the shaft to the outer periphery) is also rotated by the rotation of the rotating shaft. . Therefore, the rotation of the eccentric portion can directly or indirectly move the piston of the return pump.

(20) In the twentieth aspect of the present invention, since the rotation axis of the return pump and the rotation axis of the pressing pump are arranged non-coaxially, the degree of freedom of design in the pump device (when each pump is arranged) Degree of freedom) is increased. (21) According to a twenty-first aspect of the present invention, the rotating shaft of the return pump and the rotating shaft of the pressing pump are non-coaxially arranged and connected via a transmission mechanism (such as a gear for transmitting a driving force). I have.
Therefore, the pumps can be rotated at different rotational speeds by using gears or the like, so that the capacity of each pump can be set freely.

(22) According to the invention of claim 22, the load direction of the piston of the return pump and the load direction of the pressing pump are not the same (for example, substantially perpendicular). Therefore, the force applied to the rotating shaft and the force applied to the bearing can be reduced as compared with the case where the load direction is the same. Thereby, in the rotary pump,
Its characteristics are stabilized, rotation is smooth, durability is improved, and failures are reduced.

(23) The brake device according to the twenty-third aspect of the present invention further comprises a braking force generating means (for example, a wheel cylinder).
And a brake fluid pressure circuit having two brake fluid pressure generating means (master cylinder), and a brake fluid pressure circuit independent of the brake fluid pressure circuit (for example, a pressing pump and a solenoid valve arranged in parallel with the pump).

Therefore, by driving the above-mentioned pump device, various controls can be performed by adjusting the brake fluid pressure during braking, for example. (24) The invention of claim 24 exemplifies the control by the multi-system brake hydraulic circuit. Here, control for adjusting the wheel cylinder pressure in accordance with, for example, the rotation state of the wheel, such as anti-skid control, can be performed. Further, for example, control for increasing the master cylinder pressure according to the driver's depression force, such as brake assist control, can be performed.

(25) According to the twenty-fifth aspect of the present invention, the number of bearing members used can be reduced by providing a bearing member that supports both the load of the return pump and the load of the pressing pump. (26) According to the twenty-sixth aspect, one bearing member that supports both the load of the return pump and the load of the pressing pump is brought into contact with both the block of the return pump and the block of the pressing pump. With this configuration, there is an advantage that the center axes of both blocks can be aligned, and the vibrations of both pumps can be reduced.

(27) In the invention of claim 27, two reciprocating piston pumps and one rotary pump are driven by one motor. Therefore, similarly to the first aspect, the number of motor driving devices such as motors and gears to be used is reduced as compared with the related art, and the device configuration can be simplified. Thereby, the manufacturing process can be simplified and the manufacturing cost can be greatly reduced.

(28) In the invention of claim 28, since the two reciprocating piston pumps and the one rotary pump are integrally assembled in one block, the pump device can be made compact. As the rotary pump, a trochoid pump, an internal gear pump, an external gear pump, a vane pump, or the like can be employed as in the above-described brake device.

[0032]

DETAILED DESCRIPTION OF THE PREFERRED EMBODIMENTS An embodiment (embodiment) of a pump device and a brake device according to the present invention will be described below with reference to the drawings. First Embodiment a) First, a vehicle brake device using the pump device of the present embodiment will be described.

This vehicle brake system includes well-known anti-skid control (ABS control), brake assist control (BA control), traction control (TRC), turning control (VSC) for controlling vehicle behavior during turning, and the like. This is a vehicle brake device that can be performed.

As shown in FIG. 1, the vehicle brake device has a tandem type master cylinder 1, and a brake pedal 5 is connected to the master cylinder 1 via a brake booster 3. A master reservoir 7 is connected to the master cylinder 1, and a hydraulic control circuit 9 that is configured by, for example, two hydraulic systems of X piping (diagonal piping) and adjusts a brake hydraulic pressure is connected to the master cylinder 1. , The first hydraulic pipe 9a and the second hydraulic pipe 9
b.

In the hydraulic control circuit 9, the first hydraulic piping 9
Through a, the wheel cylinder 11 of the front right (FR) wheel and the wheel cylinder 12 of the rear left (RL) wheel communicate with each other. The wheel cylinder 13 of the rear right (RR) wheel and the wheel cylinder 14 of the front left (FL) wheel are connected to each other via the second hydraulic pipe 9b.

In the first hydraulic pipe 9a, a well-known pressure increasing control valve 16 and a pressure reducing control valve 21 for controlling a hydraulic pressure of the wheel cylinder 11 of the FR wheel, and a hydraulic pressure of the wheel cylinder 12 of the RL wheel are controlled. Pressure-reducing control valve 17 and pressure-reducing control valve 22 are provided.
The pressure increase control valve 18 and the pressure reduction control valve 23 for controlling the oil pressure of the wheel cylinder 13 of the R wheel, and the pressure increase control valve 19 and the pressure reduction control valve 24 for controlling the oil pressure of the wheel cylinder 14 of the FL wheel Is provided.

Here, the first hydraulic pipe 9a will be described. In the first hydraulic pipe 9a, a reservoir 26 for temporarily storing brake oil discharged from each of the pressure reduction control valves 21 and 22 is provided.
A return pump 41a, which is a hydraulic pump, is provided for pumping and circulating the brake oil to the hydraulic path 28. The discharge path of the brake oil from the return pump 41a is provided with a pulsation of the internal hydraulic pressure. A damper 31 for suppressing and an orifice 31a are provided.

On the other hand, in the second hydraulic pipe 9b, similarly to the first hydraulic pipe 9a, pressure increasing control valves 18, 19, pressure reducing control valves 23, 24, a reservoir 27, a return pump 41b, a damper 32, and the like. Are provided at similar locations. In the present embodiment, the hydraulic path 5 from the master reservoir 7 to the master cylinder (particularly, the liquid chamber 1a on the brake pedal 5 side) 1
1 is provided with a pressing pump 43 for pumping brake oil to the master cylinder 1 when increasing the pressure of the liquid chamber 1a. An electromagnetic valve 53 is provided in parallel with the pressing pump 43 to switch between two positions of a communication valve and a linear valve (a valve whose opening is changed according to the current to control the pressure).

Particularly, in this embodiment, as will be described in detail later, 1
The two return valve pumps 41 by two motors 45
The pump device 47 is configured so that a, 41b and one pressing pump 43 are driven. With the above-described configuration, when the motor 45 is turned on and the two return pumps 41a and 41b are driven, the reservoirs 26 and 27
Can be returned to the master cylinder 1 side, and the wheel cylinder pressure can be arbitrarily adjusted by the pressure increase control valves 16 to 19 and the pressure reduction control valves 21 to 24. Thereby, control such as anti-skid control, traction control, and turning control can be suitably performed.

When the motor 45 is turned on and the pressing pump 43 is driven, the master cylinder pressure can be arbitrarily increased according to the depression of the brake pedal 5 (or regardless of the depression). Thereby, control such as brake assist control can be suitably performed.

The first hydraulic piping 9 from the master cylinder 1
A pressure sensor 57 for detecting a master cylinder pressure is provided in a hydraulic path 55 to b, and a pedaling force sensor 59 for detecting a pedaling force is provided on a rod 5 a of the brake pedal 5. b) Next, the pump device 47 used in the above-described vehicle brake device will be described with reference to the cross-sectional view of FIG.

As shown in FIG. 2, the pump device 4 of this embodiment
7, a motor 45 is fixed to one end (lower side in FIG. 2) of a cylinder block 61 serving as a housing, and a pair of reciprocating piston pumps, which are return pumps 41a and 41b, and a pressing pump are provided inside the cylinder block 61. 43, in which one rotary pump is arranged.

That is, the inner hole 6 of the cylinder block 61
3, a reciprocating piston pump 41a, 41b for returning and circulating the brake oil to the wheel cylinders 11 to 14 in order from the motor 45 side, and a second rotary shaft seal member 65 which is liquid-tight so that the brake oil does not leak. And a rotary pump 43 (which is a trochoid pump) for supplying brake oil to the master cylinder 1 to increase the master cylinder pressure.

The motor 45 and the reciprocating piston pump 41
a, 41b and the rotary pump 43 have the same rotation axis, and a shaft (motor shaft) 66 of the motor 45 is provided.
Rotates, the piston pump side shaft 67, which is a member integral with the motor shaft 66, rotates to drive the reciprocating piston pumps 41a and 41b, and at the same time, the rotation connected to the piston pump side shaft 67 via the connection mechanism 69. When the pump-side shaft 68 rotates, the rotary pump 4
3 is driven.

Hereinafter, each component will be described in detail. The reciprocating piston pumps 41a and 41b are non-self-priming pumps (requiring back pressure),
1 are arranged in a straight line so as to be perpendicular to the axis center (vertical direction in FIG. 2) and substantially symmetric with respect to the axis center.

That is, the piston pump side shaft 67 is disposed at the center of the shaft, and the piston pump side shaft 67
Is provided with an eccentric part 71. And the eccentric part 7
The piston bearing 73 is disposed in contact with the outer periphery of the piston 1, and the left and right pistons 75 a and 75 b are disposed in contact with the outer periphery of the piston bearing 73. That is, a pair of cylinders 79a, 7 extending in the left-right direction (coaxially) in FIG.
Pistons 75a and 75b are arranged inside 9b.

The eccentric portion 71 is cut off on one side of the piston pump side shaft 67 so as to be asymmetric with respect to the axis center, and the distance from the axis center to the outer periphery is different.
Accordingly, when the piston pump-side shaft 67 rotates, the piston bearing 73 that contacts the eccentric portion 71 moves right and left in FIG. 2, and the pistons 75a and 75b that contact the outside of the piston bearing 73 also move right and left.

Also, communication passages 81a and 81b through which brake oil flows are provided inside the pistons 75a and 75b, and check valves 83a and 83b are provided outside the communication passages 81a and 81b (outside the shaft center). Is provided. The check valves 83a and 83b are composed of balls 85a and 85b for opening and closing the communication passages 81a and 81b, and springs 87a and 87b for urging the balls 85a and 85b inward (axial center side). In the cylinders 79a and 79b, springs 89a for urging the pistons 75a and 75b toward the shaft center are provided.
89b is also arranged.

Further, the motor 45 of the cylinder block 61
Inflow holes 91a and 91b through which brake oil flows are provided in communication with the shaft center sides (inside) of the communication passages 81a and 81b, and communication passages 81a and 8b are provided on the opposite side of the motor 45.
Outflow holes 93a, 93b through which the brake oil flows out are provided outside of 1b in communication with the check valves 83a, 83b. The outflow holes 93a and 93b are provided with the same check valves 95a and 95b as described above.

A motor bearing 77 is disposed on the piston pump side shaft 67 on the motor 45 side. The rotary pump 43 is configured as a self-priming pump (operable even when the back pressure is atmospheric pressure),
Cylindrical opening 6 formed on the opposite side of the first motor 45
3.

In the rotary pump 43, a rotary pump side shaft 68 is disposed at the center of the shaft, and a needle bearing 101,
103 are arranged in two rows. An internal gear structure 109 (having a trochoid pump structure) is formed between the cylindrical cylinder top 105 and the cylinder end 107 (one end of which is closed) in order to suck and discharge brake oil. Have been.

3, the inner rotor 111 and the outer rotor 113 mesh with each other with a predetermined gap 115 inside the casing 120, as shown in FIG. Things. As a result, the brake oil is sucked into the gap 115 from the inflow hole 117 (FIG. 2) through the half-moon-shaped concave portion 119 (provided on the cylinder side), and (also provided on the cylinder side). The liquid is discharged from the outflow hole 123 (FIG. 2) through the half-moon-shaped recess 121.

As shown in FIG. 2, the piston pump side shaft 67 and the rotary pump side shaft 68
Are connected by a so-called two-plane width. In other words, a plate-shaped convex portion 67a that protrudes from the eccentric portion 71 is provided at the axial end of the piston pump-side shaft 67 (upper part in the figure), and the axial end of the rotary pump-side shaft 68 (see FIG. A groove-shaped concave portion 68a is provided on the lower side), and the piston pump-side shaft 67 and the rotary pump-side shaft 68 move in the axial direction by fitting the convex portion 67a and the concave portion 68a with two widths. It is movable and coaxially rotatable. Incidentally, connection by a spline shaft is also possible.

Further, the rotary pump side shaft 68
Is an oil seal for preventing the brake oil from leaking from the rotary pump 43, which is at a high pressure, to the reciprocating piston pumps 41a, 41b at a low pressure.

The reciprocating piston pumps 41a, 41
As shown schematically in FIG. 4A, b and the rotary pump 43 are arranged such that the load applied to the rotating shaft is at a right angle. In other words, the rotating shaft composed of the piston pump-side shaft 67 and the rotary pump-side shaft 68 receives a load from the left and right directions in FIG. A load is applied from a certain discharge side (upper side in the figure) to a lower side in the figure. Thereby, the reciprocating piston pumps 41a, 41b
Is perpendicular to the load direction of the rotary pump 43.

C) With the above-described configuration, the pump device 47 of this embodiment operates as follows. For example, when it is necessary to increase the wheel cylinder pressure or the master cylinder pressure in accordance with the anti-skid control or the brake assist control, the motor 45 of the pump device 47 is energized to drive the motor 47.

This energization causes the motor shaft 66 of the motor 47 to rotate, so that the piston pump side shaft 67 integral with the motor shaft 66 also rotates, and at the same time, the rotary pump side shaft connected to the piston pump side shaft 67. 68 also rotates. That is, the piston pump side shaft 67 and the rotary pump side shaft 68
Rotate synchronously in the same direction as the same rotation axis.

When the piston pump-side shaft 67 rotates, the eccentric portion 71 rotates.
1 according to the rotation of the piston 75a in the left-right direction of FIG.
75b moves right and left. That is, the portion of the piston bearing 73 that is in contact with the outer periphery of the eccentric portion 71 on the non-notched side (the left side in FIG. 2) is pressed by the non-notched side of the eccentric portion 71 and moves to the left side in FIG. The portion of the portion 71 that is in contact with the outer periphery on the cutout side (the right side in FIG. 2) is pressed by the spring 89b and moves to the left side in FIG. Therefore, both pistons 75
a and 75b move to the left side together. In addition, the eccentric part 7
When 1 rotates by 180 degrees, this time, conversely, both pistons 75
a and 75b move to the right side together. Accordingly, by repeating this operation, the pistons 75a and 75b repeatedly move in the left-right direction.

As a result, in the reciprocating piston pump 41a on the left side of FIG.
Flows to the right through the inflow hole 91a (flow path A) into the reciprocating piston pump 41a,
a, flows into the pump chamber 87a through the check valve 83a. Also, when the piston 75a moves to the left, it flows out of the outflow hole 93a (flow path B). Similarly, in the reciprocating piston pump 41b on the right side of FIG.
It flows into the reciprocating piston pump 41b from (flow path C) through the communication path 81b, and flows out from the outflow hole 93b (flow path D).

By the above-described operation, the brake oil is pumped from the reservoirs 26 and 27 and is sent to the hydraulic path 28 under pressure. On the other hand, when the rotary pump side shaft 68 rotates, the inner rotor 111 rotates and the outer rotor 113 also rotates, and the operation of the inscribed gear structure 109 causes the brake oil to be supplied to the liquid chamber 1 a of the master cylinder 1.
To pump.

That is, when the rotary pump-side shaft 68 rotates, the brake fluid flows from the inflow hole 117 (flow path E) into the half-moon-shaped concave portion 119, It flows out from the outflow hole 123 (flow path F) through the concave part 121 of the shape.

By the above-described operation, the brake oil is sucked from the master reservoir 7 and sent to the liquid chamber 1a of the master cylinder 1 under pressure, so that the master cylinder pressure increases. d) Next, the effect of this embodiment with the above-described configuration will be described. In this embodiment, a pair of reciprocating piston pumps 41a,
41b and one rotary pump 43 and one motor 4
5, the motor 45 and the motor driving device are required to be a single set, and the device configuration can be simplified. Thereby, the manufacturing process can be simplified, which contributes to cost reduction.

A pair of reciprocating piston pumps 41a,
Since the rotary pump 43b and the rotary pump 43 are provided in one cylinder block 61, the apparatus can be made compact. Further, the piston pump-side shaft 67 and the rotary pump-side shaft 68 are formed separately, and they are connected to each other with a two-plane width, so that the pump device 47 can be easily assembled.

In addition, the reciprocating piston pumps 41a, 41
Since the direction of the load applied to the rotary shaft from b is perpendicular to the direction of the load applied to the rotary shaft from the rotary pump 43, no excessive load is applied to the rotary shaft in only one direction.
Rotation is stable and durability is improved.

As shown in FIG. 4B, the right and left reciprocating piston pumps 41a 'and 41b' are arranged at an angle of 120 degrees with respect to the load direction of the rotary pump 43 '. The resultant force of the load applied to the rotary shaft from the rotary shaft 41b 'and the load applied to the rotary shaft from the rotary pump 43' is smaller than that of the first embodiment, which is more preferable.

E) Next, another example in which the coupling mechanism of the shaft is changed will be described with reference to FIG. In the example shown in FIG. 5A, a protrusion 131a is provided on the distal end side (upper part of the figure) of the piston pump side shaft 131, and a concave part 133a is provided on the distal end side (lower part of the figure) of the rotary pump side shaft 133. The projection 131a and the recess 133a are fitted to each other to form a connection mechanism 134 having a so-called two-plane width.

Here, the rotary pump side shaft 133 is used.
An eccentric portion 135 similar to the above is provided at the connection portion of
Outside the eccentric portion 135, a piston bearing 137 is provided.
And reciprocating piston pumps 139a and 139b. In this example, the connection mechanism 13 is different from that of the first embodiment.
4 has the advantage that the strength is large.

In the example shown in FIG. 5B, a concave portion 141 is provided on the tip side (upper side of the figure) of the piston pump side shaft 141.
a is provided, and a convex portion 143a is provided on the tip side (lower side in the figure) of the rotary pump side shaft 143, and the concave portion 14a is provided.
1a and the convex portion 143a are fitted to each other, so-called 2
A connecting mechanism 154 having a surface width is formed.

Here, the piston pump side shaft 14
An eccentric portion 145 similar to that described above is provided at the connection portion 1, that is, a portion where the concave portion 141 a is provided, and a piston bearing 147 and reciprocating piston pumps 149 a and 149 b are arranged outside the eccentric portion 145. .

This embodiment has an advantage over the first embodiment in that the strength of the connecting mechanism 154 is higher. In the example shown in FIG. 5C, the shaft on the piston pump side and the shaft on the rotary pump side are not separate bodies but an integral shaft 151. And the reciprocating piston pump 153
a, eccentric part 155 for operating 153b
It is provided in the middle of 51.

In this example, there is an advantage that the shaft can be composed of one part and the number of parts can be reduced. (Embodiment 2) Next, Embodiment 2 will be described, but the description of the same parts as in Embodiment 1 will be omitted or simplified.

As shown in FIG. 6, the pump device 2 of this embodiment
01 is the motor 20 inside the cylinder block 203.
5 side, a motor bearing 207, a piston bearing 209, and a pair of reciprocating piston pumps 211a,
211b, a shaft bearing 213, a first rotating shaft seal member 215, and a rotary pump 217 are arranged, and a shaft 219 is arranged at the axis center of the cylinder block 203.

Hereinafter, each configuration will be described. In this embodiment, a single shaft 219 in which the motor shaft, the piston pump side shaft, and the rotary pump side shaft of the first embodiment are integrated is used as the rotating shaft.

An eccentric portion 221 substantially similar to that of the first embodiment is provided in the middle of the shaft 219, and a piston bearing 209 is in contact with the outside of the eccentric portion 211. The pair of reciprocating piston pumps 211a and 211b
Is a non-self-priming pump, which is the same as in the first embodiment.

Therefore, by the rotation of the shaft 219,
As the pistons 223a and 223b slide left and right, the brake oil is sucked from the flow path A (on the reservoir side) and discharged to the flow path B (on the hydraulic path 28 on the master cylinder side), and The brake oil can be sucked from the flow path C and discharged to the flow path D (of the hydraulic path 29 on the master cylinder side).

The rotary pump 217 is a self-priming pump, and is a trochoid pump similar to that of the above embodiment.
Accordingly, the rotation of the shaft 219 causes the internal gear mechanism 225 to operate, thereby (on the master reservoir side).
The brake oil can be sucked in from the flow path E and discharged to the flow path F (on the master cylinder side).

In this embodiment, the same effects as those of the first embodiment are obtained, and the shaft 219 is integrated. The shaft 219 is connected to both the motor bearing 207 and the shaft bearing 213 which are in contact with the cylinder block 203. , 213, the structure is simple, the deflection of the shaft 219 is small,
Moreover, there is an advantage that the rotation is stable and the vibration is small.

Further, the outer ring 2 of the shaft bearing 213
13a includes a piston pump block 203a (a part of the cylinder block 203) and an inner block 218.
Of both the rotary pump blocks 218a, so that both blocks 203a, 218
There is an advantage in that the center axis between a can be aligned and both pump vibrations can be reduced.

(Embodiment 3) Next, Embodiment 3 will be described, but the description of the same parts as in Embodiment 1 will be omitted or simplified. As shown in FIG. 7, the pump device 30 of the present embodiment
1 is a motor 305 inside the cylinder block 303.
From the side, a motor bearing 307, a piston bearing 309, and a pair of reciprocating piston pumps 311a,
11b, first rotary shaft seal member 313, rotary pump 3
15 are arranged.

Hereinafter, each configuration will be described. In the present embodiment, a piston pump-side shaft 319 integrated with the motor shaft 317 is used as the rotation shaft, as in the first embodiment, and the rotary pump-side shaft 321 has a two-plane width on the piston pump-side shaft 319. They are connected by a connection mechanism 322.

An eccentric portion 323 similar to that of the first embodiment is provided on the piston pump side shaft 319, and a piston bearing 309 is in contact with the outside of the eccentric portion 323. The pair of reciprocating piston pumps 311a, 311b
Is a non-self-priming pump, which is the same as in the first embodiment.

Therefore, the rotation of the piston pump side shaft 319 integral with the motor shaft 317 causes the pistons 325a and 325b to slide left and right,
Brake oil is sucked in from the channel A (on the reservoir side) and discharged to the channel B (on the master cylinder side), and brake oil is sucked in from the channel C (on the reservoir side) (on the master cylinder side). It can be discharged to the flow path D.

The rotary pump 315 is a self-priming pump, which is a so-called circumscribed gear pump different from the first embodiment. When the two gears 327a and 327b mesh with each other and rotate in the casing 329 as illustrated in FIG.
The brake oil sucked from 1 enters the tooth groove, the volume enclosed between the casing 329 and the tooth moves to the discharge side, and is discharged from the outlet hole 333.

In this embodiment, the rotary pump side shaft 321 connected to the piston pump side shaft 319 is the rotation shaft of the first gear 327a, and the second gear rotating in mesh with the first gear 327a in parallel therewith. The rotation shaft 335 of 327b is provided.

Incidentally, around the rotation shafts 321 and 335,
Needle bearings 337a to 337c are arranged in two rows. Therefore, the piston pump side shaft 3
When the rotary pump-side shaft 321 is rotated by the rotation of the rotation of the rotary shaft 19, the first gear 327a rotates and the second gear 327b rotates, so that the brake oil is sucked from the flow path E (on the master reservoir side). It can be discharged to the flow path F (on the master cylinder side).

In this embodiment, the same effects as in the first embodiment can be obtained. (Embodiment 4) Next, Embodiment 4 will be described, but the description of the same parts as in Embodiment 1 will be omitted or simplified.

As shown in FIG. 9, the pump device 4 of this embodiment
01 is the motor 40 inside the cylinder block 403.
In order from the fifth side, a motor bearing 407, a piston bearing 409, and a pair of reciprocating piston pumps 411a,
411b, transmission mechanism 413, first rotating shaft seal member 41
5. A rotary pump 417 is provided.

Hereinafter, each configuration will be described. In the present embodiment, a piston pump-side shaft 421 integral with the motor shaft 419 is used as a rotating shaft, as in the first embodiment, and the piston pump-side shaft 421 and the rotary pump-side shaft 423 are connected to the transmission mechanism 4.
13 are connected.

The transmission mechanism 413 is attached to a first gear 413a attached to the distal end side (upper side in the figure) of the piston pump side shaft 421, and to the distal end side (lower side in the figure) of the rotary pump side shaft 423. Second gear 413b
Are engaged with each other to transmit a driving force, whereby the rotation speed of the rotary pump side shaft 423 can be changed with respect to the rotation speed of the piston pump side shaft 421.

An eccentric portion 425 similar to that of the first embodiment is provided on the piston pump-side shaft 421, and a piston bearing 409 is in contact with the outside of the eccentric portion 425. The pair of reciprocating piston pumps 411a, 411b
Is a non-self-priming pump, which is the same as in the first embodiment.

Therefore, the rotation of the piston pump side shaft 421 integral with the motor shaft 419 causes the pistons 427a and 427b to slide left and right,
Brake oil is sucked in from the channel A (on the reservoir side) and discharged to the channel B (on the master cylinder side), and brake oil is sucked in from the channel C (on the reservoir side) (on the master cylinder side). It can be discharged to the flow path D.

The rotary pump 417 is a self-priming pump, and is a trochoid pump similar to the above embodiment.
Therefore, when the rotation of the piston pump-side shaft 421 is transmitted to the rotary pump-side shaft 423 via the transmission mechanism 413, the rotation of the rotary pump-side shaft 423 activates the internal gear mechanism 429. Thereby, the brake oil is sucked from the flow path E (on the master reservoir side),
It can be discharged to the flow path F (on the master cylinder side).

In this embodiment, the same effects as those of the first embodiment can be obtained, and the rotation speed of the piston pump side shaft 421 and the rotation speed of the rotary pump side shaft 423 can be made different by the transmission mechanism 413. The discharge capacity required for each of the pumps 411a, 411b, and 417 can be arbitrarily set.

(Embodiment 5) Next, Embodiment 5 will be described, but the description of the same parts as in Embodiment 1 will be omitted or simplified. As shown in FIG. 10, the pump device 5 of the present embodiment
01 is the motor 50 inside the cylinder block 503.
The motor bearing 507, the first rotary shaft seal member 509, the rotary pump 511, the second rotary shaft seal member 513, the shaft bearing 515, the piston bearing 517, and the pair of reciprocating piston pumps 519 are arranged in this order from the fifth side.
a, 519b are arranged.

Hereinafter, each configuration will be described. In the present embodiment, a rotary pump-side shaft 523 (which is a rotation axis of the rotary pump 511) is connected to a distal end side (upper side in the drawing) of the motor shaft 521 by a coupling mechanism 529 having a two-plane width.
It is connected by. This rotary pump side shaft 523
Is composed of a member (rod) integral with the piston pump-side shaft 525 (which is the rotation axis of the reciprocating piston pumps 519a and 519b). The rotation of the motor shaft 521 causes the rotary pump-side shaft 523 and the piston pump-side shaft 525 to rotate. They rotate together.

The piston pump side shaft 525 is provided with an eccentric portion 527 substantially similar to that of the first embodiment, and the piston bearing 51 is provided outside the eccentric portion 527.
7 is in contact. This rotary pump side shaft 523
The rod constituting the piston pump side shaft 525 is supported by the motor bearing 507 and the shaft bearing 515 on the outer periphery, and rotates smoothly.

The pair of reciprocating piston pumps 519
Reference numerals a and 519b denote non-self-priming pumps, which have basically the same configuration as that of the first embodiment. Therefore, the rotation of the motor shaft 521 causes the rotary pump side shaft 5 to rotate.
When the piston 23 and the piston pump side shaft 525 rotate, the pistons 527a and 527b slide left and right, so that the brake oil is sucked from the flow path A (on the reservoir side) and the flow path B (on the master cylinder side). Discharge to
In addition, the brake oil can be sucked from the flow path C (on the reservoir side) and discharged to the flow path D (on the master cylinder side).

The rotary pump 511 is a self-priming pump, and is basically a trochoid pump substantially similar to that of the first embodiment. Therefore, the rotation of the motor shaft 521 is transmitted to the rotary pump side shaft 5 via the connecting mechanism 529.
23, the rotation of the rotary pump-side shaft 523 causes the internal gear mechanism 531 to operate. Thereby, the brake oil can be sucked from the flow path E (on the master reservoir side) and discharged to the flow path F (on the master cylinder side).

In this embodiment, the same effects as in the first embodiment can be obtained, and the rotary pump side shaft 52 can be used.
Since the outer circumference of the rod constituting the shaft 3 and the piston pump-side shaft 525 is supported by the motor bearing 507 and the shaft bearing 515, the rod can be smoothly rotated without any shaft deflection.

Further, since the first rotary shaft seal member 509 and the second rotary shaft seal member 513 provide an oil seal, leakage of brake oil from the rotary pump 511 to the motor 505 side and the rotary pump 511 Of the brake oil from the side to the reciprocating piston pumps 519a, 519b.

As a modification of this embodiment, for example, the second
The rotary shaft seal member 513 may be omitted, or the rotary pump 5 may be omitted.
The positions of the eleventh inflow holes 533 may be provided at different locations (for example, above the drawing along the rotation axis). (Embodiment 6) Next, Embodiment 6 will be described, but the description of the same parts as in Embodiment 1 will be omitted or simplified.

This embodiment is basically the same as the fifth embodiment except that the rotary pump is not a trochoid pump but an external gear pump. That is, as shown in FIG.
In the cylinder block 603, a motor bearing 607, a first rotary shaft seal member 609, a rotary pump 611, a second rotary shaft seal member 613, a shaft bearing 615, a piston bearing 617, and a pair are sequentially arranged from the motor 605 side. Reciprocating piston pumps 619a, 6
19b are arranged.

Hereinafter, each configuration will be described. In the present embodiment, similarly to the fifth embodiment, the (rotary pump 61)
1) is a rotary pump side shaft 623.
They are connected by a connection mechanism 629 having a two-plane width. The rotary pump-side shaft 623 is connected to the (reciprocating piston pump 61
9a, 619b), which is a member (rod) integral with the piston pump side shaft 625, and the rotation of the motor shaft 621 causes the rotary pump side shaft 6 to rotate.
23 and the shaft 625 on the piston pump side rotate integrally.

Further, an eccentric portion 627 is provided on the piston pump side shaft 625, and a piston bearing 617 is in contact with the outside of the eccentric portion 627. The pair of reciprocating piston pumps 519a, 519b
Is a non-self-priming pump, and has basically the same configuration as that of the first embodiment.

Therefore, the rotation of the motor shaft 521 causes the rotary pump side shaft 523 and the piston pump side shaft 525 to rotate, so that the pistons 527a and 527b slide right and left, thereby forming the flow path (on the reservoir side). A sucks brake oil from A and discharges it to flow path B (on the master cylinder side), and (on the reservoir side)
The brake oil can be sucked from the flow path C and discharged to the flow path D (on the master cylinder side).

The rotary pump 611 is a self-priming pump, and is an external gear pump basically similar to that of the third embodiment. Accordingly, the rotation of the motor shaft 621 is transmitted to the rotary pump side shaft 6 via the coupling mechanism 629.
23, the rotation of the rotary pump-side shaft 623 causes the first gear 629a and the second gear 629b meshing therewith to rotate. Thereby, the brake oil can be sucked from the flow path E (on the master reservoir side) and discharged to the flow path F (on the master cylinder side).

In this embodiment, the same effects as in the fifth embodiment can be obtained. (Embodiment 7) Next, Embodiment 7 will be described, but the description of the same parts as in Embodiment 1 will be omitted or simplified.

This embodiment is different from the first to sixth embodiments.
A motor is located in the center of the pump device. That is,
As shown in FIG. 12, a pump device 701 of this embodiment includes a motor bearing 707, a piston bearing 709, and a pair of motors 703 on a first cylinder block 705 on one side (upper side of the figure) of a motor 703 in order from the motor 703 side. Reciprocating piston pumps 711a and 711b are disposed, and a first rotary shaft seal member 715 and a rotary pump 717 are disposed in the second cylinder block 713 on the other side of the motor 703 (downward in the figure) in order from the motor 703 side. Have been.

Hereinafter, each configuration will be described. In the present embodiment, the motor shaft 719 and the piston pump-side shaft 721 (which is the rotation axis of the reciprocating piston pumps 711a and 711b) are formed as an integral member (rod), and are on the distal end side of the motor shaft 719 (downward in the figure). , The rotary pump-side shaft 723 (which is the rotation axis of the rotary pump 717) is connected by a connecting mechanism 727 having a two-plane width.

Therefore, the motor shaft 719, the piston pump side shaft 721, and the rotary pump side shaft 72
3 and coaxially rotate together. In addition, a motor inner bearing 729 that is in contact with and supports the outer periphery of the motor shaft 719 is disposed outside the coupling mechanism 727.

Further, an eccentric portion 725 is provided on the piston pump side shaft 721, and a piston bearing 709 is in contact with the outside of the eccentric portion 725. The pair of reciprocating piston pumps 711a and 711b
Is a non-self-priming pump, and has basically the same configuration as that of the first embodiment.

Therefore, the rotation of the piston pump-side shaft 721 integral with the motor shaft 719 causes the pistons 731a and 731b to slide left and right, thereby sucking brake oil from the flow path A (on the reservoir side). The brake fluid can be discharged to the flow path B (on the master cylinder side), and the brake oil can be sucked from the flow path C (on the reservoir side) and discharged to the flow path D (on the master cylinder side).

The rotary pump 717 is a self-priming pump, and is basically a trochoid pump substantially similar to that of the first embodiment. Therefore, the rotation of the motor shaft 719 is transmitted to the rotary pump side shaft 7 via the coupling mechanism 727.
23, the rotation of the rotary pump-side shaft 723 activates the internal gear structure 733. Thereby, the brake oil can be sucked from the flow path E (on the master reservoir side) and discharged to the flow path F (on the master cylinder side).

In this embodiment, the positions of the reciprocating piston pumps 711a and 711b and the rotary pump 717 are different from those of the first to sixth embodiments, but the same effects as in the first embodiment are exerted. (Eighth Embodiment) Next, an eighth embodiment will be described, but the description of the same parts as in the first embodiment will be omitted or simplified.

This embodiment is basically the same as the seventh embodiment, except that the rotary pump is not a trochoid pump but an external gear pump. That is, as shown in FIG. 13, the pump device 801 of the present embodiment is
The motor bearing 807, the piston bearing 809, and the pair of reciprocating piston pumps 811a and 811b are arranged in the first cylinder block 805 on one side (upper side in the figure) of the motor 803 in order from the motor 803 side.
A first rotary shaft seal member 815 and a rotary pump 817 are arranged in the second cylinder block 813 on the other side of the motor 803 (downward in the figure) in order from the motor 803 side.

Hereinafter, each configuration will be described. In the present embodiment, the motor shaft 819 and the piston pump-side shaft 821 (which is the rotation axis of the reciprocating piston pumps 811a and 811b) are formed as an integral member (rod), and the distal end side of the motor shaft 819 (downward in the figure). , The rotary pump side shaft 823 (which is the rotation axis of the rotary pump 817) is connected by a connecting mechanism 827 having a two-plane width.

Therefore, the motor shaft 819, the piston pump side shaft 821, and the rotary pump side shaft 82
3 and coaxially rotate together. A motor inner bearing 829 that is in contact with and supports the outer periphery of the motor shaft 819 is disposed outside the coupling mechanism 827.

Further, an eccentric portion 825 is provided on the piston pump side shaft 821, and a piston bearing 809 is in contact with the outside of the eccentric portion 825. The pair of reciprocating piston pumps 811a and 811b
Is a non-self-priming pump, and has basically the same configuration as that of the first embodiment.

Therefore, when the piston pump side shaft 821 integrated with the motor shaft 819 rotates, the pistons 831a and 831b slide left and right, so that brake oil is sucked from the flow path A (on the reservoir side). The brake fluid can be discharged to the flow path B (on the master cylinder side), and the brake oil can be sucked from the flow path C (on the reservoir side) and discharged to the flow path D (on the master cylinder side).

The rotary pump 817 is a self-priming pump, which is a so-called circumscribed gear pump different from the seventh embodiment. Therefore, when the rotation of the motor shaft 819 is transmitted to the rotary pump-side shaft 823 via the coupling mechanism 827, the rotation of the rotary pump-side shaft 823 causes the first gear 829a and the second gear 829 meshing therewith.
b rotates. Thereby, the brake oil can be sucked from the flow path E (on the master reservoir side) and discharged to the flow path F (on the master cylinder side).

In this embodiment, the same effects as in the seventh embodiment can be obtained. (Embodiment 9) Next, Embodiment 9 will be described, but the description of the same parts as in Embodiment 1 will be omitted or simplified.

This embodiment is basically the same as the seventh embodiment except that the transmission mechanism for transmitting the power from the motor to the rotary pump is greatly different. That is, as shown in FIG. 14, the pump device 901 of this embodiment includes a first cylinder block 905 on one side (upper side in the figure) of the motor 903.
Then, in order from the motor 903 side, the motor bearing 90
7, a piston bearing 909 and a pair of reciprocating piston pumps 911a and 911b are arranged, and the second cylinder block 913 on the other side (the lower side in the figure) of the motor 903.
In the order from the motor 903 side, a transmission mechanism 91 by gears
5. First rotating shaft seal member 917, rotary pump 919
Is arranged.

Hereinafter, each configuration will be described. In the present embodiment, the motor shaft 921 and the shaft 923 on the piston pump side (which is the rotation axis of the reciprocating piston pumps 911a and 911b) are formed as an integral member (rod).

Further, a rotary pump side shaft 925 (which is a rotary shaft of the rotary pump 919) is connected to a distal end side (lower side in the figure) of the motor shaft 921 by a transmission mechanism 915 using gears. That is, the motor shaft 9
The small-diameter first gear 927a on the 21 side and the large-diameter second gear 927a on the rotary pump-side shaft 925 mesh with each other to transmit driving force.

Accordingly, when the motor shaft 921 and the piston pump-side shaft 923 rotate, the rotary pump-side shaft 925 rotates at a different rotation speed. An eccentric portion 929 is provided on the piston pump-side shaft 923, and a piston bearing 909 is in contact with the outside of the eccentric portion 929.

The pair of reciprocating piston pumps 911
Reference numerals a and 911b denote non-self-priming pumps, which have basically the same configuration as that of the first embodiment. Therefore, when the piston pump side shaft 923 integral with the motor shaft 921 rotates, the pistons 931a and 931b slide left and right, so that brake oil is sucked from the flow path A (on the reservoir side) (master cylinder). Channel B)
And the brake oil can be sucked in from the flow path C (on the reservoir side) and discharged to the flow path D (on the master cylinder side).

The rotary pump 919 is a self-priming pump, and is a trochoid pump similar to that of the first embodiment. Therefore, when the rotation of the motor shaft 921 is transmitted to the rotary pump-side shaft 925 via the transmission mechanism 915, the rotation of the rotary pump-side shaft 925 activates the internal gear mechanism 933. Thereby, the brake oil can be sucked from the flow path E (on the master reservoir side) and discharged to the flow path F (on the master cylinder side).

In this embodiment, the same effects as those of the first embodiment can be obtained, and the rotation speed of the rotary pump side shaft 925 and the rotation speed of the piston pump side shaft 923 can be made different by the transmission mechanism 915. The discharge capacity required for each pump 911a, 911b, 919 can be set arbitrarily.

As described above, the present invention is not at all limited to the embodiments described above, and can be implemented in various forms without departing from the gist of the present invention.

[Brief description of the drawings]

FIG. 1 is a schematic configuration diagram of a vehicle brake device in which a pump device according to a first embodiment is used.

FIG. 2 is a schematic sectional view illustrating a pump device according to the first embodiment.

FIG. 3 is an explanatory view showing a trochoid pump.

FIG. 4 is an explanatory view showing a load direction of a reciprocating piston pump and a rotary pump.

FIG. 5 is an explanatory view showing another connecting mechanism.

FIG. 6 is a schematic sectional view illustrating a pump device according to a second embodiment.

FIG. 7 is a schematic sectional view illustrating a pump device according to a third embodiment.

FIG. 8 is an explanatory view showing an external gear pump.

FIG. 9 is a schematic sectional view illustrating a pump device according to a fourth embodiment.

FIG. 10 is a schematic sectional view showing a pump device according to a fifth embodiment.

FIG. 11 is a schematic sectional view showing a pump device according to a sixth embodiment.

FIG. 12 is a schematic sectional view showing a pump device according to a seventh embodiment.

FIG. 13 is a schematic sectional view showing a pump device according to an eighth embodiment.

FIG. 14 is a schematic sectional view showing a pump device according to a ninth embodiment.

[Explanation of symbols]

1: Master cylinder 11, 12, 13, 14 ... Wheel cylinder 41a, 41b, 41a ', 41b', 139a, 13
9b, 149a, 149b, 153a, 153b, 21
1a, 211b, 311a, 311b, 411a, 41
1b, 519a, 519b, 619a, 619b, 71
1a, 711b, 811a, 811b, 911a, 91
1b: Reciprocating piston pumps 43, 43 ', 217, 31
5, 417, 511, 611, 717, 817, 919
... Rotary pumps 45, 205, 305, 405, 505, 605, 70
3, 803, 903 ... motors 47, 201, 301, 401, 501, 601, 70
1,801,901 ... pump device 66,219,317,419,521,621,71
9, 819, 921 ... motor shafts 67, 221, 319, 412, 525, 625, 72
1, 821, 923: shaft on piston pump side 68, 321, 423, 523, 623, 723, 82
3, 925: rotary pump side shaft 69, 134, 154, 322, 529, 629, 72
7, 827 ... connecting mechanism 413, 915 ... transmitting mechanism

Continuing from the front page (72) Inventor Taku Sato 1-1-1, Showa-cho, Kariya-shi, Aichi, Japan Denso Co., Ltd. 72) Inventor Takahiro Yamaguchi 1-1-1, Showa-cho, Kariya-shi, Aichi F-term in DENSO Corporation (Reference) 3D046 BB12 BB28 CC02 LL11 LL37 LL50 3D049 BB00 BB32 BB39 CC02 HH12 HH53 PP01

Claims (28)

[Claims] 1. A return pump for circulating brake fluid supplied to a braking force generating means for generating a braking force on wheels, and a brake fluid pressure generating means for generating a brake fluid pressure in accordance with a driver's treading force. A pressurizing pump for supplying a brake fluid to increase the brake fluid pressure. A brake device, comprising: a single motor that drives the return pump and the pressurizing pump. 2. The return pump according to claim 1, wherein two return pumps are provided for each system so as to recirculate the brake fluid of the two brake hydraulic circuits. 2. The brake device according to 1. 3. The brake device according to claim 1, wherein the return pump is for anti-skid control. 4. The brake device according to claim 1, wherein the return pump is a non-self-priming pump. 5. The brake device according to claim 1, wherein the pressing pump is a self-priming pump. 6. The brake device according to claim 1, wherein the return pump is a reciprocating piston pump. 7. The brake device according to claim 1, wherein the pressing pump is a rotary pump. 8. The brake device according to claim 7, wherein the rotary pump is a trochoid pump, an internal gear pump, an external gear pump, or a vane pump. 9. The brake device according to claim 1, wherein the return pump and the pressing pump are integrated into one block. 10. The pump according to claim 1, wherein the return pump and the pressing pump are arranged in this order on one side as viewed in the axial direction of the motor, from the motor side. Brake equipment. 11. The pump according to claim 1, wherein the pressing pump and the return pump are arranged in this order on one side as viewed in the axial direction of the motor, from the motor side. Brake equipment. 12. The motor according to claim 1, wherein the return pump is arranged on one side as viewed in the axial direction of the motor, and the pressing pump is arranged on the other side. The brake device according to any one of the above. 13. The brake device according to claim 11, wherein a liquid-tight first rotary shaft sealing member is disposed between the motor and the pressing pump. 14. The brake device according to claim 10, wherein a liquid-tight second rotary shaft sealing member is disposed between the return pump and the pressing pump. 15. The brake device according to claim 1, wherein a rotation axis of the return pump and a rotation axis of the pressing pump are coaxially arranged. 16. The brake device according to claim 15, wherein the rotating shaft of the return pump and the rotating shaft of the pressing pump are formed as an integral member. 17. The rotating shaft of the return pump and the rotating shaft of the pressing pump are formed as separate members, and the two rotating shafts are connected by a connecting mechanism to rotate integrally. The brake device according to claim 15, wherein the brake device is configured. 18. The apparatus according to claim 1, wherein said rotating shafts are connected by a connecting mechanism movable in an axial direction.
The brake device according to claim 7. 19. The eccentric part is provided on the rotary shaft of the return pump in order to move the piston with the rotation of the rotary shaft of the return pump. Brake device. 20. The brake device according to claim 1, wherein a rotation axis of the return pump and a rotation axis of the pressing pump are non-coaxially arranged. 21. A rotating shaft of said return pump and a rotating shaft of said pressing pump, which are arranged non-coaxially, are connected via a transmission mechanism, and are configured to rotate at different rotational speeds. The brake device according to claim 20, characterized in that: 22. The apparatus according to claim 1, wherein the load direction of the piston of the return pump and the load direction of the pressing pump are not the same.
2. The brake device according to claim 1. 23. The system according to claim 21, further comprising two brake hydraulic circuits each including said braking force generating means and said brake hydraulic pressure generating means, and an independent brake hydraulic circuit. 23. The brake device according to any one of 1 to 22. 24. A control system for controlling the brake fluid pressure of the braking force generating means and increasing the brake fluid pressure of the brake fluid pressure generating means by the multi-system brake fluid pressure circuit. Item 24. The brake device according to item 23. 25. The brake device according to claim 16, wherein at least one bearing member that supports both the load of the return pump and the load of the pressing pump is provided. 26. One bearing member that supports both the load of the return pump and the load of the pressing pump abuts on both the block of the return pump and the block of the pressing pump. 17. The method according to claim 16, wherein
The brake device according to item 1. 27. A pump device wherein two reciprocating piston pumps and one rotary pump are driven by one motor. 28. The pump device according to claim 27, wherein said two reciprocating piston pumps and said one rotary pump are integrally assembled in one block.