JP2001010462A - Vehicle brake device - Google Patents

Abstract

PROBLEM TO BE SOLVED: To prevent the enlargement of an actuator or the extensive consumption of electric energy by regulating the output hydraulic pressure of a hydraulic source, compounding the output of the actuator with the output hydraulic pressure of a pressure regulator means, and imparting the resulting hydraulic pressure to a wheel brake. SOLUTION: The spring characteristics and set load of simulator springs 72, 77 in first and second operation simulators 65, 68 are selected, whereby the brake force by the output hydraulic pressure of an actuator 12 and the brake force by the hydraulic pressure obtained by regulating the output hydraulic pressure of an accumulator 13 by a pressure regulator means 14 can be generated in an optional set ratio from the initial stage of brake operation. Thus, even if the responsiveness of brake force generation by the output hydraulic pressure of the actuator 12 is low, it can be covered with the brake force by the brake hydraulic pressure obtained by regulating the output hydraulic pressure of the accumulator 13 by the pressure regulator means 14.

Description

DETAILED DESCRIPTION OF THE INVENTION

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a vehicle brake device having an actuator which has an electric operating portion which operates in response to an electric input and which can output a brake fluid pressure in accordance with the operation of the electric operating portion.

[0002]

2. Description of the Related Art Conventionally, such a braking device is operated, for example, by controlling the operation of an electric operating portion based on a brake operation input by a driver or operating the electric operating portion based on other information unrelated to the driver's brake operation. The brakes that exceed the operation input are generated by the wheel brakes according to the urgency of the brake operation, and automatic braking is applied to maintain the inter-vehicle distance with the preceding vehicle. A system in which a master cylinder is driven by a negative pressure booster is disclosed in, for example, Japanese Patent Application Laid-Open No. 10-19 / 1998.
No. 4098, and Japanese Patent No. 2596.
As disclosed in Japanese Patent Publication No. 224/224, there is a type in which the output hydraulic pressure of the master cylinder is boosted and output in response to the operation of the electric motor, or the hydraulic pressure of the accumulator is adjusted by an electromagnetic valve to control the brake hydraulic pressure. Is already known, and a wheel brake itself having an electric motor is also known.

[0003]

However, in the above-mentioned prior art, the response until the wheel brake exerts the braking force is improved, the brake fluid pressure required for the wheel brake is secured, In order to cope with the failure, the following measures are required. In other words, in order to improve the response, an electronic control negative pressure booster is used to secure a sufficiently large air passage area for circulating air, and in the case of using an electric motor, the capacity of the electric motor is increased or used. In the case of increasing the voltage and adjusting the output hydraulic pressure of the accumulator, the accumulator hydraulic pressure of the accumulator is set relatively high. Also, in order to secure the brake fluid pressure (that is, fluid volume), it is necessary to increase the size of the actuator, use a large amount of electric energy,
Or the accumulator pressure is set high.
Further, in order to cope with a failure related to electricity, a power supply system, an input system, and an actuator system are duplicated.

[0004] In the conventional brake device, since the above-described countermeasures are required, the structure of the brake device is complicated, and the cost and weight are increased.

SUMMARY OF THE INVENTION The present invention has been made in view of the above circumstances, and aims at simplifying the configuration while preventing the actuator from being enlarged and consuming a large amount of electric energy, and avoiding an increase in cost and weight. It is an object of the present invention to provide a vehicular brake device that can be obtained.

[0006]

SUMMARY OF THE INVENTION In order to achieve the above object, the present invention provides an actuator having an electric operating portion which operates in response to an electric input and capable of outputting a braking force in accordance with the operation of the electric operating portion. A hydraulic pressure source, pressure regulating valve means for regulating an output hydraulic pressure of the hydraulic pressure source, an output of the actuator and an output hydraulic pressure of the pressure regulating valve means, and applied to a wheel brake. And output synthesizing means.

[0007] According to such a configuration, the output of the actuator in accordance with the operation of the electric operating section and the hydraulic pressure obtained by adjusting the output hydraulic pressure of the hydraulic pressure source by the pressure adjusting valve means are output by the output synthesizing means. Since it is synthesized and acts on the wheel brake,
In the actuator, it is possible to prevent large consumption of electric energy while reducing the size, and it is not necessary to set the output hydraulic pressure on the hydraulic pressure source side high. In addition, even if a failure occurs in the electrical part of the actuator, the required minimum braking force can be secured by the brake fluid pressure from the fluid pressure source side. There is no need to make it heavy. Therefore, it is possible to simplify the overall configuration and avoid an increase in cost and weight.

[0008]

DETAILED DESCRIPTION OF THE PREFERRED EMBODIMENTS Hereinafter, embodiments of the present invention will be described based on embodiments of the present invention shown in the accompanying drawings.

FIGS. 1 to 7 show a first embodiment of the present invention. FIG. 1 is a hydraulic circuit diagram showing the overall structure of a vehicle brake device, and FIG. 2 is a diagram showing the structure of a brake hydraulic pressure generating device. FIG. 3 is a sectional view taken along line 3-3 in FIG. 2, FIG.
FIG. 5 is an enlarged cross-sectional view of a part of the actuator, FIG. 5 is an enlarged cross-sectional view of the pressure regulating valve means, FIG. 6 is a view showing a hydraulic pressure synthetic characteristic by the output synthesizing means, and FIG. It is a figure showing other examples of.

First, in FIG. 1, the left and right front wheels and the left and right rear wheels of a passenger vehicle are provided with wheel brakes B _FL , B _FR ,
B _RL and B _RR are mounted, respectively, and the brake fluid pressure according to the brake operation of the brake operation member 30 which can be operated by the driver's foot or hand is applied to the left front wheel brake B _FL.
And is output to the output fluid pressure channel 2A from the brake fluid pressure generating device 1A ₁ corresponding to the right rear wheel brake B _RR, corresponding to the right front wheel brake B _FR and the left rear wheel brake B _RL output from the brake fluid pressure generating device 1B ₁ to the output fluid pressure passage 2B.

One output hydraulic pressure passage 2A is connected to a front left wheel brake _BFL and a right rear wheel brake _BRR via a brake hydraulic pressure control device 3A, and the other output hydraulic pressure passage 2B. Is a front right wheel brake _BFR and a left rear wheel brake _BRL via the brake fluid pressure control device 3B.
Connected to.

The brake hydraulic pressure control device 3A has an output hydraulic pressure path.
2A and left front wheel brake B _FLAlways between
Open solenoid valve 4_FLAnd output hydraulic pressure path 2A and right rear wheel
Brake B_RRNormally open solenoid valve 4 provided between_RRAnd Liza
5A and front left wheel brake B_FLAnd reservoir
Normally closed solenoid valve 6 provided between 5A_FLAnd the right rear wheel
Brake B_RRAnd normally closed type provided between reservoir and 5A
Solenoid valve 6_RRAnd pumping the brake fluid from reservoir 5A
Both pumped brake fluid can be returned to the output hydraulic pressure line 2A
Return pump 7A, return pump 7A and reservoir 5A
The suction valve 8A, the return pump 7A and the outlet
And a discharge valve 9A provided between the power hydraulic pressure passages 2A.

Furthermore brake fluid pressure control apparatus 3B, the output fluid pressure passage 2B and the right front wheel brake B and the normally open solenoid valve 4 _FR provided between _FR, the output fluid pressure passage 2B and the left rear wheel brake A _normally open solenoid valve 4 _RL provided between B _RL and
A reservoir 5B, a normally closed solenoid valve 6 _FR provided between the right front wheel brake B _FR and the reservoir 5B, a normally closed solenoid valve 6 _RL provided between the wheels for the left rear wheel brake B _RL and the reservoir 5B A return pump 7B capable of pumping up the brake fluid in the reservoir 5B and returning the pumped brake fluid to the output hydraulic pressure path 2B, a suction valve 8B provided between the return pump 7B and the reservoir 5B, a return pump 7B and an output fluid. A discharge valve 9B provided between the pressure paths 2B.

The return pumps 7A and 7B of the two brake fluid pressure controllers 3A and 3B are connected to a common single electric motor 10, and the return pumps 7A and 7B are operated according to the operation of the electric motor 10. Driven.

The brake hydraulic pressure control devices 3A, 3
In B, at the time of normal braking in which there is no possibility that each wheel locks, the normally open solenoid valves 4 _FL to 4 _RR are demagnetized and opened, and the normally closed solenoid valves 6 _{FL to} 6 _RR are opened. demagnetized, is a closed state, the brake fluid pressure in the output hydraulic pressure passage 2A, 2B acts on the wheel brakes B _FL .about.B _RR through the normally open electromagnetic valve 4 _FL to 4 _RR.

When the wheels are about to enter the locked state during the braking, the normally open solenoid valves corresponding to the wheels that are about to enter the locked state among the normally open solenoid valves 4 _FL to 4 _RR. Is energized and closed, and each normally closed solenoid valve 6 _FL
Normally-closed solenoid valve corresponding to the above wheels out of ~ 6 _RR is excited,
The valve is opened. As a result, a part of the brake fluid pressure of the wheel which is about to enter the locked state is changed to the reservoir 5A or 5B.
And the brake fluid pressure of the wheels that are about to enter the locked state is reduced.

Further when holding the brake fluid pressure constant, the normally open electromagnetic valve 4 _FL to 4 _RR is energized, while being closed, the normally closed electromagnetic valves 6 _FL to 6 _RR is deenergized, The valve will be closed. When the brake fluid pressure is further increased, the normally open solenoid valves 4 _FL to 4 _RR are demagnetized and opened, and
It is sufficient that the normally closed solenoid valves 6 _{FL to} 6 _RR are demagnetized and closed.

The electric motor 10 is operated during the antilock brake control as described above, and the return pumps 7A and 7B are driven by the operation of the electric motor 10, so that the return pumps 7A and 7B are absorbed by the reservoirs 5A and 5B. The supplied brake fluid is sucked into the return pumps 7A and 7B, and then returned to the output hydraulic pressure paths 2A and 2B. Such a return of the brake fluid can prevent an increase in the operation amount of the brake operation member 30 due to the absorption of the brake fluid in the reservoirs 5A and 5B.

In FIG. 2, the left front wheel brake B _FL
And the brake fluid pressure generating device 1A ₁ corresponding to the right rear wheel brake B _RR is the operation of the electric motor 11 and having an electric motor 11 of the DC motor or the like as an electric actuating unit for actuating in response to an electrical input An actuator 12 capable of outputting a corresponding braking force, an accumulator 13 as a hydraulic pressure source, pressure regulating valve means 14 for regulating the output hydraulic pressure of the accumulator 13, and an output of the actuator 12 and an output hydraulic pressure of the pressure regulating valve means 14. An output synthesizing means 15 for synthesizing and applying the resultant to the front left wheel brake _BFL and the rear right wheel brake _BRR .

The actuator 12 includes a housing 16
A piston 17 which is slidably fitted to the housing 16 and has a front end (left end in FIG. 2) facing an output hydraulic pressure chamber 18 formed between the housing 16 and the piston 17. A return spring 19 provided between the housing 16 and the piston 17 to exert a spring force for urging the piston 17 rearward in the axial direction (to the right in FIG. 2); an electric motor 11 disposed at a fixed position; A transmission mechanism 20 provided between the electric motor 11 and the piston 17 so as to convert the rotational power of the electric motor 11 into the axial power of the piston 17; and the output hydraulic chamber 18 is provided in the output hydraulic path 2A. Is communicated to.

A transmission mechanism 20 is coaxially connected to a rear end (the right end in FIG. 2) of the piston 17 and penetrates a rear end wall of the housing 16 in a liquid-tight manner and movably in the axial direction.
A driven gear 23 coupled to the transmission shaft 21 via a screw 22; and a drive gear 24 fixed to the output shaft 11a of the electric motor 11 and meshing with the driven gear 23. The electric motor 11 is fixedly mounted on the housing 16, and the driven gear 23 is rotatably supported by the housing 16 such that the axial position thereof is fixed.

Referring also to FIG. 3, a pair of grooves 25, 2 extending in the axial direction on one diameter line of the transmission shaft 21, that is, the piston 17, connected to the driven gear 23 via the screw 22.
5 is provided on the outer surface of the piston 17, and hemispherical recesses 27, 27 are provided on the inner surface of the housing 16 for receiving balls 26, 26 that can roll in the grooves 25, 25. As a result, the piston 17 is slidably fitted to the housing 16 in such a manner that the piston 17 is prevented from rotating around its axis but is allowed to move along the axial direction. Accompanying driven gear 2
In response to one rotation, the piston 17 moves forward in the axial direction. In the rest state of the electric motor 11, the piston 17 moves backward in the axial direction by the spring force of the return spring 19. At this time, the electric motor 11 is caused to idle by the transmission mechanism 20.

A flange 17a extending outward in the radial direction of the piston 17 is integrally provided at an intermediate portion in the axial direction of the piston 17, and the outer periphery of the flange 17a is slidably fitted. A large-diameter cylindrical portion 16a is provided at an axially intermediate portion of the housing 16.

The flange 17a of the piston 17
The front, which faces the release chamber 30 formed between the piston 17 and the housing 16, the release chamber 30 is communicated with the reservoir R _1. An annular seal member 29 for sealing between the release chamber 30 and the output hydraulic chamber 18 is mounted on the outer periphery of the front end of the piston 17 so as to slide on the inner surface of the housing 16.

At the front end of the piston 17, the piston 1
When the piston 7 is in the retreat limit (the state shown in FIG. 2), the output hydraulic chamber 18 is communicated with the release chamber 30, but when the piston 17 advances from the retreat limit, the output hydraulic chamber 18 and the release chamber are released. A relief valve 31 for shutting off the space between the two is mounted.

In FIG. 4, a relief valve 31 is provided with a valve body 33 that allows one end to pass through a release chamber 30 and closes the other end of a valve hole 32 provided at the front end of the piston 17.
And a spring 34 for urging the valve 3 in the valve closing direction.

A recess 35 is provided at the front end of the piston 17, and the other end of the valve hole 32 is provided at the piston 17 so as to open at the center of the closed end of the recess 35. Further, a disc-shaped first retainer 37 having a through hole 36 having a diameter smaller than the diameter of the concave portion 35 at the center thereof is in contact with the front end of the piston 17, and the valve body 33 is moved by the first retainer 37. The retainer 37 and the valve body 3 are housed in the recess 35 so as to prevent the detachment from the recess 35.
The spring 34 is contracted between the three.

On the other hand, a second retainer 38 is in contact with the inner surface of the front end of the housing 16, and a return spring 19 is provided between the retainers 37, 38. Therefore, the first retainer 37 is pressed against the front end of the piston 17 by the spring force of the return spring 19, and the first retainer 37 is pressed.
Is substantially fixed to the front end of the piston 17. Also, the second retainer 38 is pressed against the front end of the housing 16 by the spring force of the return spring 19, and the second retainer 38 is substantially fixed to the front end of the housing 16.

The piston 1 is located at the center of the second retainer 38.
An engagement hole 40 is provided coaxially with the shaft 7. A front end of a valve shaft 39 that penetrates the engagement hole 40 movably in the axial direction is provided on the second retainer 38 at a peripheral edge of the engagement hole 40. An engagement flange 39a engageable from the front end side of the housing 16 is provided. The rear end of the valve shaft 39 passes through the insertion hole 36 of the first retainer 37 movably in the axial direction, and is coaxially connected to the valve body 33.

According to such a relief valve 31, when the piston 17 is in the retreat limit position (the position shown in FIGS. 2 and 4), the engagement flange 39a of the valve shaft 39 is connected to the second retainer 38. The engagement of the valve body 33 causes the valve hole 3
Stopped by a position spaced from the open end of the second recess 35 will be the valve hole 32 is opened, the release chamber 30 that communicates with the reservoir R ₁ and the output fluid pressure chamber 18 is communicated state. On the other hand, when the piston 17 advances from the retreat limit position, the valve body 33 closes the opening end of the valve hole 32 to the concave portion 35 by the spring force of the spring 34, and the space between the release chamber 30 and the output hydraulic pressure chamber 18 is formed. Will be shut off.

Referring again to FIG. 2, the output synthesizing means 15
An annular input hydraulic chamber 42 is formed between the piston 17 and the housing 16 so as to face the rear surface of the flange 17 a of the piston 17. Thus, on the outer periphery of the flange portion 17a, an annular sealing member 43 that seals between the release chamber 30 and the input hydraulic chamber 42 and slides on the inner surface of the large-diameter cylindrical portion 16a.
Is mounted, and the piston 1 is positioned rearward of the flange 17a.
7, an annular sealing member 4 which seals between the release chamber 30 and the outside and slides on the inner surface of the rear portion of the housing 16 is provided.
4 is attached.

According to the actuator 12 and the output synthesizing unit 15, the input hydraulic chamber 42 in the output synthesizing unit 15 is operated by operating the electric motor 11.
Irrespective of the hydraulic pressure, the piston 17 moves forward and the relief valve 31
Is closed, and as the volume of the output hydraulic chamber 18 is reduced, the hydraulic pressure of the output hydraulic chamber 18 is increased, and the hydraulic pressure of the output hydraulic chamber 18 acts on the output hydraulic path 2A. Will be. When a hydraulic pressure acts on the input hydraulic chamber 42 of the output synthesizing means 15, a hydraulic pressure acts on the piston 17 to further advance the piston 17 from the advanced position of the piston 17 determined by the power exerted by the electric motor 11. Thus, the output hydraulic pressure chamber 18 outputs a brake hydraulic pressure obtained by synthesizing a hydraulic pressure determined by the operation of the electric motor 11 and a hydraulic pressure determined by the hydraulic pressure acting on the input hydraulic pressure chamber 42. Will be.

The output hydraulic pressure path 2A is connected to the accumulator 13 through a solenoid valve 45 and a check valve 46, which are normally closed solenoid valves, so that the electric motor 11 of the actuator 12 can be operated without a braking force. Is activated, the output hydraulic chamber 1 of the actuator 12 is operated.
The hydraulic pressure output from 8 is stored in accumulator 13. That is, in a state where the braking force is not required, the electromagnetic on-off valve 45 is opened, and the brake fluid pressure control device 3 is opened.
The hydraulic pressure can be stored in the accumulator 13 by exciting and closing the normally open solenoid valves 4 _FL and 4 _RR (see FIG. 1) in A, and operating the electric motor 11.
The electromagnetic on-off valve 45 is demagnetized and closed during braking.

The pressure regulating valve means 14 is a piston which has a front end (left end in FIG. 2) facing a pressure regulating chamber 48 formed between the housing 47 and the housing 47 slidably. 49, an input rod 50 coaxially connected to the rear end (the right end in FIG. 2) of the piston 49,
A return spring 51 provided between the housing 47 and the piston 49 in the pressure adjusting chamber 48 to exert a spring force for urging the piston 49 rearward in the axial direction (to the right in FIG. 2); Relief valve 5 provided between reservoirs R ₁
2 and an on-off valve 53 provided between the pressure regulating chamber 48 and the accumulator 13, and the pressure regulating chamber 48 is communicated with the input hydraulic chamber 42 of the output synthesizing means 15.

In FIG. 5, the outer periphery of the piston 49 and
Between the inner circumference of the housing 47 and the outer circumference of the piston 49
A pair of annular rings that are mounted and slidably contact the inner periphery of the housing 47
Are sealed at both ends in the axial direction by the sealing members 54, 54.
An annular release chamber 55 is formed.
Is the reservoir R regardless of the axial position of the piston 49.
₁Is always in communication with

A valve housing 56 is coaxially connected to the front end of the housing 47.
A valve shaft 57 that makes the rear end of the housing 47 project into the pressure regulating chamber 48 in the front end of the housing 47 is accommodated so as to be movable in the axial direction.
A flange 5 extending radially outward is provided at an intermediate portion of the valve shaft 57.
7a, the flange portion 57a and the valve housing 56 are provided.
A spring 58 that exerts a spring force smaller than the spring force of the return spring 51 is provided therebetween. The spring 58 urges the valve shaft 57 toward the rear side in the axial direction, that is, toward the piston 49.

The relief valve 52 has a valve hole 59 provided in the piston 49 such that one end thereof communicates with the release chamber 55 and the other end opens to the pressure regulating chamber 48 at the center of the front end of the piston 49. And a spherical valve body 60 provided integrally with the rear end of the valve shaft 57 so that the opening end of the valve 59 to the pressure regulating chamber 48 can be closed. The relief valve 52 is a piston 49 to communicate with the one state release chamber 55 i.e. the reservoir R ₁ a pressure regulating chamber 48 in to open (FIGS. 2 and 5 state indicated by) the backward limit, the piston 49 is retracted When advanced from limited operates as so as to block the valve hole 59 in the valve body 60 allowed to cut off from the release chamber 55 i.e. the reservoir R ₁ a pressure regulating chamber 48.

The on-off valve 53 opens and closes a valve hole 61 formed in an intermediate portion of the valve housing 56 through the pressure regulating chamber 48 and has a valve shaft 5 that is gently inserted into the valve hole 61.
7 is housed in a valve chamber 63 formed at the front end of the valve housing 56 through the accumulator 13 and urges the valve body 62 in the valve closing direction. A valve spring 64 that exerts a spring force is stored in the valve chamber 63.

In such an on-off valve 53, the piston 49
Is in the retreat limit, the valve body 62 is located at a position separated from the front end of the valve shaft 57, so that the valve body 62 is in a position to close the valve hole 61 by the spring force of the valve spring 64, and the accumulator 1
3 and the pressure regulation chamber 48 are shut off. Also piston 4
9 advances from the retreat limit, the front end of the valve shaft 57
The valve body 62 is pressed against the spring force of the valve spring 64 to the position where the valve hole 61 is opened, and the on-off valve 53 is opened, and the accumulator 13 is moved to the pressure regulating chamber 48. Will be communicated.

According to the pressure regulating valve means 14, the piston 49 moves forward by the action of the pressing force from the input rod 50, whereby the relief valve 52 is closed and the on-off valve 53 is opened. Therefore, the accumulator 13
Is adjusted in accordance with the pressing force acting on the piston 49 from the input rod 50, the operating force is amplified at a predetermined ratio, and the adjusted hydraulic pressure is output from the pressure adjusting chamber 48. It acts on the input hydraulic chamber 42 of the synthesizing means 15.

By the way, the driver's braking force is
It acts on one end of the brake operating member 30, and an intermediate portion of the brake operating member 30 is rotatably supported on a fixed support 66 via a first operation simulator 65. One end of a pair of cables 67A and 67B is connected to the other end of 30. Thus, the other end of the one cable 67A is connected to the second operation simulator 68.
The other end of the link 69 is connected to the input rod 50.

The first operation simulator 65 includes a support 66
And a brake operating member 30
A simulator piston 71 connected to the housing 70 and slidably fitted to the housing 70, and a spring force against the pressing force acting on the simulator piston 71 from the brake operating member 30 is applied to the simulator piston 71 so as to be provided in the housing 70. A front end of a rod 71a rotatably supporting a middle portion of the brake operating member 30 at a rear end thereof is provided coaxially and integrally with the simulator piston 71. The rod 71a may be separate from the simulator piston 71.

An operating force detector 73 for detecting an operating force applied from the simulator piston 71 via the simulator spring 72 is housed in the housing 70. The operation force detector 73 detects the operation force of the brake operation member 30 in order to control the operation amount of the electric motor 11 in the actuator 12 according to the operation force applied to the brake operation member 30.

The second operation simulator 68 includes a link 69
A movable housing 75 having one end connected to one end of the cable 67A, and a movable member 76 housed in the movable housing 75 so as to be relatively movable in the axial direction and connected to the other end of the cable 67A.
And a simulator spring 77 provided between the movable housing 75 and the movable member 76 by exerting a spring force for pressing the movable member 76 toward one end of the movable housing 75.
And

According to the first and second operation simulators 65 and 68, a brake operation load is applied to the first operation simulator 65 in response to the brake operation of the brake operation member 30 by the driver. After the spring load of the simulator spring 72 in the first operation simulator 65 becomes a value corresponding to the set load of the simulator spring 77 in the second operation simulator 68, the second operation simulator 68 sets the link 69 and the input rod 5
0, the pressing action of the pressure regulating valve means 14 on the piston 49 is started, and both operation simulators 65 and 6 are started.
By selecting the spring characteristics and the set load of the simulator springs 72 and 77 in 8, the operation start timing of the pressure regulating valve means 14 can be arbitrarily selected.

The right front wheel brake B _FR and the brake fluid pressure generating device 1B that corresponds to the left rear wheel brake B _RL
1 is intended to the brake fluid pressure generating device 1A ₁ basically have the same configuration, the cable 67B leading to the brake operating member 30 is connected to the brake fluid pressure generating device 1B _1.

The operation of the first embodiment will be described. The actuator 12 operates so as to output a hydraulic pressure in accordance with the operation of the electric motor 11, and the accumulator 13
The output hydraulic pressure of the actuator 12 and the hydraulic pressure obtained by adjusting the output hydraulic pressure of the actuator 12 with the output hydraulic pressure of the actuator 12 are synthesized by the output synthesizing means 15. _FL , _BRR ; _BFR , _BRL .

At this time, by selecting the spring characteristics and the set load of the simulator springs 72 and 77 in the first and second operation simulators 65 and 68, as shown in FIG. And the output hydraulic pressure of the accumulator 13
It is possible to generate the braking force due to the fluid pressure obtained by adjusting the pressure at 4 at an arbitrary set ratio from the initial stage of the brake operation. With this configuration, even when the response of the brake force generation due to the output hydraulic pressure of the actuator 12 is low,
The output hydraulic pressure from the accumulator 13 can be covered by the braking force by the brake hydraulic pressure obtained by the pressure adjustment by the pressure adjusting valve means 14.

As shown in FIG. 7, a brake force is obtained only by the output hydraulic pressure of the actuator 12 from the start of the brake operation to a certain set operation amount. It is also possible to add a braking force due to the fluid pressure obtained by regulating the output fluid pressure of the accumulator 13 by the pressure regulating valve means 14 to the braking force due to the fluid pressure. In this way, in consideration of the fact that the deceleration is relatively low during normal general braking, only the braking force generated by the output hydraulic pressure of the actuator 12 is used to provide sufficient braking power, so that the electric vehicle can sufficiently perform brake regeneration. Brake control can be easily performed.

As described above, the brake fluid pressure is obtained by combining the output fluid pressure of the actuator 12 and the fluid pressure obtained by regulating the output fluid pressure of the accumulator 13 by the pressure regulating valve means 14. Electric motor 1 for driving the actuator 12 while reducing the size of the motor 12
1 can be prevented from consuming a large amount of electrical energy, and there is no need to set the output hydraulic pressure of the accumulator 13 high.

Further, instead of the driver operating the brake operating member 30 with his / her foot as in the conventional brake device, the driver can operate the brake operating member 30 by hand. Thus, it is possible to easily configure a hand-operated brake operation mechanism in consideration of backup in a case where a required brake fluid pressure cannot be output from the vehicle.

Even if the electric part of the electric motor 11 in the actuator 12 fails, as long as the hydraulic pressure is accumulated in the accumulator 13, the brake hydraulic pressure from the accumulator 13 is the minimum necessary brake hydraulic pressure. Therefore, it is not necessary to make the power supply system, the input system, and the actuator system a dual system. Therefore, it is possible to simplify the overall configuration and avoid an increase in cost and weight.

The output synthesizing means 15 includes the actuator 12
17a provided integrally with the piston 17 at
And the housing 16, the number of components can be reduced and the configuration can be simplified as compared with a configuration in which output combining means is configured separately from the actuator 12.

The hydraulic pressure accumulation in the accumulator 13 is as follows:
Since the operation is performed by the hydraulic pressure output from the actuator 12 in accordance with the operation of the actuator 12 during non-braking, it is not necessary to provide a hydraulic pump other than the actuator 12, and the number of parts can be reduced. In addition, the configuration can be further simplified. In addition, since the electromagnetic on-off valve 45 is provided between the accumulator 13 and the actuator 12, when the hydraulic pressure is output from the output hydraulic pressure chamber 18 to obtain the braking force, the electromagnetic on-off valve 45 is closed. The output hydraulic pressure of the output hydraulic pressure chamber 18 is not accumulated in the accumulator 13, and the braking force can be reliably obtained.

FIG. 8 shows a second embodiment of the present invention, in which parts corresponding to those of the first embodiment are denoted by the same reference numerals.

The output hydraulic pressure passage 2 corresponding to the left front wheel brake B _FL and the right rear wheel brake B _RR (see FIG. 1).
Brake fluid pressure generating device 1A ₂ which is connected to the A includes an actuator 12 having an electric motor 11, the output fluid pressure passage 2
A is provided with an accumulator 13 connected to A through an electromagnetic on-off valve 45 and a check valve 46, a pressure regulating valve means 78, and an output synthesizing means 15.

The pressure regulating valve means 78 is connected to the input of the output synthesizing means 15.
Provided between the power hydraulic chamber 42 and the accumulator 13
A normally closed solenoid valve 79, the input hydraulic chamber 42 and the reservoir
Bar R ₁And a normally-open solenoid valve 80 provided therebetween.
Degaussing / closing and energizing / opening of normally closed solenoid valve 79
And de-energize / open and energize / close the normally open solenoid valve 80
By controlling, the hydraulic pressure of the accumulator 13 is adjusted.
To act on the input hydraulic chamber 42 of the output synthesizing means 15
be able to.

[0058] The brake hydraulic pressure generating device 1B ₂ connected to the output fluid pressure channel 2B corresponding to the right front wheel brake B _FR and the left rear wheel brake B _RL (see FIG. 1), said brake fluid pressure basically the generator 1A ₂ are those having the same configuration.

Further, the other end of the brake operation member 30 to which a brake operation force by the driver's foot or hand is applied to one end is rotatably supported at a fixed position. An operation simulator 65 provided with an operation force detector 73 is provided between the operation simulator 65 and the support 66.

That is, an intermediate portion of the brake operating member 30 is rotatably connected to a rod 71 a integral with a piston 71 slidably fitted to a housing 70 fixed to the support 66, A spring force opposing the pressing force acting on the piston 71 from the piston 71
An operating force acting from the piston 71 via a simulator spring 72 applied to the housing 70 is detected by an operating force detector 73 housed in the housing 70.

According to the second embodiment, the pressure regulating valve means 78
Can be applied to an unmanned vehicle because it operates electrically and regulates the output hydraulic pressure of the accumulator 13 without depending on the operation of the driver. Even in the event that it cannot be expected, braking force can be obtained.

[0062] As another embodiment of the present invention, a position communicating between the accumulator 13 and the input fluid pressure chamber 42, and a position communicating between the reservoir R ₁ and the input fluid pressure chamber 42, the input liquid pressure chamber 42 Accumulator 13 and reservoir R ₁
A three-port, three-position solenoid-operated switching valve capable of switching the position to shut off any of the above may be used as the pressure regulating valve means.

FIG. 9 shows a third embodiment of the present invention, and portions corresponding to the above embodiments are given the same reference numerals.

Output hydraulic pressure passage 2 corresponding to left front wheel brake B _FL and right rear wheel brake B _RR (see FIG. 1)
Brake fluid pressure generating device 1A ₃ connected to the A includes an actuator 12 having an electric motor 11, the output fluid pressure passage 2
A, an accumulator 13 connected via a solenoid on-off valve 45 and a check valve 46, and a first pressure regulating valve means 14
, Second pressure regulating valve means 78, and output synthesizing means 15.

The first pressure regulating valve means 14 is the same as the pressure regulating valve means 14 of the first embodiment, and
0 so that the accumulator 1 operates according to the operation of the accumulator 1.
3 and the hydraulic path 81. The second pressure regulating valve means 78 is composed of a normally closed solenoid valve 79 and a normally open solenoid valve 80 in the same manner as the pressure regulating valve means 78 of the second embodiment, and the normally closed solenoid valve 79 is connected to the accumulator 13. Hydraulic passage 8
2 and an input hydraulic chamber 42 of the output synthesizing means 15, and a normally open solenoid valve 80 is provided between the hydraulic path 81 and the input hydraulic chamber 42.

The output hydraulic pressure passage 2 corresponding to the right front wheel brake _BFR and the left rear wheel brake _BRL (see FIG. 1).
Brake fluid pressure generating device 1B is connected to the B ₃ has basically the same configuration as the brake fluid pressure generating device 1A _3.

According to the third embodiment, the brake force by the brake fluid pressure obtained by synthesizing the fluid pressure obtained by adjusting the output fluid pressure of the accumulator 13 and the output fluid pressure of the actuator 12 is applied to the driver's brake operation. Not only can it be obtained accordingly, but also the braking force can be obtained independently of the driver's braking operation.

FIG. 10 shows a fourth embodiment of the present invention, and portions corresponding to the above embodiments are given the same reference numerals.

Output hydraulic pressure path 2 corresponding to the left front wheel brake B _FL and the right rear wheel brake B _RR (see FIG. 1)
Brake fluid pressure generating device 1A ₄ which is connected to the A includes an actuator 12 having an electric motor 11, the output fluid pressure passage 2
A is provided with an accumulator 13 connected to A through an on-off valve 83 and a check valve 46, a pressure regulating valve means 14, and an output synthesizing means 15.

The on-off valve 83 includes a valve housing 84 and an output
Pilot chamber 8 communicating with input hydraulic chamber 42 of synthesis means 15
5 is slidably fitted to the valve housing 84 with the back facing 5
And an input hydraulic chamber.
The hydraulic pressure of 42, that is, the pilot hydraulic pressure of the pilot chamber 85
When the pressure rises, the accumulator 13 and the output liquid
It operates so as to cut off between the pressure paths 2A. This allows each
Wheel brake B_FL, B _FR, B_RL, B_RRBrake fluid pressure
In the operating state, the pressure is stored in the accumulator 13.
Although not performed, each wheel brake B_FL, B_FR,
B_RL, B_RRBrake fluid pressure is not applied to the
When the on-off valve 53 of the pressure regulating valve means 14 is closed,
By operating the motor 11, the actuator
It is possible to accumulate the output hydraulic pressure of 12 in the accumulator 13.
it can.

The driver's brake operating force acts on one end of the brake operating member 30, and the intermediate portion of the brake operating member 30
The other end of a cable 67A, which is rotatably supported by a fixed support 66 via the fifth member 5 and has one end connected to the other end of the brake operation member 30, is connected to one end of a link 69 via a second operation simulator 68. The other end of the link 69 is connected to the input rod 50 which is connected to the piston 49 of the pressure regulating valve means 14.

Further, a stroke detector 8 for detecting the stroke of the simulator piston 71 in the first operation simulator 65, that is, the operation amount of the brake operation member 30.
7 is attached to the first operation simulator 65.

Output hydraulic pressure passage 2 corresponding to right front wheel brake _BFR and left rear wheel brake _BRL (see FIG. 1)
Brake fluid pressure generating device 1B is connected to B ₄ are those in the brake fluid pressure generating device 1A ₄ basically have the same configuration, the cable 67B leading to the brake operating member 30 is the brake fluid pressure generating device It is connected to 1B _4.

According to the fourth embodiment, the first to fourth embodiments
Since the on-off valve 83 operated by pilot pressure is used instead of the on-off valve 45 of the embodiment, the cost can be further reduced.

FIG. 11 shows a fifth embodiment of the present invention, in which parts corresponding to the above embodiments are given the same reference numerals.

This brake device comprises a brake fluid pressure control device 3A corresponding to the front left wheel brake _BFL and the right rear wheel brake _BRR , and a front right wheel brake B
_The actuator 92 having the electric motor 11, the accumulator 13, and the pressure regulating valve means 14 for regulating the output hydraulic pressure of the accumulator 13 are common to the brake fluid pressure control device 3 </ b _> B corresponding to the _FR and the left rear wheel brake BRL. And an output synthesizing means 93 for synthesizing the output hydraulic pressure of the actuator 92 and the output hydraulic pressure of the pressure regulating valve means 14.

The actuator 92 has a first output between a cylindrical housing 94 closed at both ends and a front end wall (left end wall in FIG. 11) of the housing 94 slidably fitted to the housing 94. A first output piston 95 forming a hydraulic chamber 97 and a second output piston 96 slidably fitted to the housing 94 and forming a second output hydraulic chamber 98 between the first output piston 95. And a pressing piston 99 integrally having a rod 99a coaxially connected to the back surface of the second output piston 96 and slidably fitted to the rear portion of the housing 94; A first return spring 100 provided between the housing 94 and the first output piston 95 to exert a spring force for urging the first output piston 95 axially rearward (to the right in FIG. 11).
And both output pistons 95, 96 in the second output hydraulic chamber 98.
A second return spring 101 provided between the second return spring 101 to exert a spring force for urging the second output piston 96 rearward in the axial direction (to the right in FIG. 11), and the electric motor 11 disposed at a fixed position.
And the rotational power of the electric motor 11
9, a power transmission mechanism 102 provided between the electric motor 11 and the rod 99a so as to convert the power into the axial power of the first hydraulic fluid 9 and the first output hydraulic pressure chamber 97 is communicated with the output hydraulic pressure path 2A.
The second output hydraulic chamber 98 communicates with the output hydraulic passage 2B.

The transmission mechanism 102 includes a driven gear 104 coupled to the rod 99a via a screw 103, and a drive gear 105 fixed to the output shaft 11a of the electric motor 11 and meshing with the driven gear 104. .

The electric motor 11 is fixedly mounted on the housing 94, and the driven gear 104 is mounted on the housing 94 such that its axial position is fixed.
It is supported rotatably.

A pair of balls 26, 26 is provided between the pressing piston 99 and the housing 94 in the same manner as between the piston 17 and the housing 16 in the first embodiment. The rotation of the driven gear 21 accompanying the operation of the electric motor 11 is slidably fitted to the housing 94 in such a manner that rotation about the axis is prevented but movement along the axis is permitted. , The pressing piston 99
Will move in the axial direction.

The first and second output hydraulic chambers 97 and 98 are
First and second output piston 95 and 96 is communicated with the reservoir R ₂ in the state (the state of FIG. 11) in the retracted limit position.

The output synthesizing means 93 is provided with the pressing piston 9
9 and a housing 94, and an annular input hydraulic chamber 106 facing the back of the pressing piston 99.
Is formed between the pressing piston 99 and the housing 94.

According to such an actuator 92 and the output synthesizing means 93, the electric motor 11 is operated, whereby the input hydraulic chamber 10 in the output synthesizing means 93 is operated.
6, the pressing piston 99 moves forward in accordance with the power exerted by the electric motor 11, and the output fluid is reduced as the volumes of the first and second output hydraulic chambers 97 and 98 are reduced. The hydraulic pressure in the pressure chambers 97 and 98 is increased, and the output hydraulic pressure chambers 9 are increased.
The hydraulic pressure of 7,98 acts on the output hydraulic pressure passages 2A, 2B. The input hydraulic chamber 10 in the output synthesizing means 93
When the hydraulic pressure acts on the push piston 6, the hydraulic pressure for further driving the push piston 99 forward from the forward position of the push piston 99 determined by the power exerted by the electric motor 11 acts on the push piston 99. From the hydraulic pressure chambers 97 and 98, a brake hydraulic pressure obtained by combining a hydraulic pressure determined by the operation of the electric motor 11 and a hydraulic pressure determined by the hydraulic pressure acting on the input hydraulic pressure chamber 106 is output. .

The output hydraulic pressure path 2A is connected to the accumulator 13 via the electromagnetic on-off valve 45 and the check valve 46, and is operated by operating the electric motor 11 of the actuator 92 without requiring a braking force. The hydraulic pressure output from the output hydraulic pressure chamber 97 is stored in the accumulator 13.

The pressure regulating chamber 48 of the pressure regulating valve means 14 is connected to the reservoir R ₂ via a relief valve 52, and the pressure regulating chamber 48
The output synthesizing unit 93 is connected to the input hydraulic chamber 106.

An intermediate portion of the brake operating member 30 is rotatably supported by a fixed support 66 via a first operation simulator 65 provided with an operating force detector 73. One end of a cable 67 is connected to the other end. The other end of the cable 67 is connected to one end of a link 69 via a second operation simulator 68, and the other end of the link 69 is connected to an input rod 50 connected to a piston 49 of the pressure regulating valve means 14. Linked to

According to the fifth embodiment, the actuator 92, the accumulator 13, the pressure regulating valve means 14, the output synthesizing means 93, the electromagnetic switching valve are commonly used for all the wheel brakes B _FL , B _RR ; B _FR , B _RL. Only one check valve 45, one check valve 46 and one cable 67 are required, and the number of parts can be reduced.

FIG. 12 shows a sixth embodiment of the present invention, and portions corresponding to the above embodiments are given the same reference numerals.

The sixth embodiment is similar to the fifth embodiment, except that the brake operating member 3 is different from the fifth embodiment.
0 is rotatably supported by a fixed support 66 via a first operation simulator 65, whereas a rod 107 connected to an intermediate portion of the brake operating member 30 is a pressing piston of the actuator 92. An operation force detector 73 is interposed at the center of the rod 107 and connected to the center of the back surface of the rod 99.

According to the sixth embodiment, the electric motor 11
The hydraulic pressure output from the actuator 92 in accordance with the operation of the actuator and the hydraulic pressure obtained by adjusting the output hydraulic pressure of the accumulator 13 by the pressure adjusting valve means 14 in accordance with the brake operating force of the driver. It is possible to add the fluid pressures to act on the wheel brakes B _FL , B _RR ; B _FR , B _RL , and even if the electric motor 11 and the pressure regulating valve means 14 break down, the driver's brake operating force Only the brake fluid pressure can be obtained.

FIG. 13 shows a seventh embodiment of the present invention, in which parts corresponding to the above embodiments are given the same reference numerals.

The brake device comprises a brake fluid pressure control device 3A corresponding to the front left wheel brake B _FL and the right rear wheel brake B _RR and a front right wheel brake B B
An actuator 112 having an electromagnetic switching valve 111 as an electric operating unit, an accumulator 13, and an output hydraulic pressure of the accumulator 13 are commonly controlled by the brake fluid pressure control device 3B corresponding to the _FR and the rear left wheel brake _BRL. The pressure regulating valve means 14 for pressure control and the output synthesizing means 113 for synthesizing the output hydraulic pressure of the actuator 112 and the output hydraulic pressure of the pressure adjusting valve means 14 are provided.

The actuator 112 amplifies the brake operating force of the master cylinder 114 and the brake operating member 30 in accordance with the switching operation of the electromagnetic switching valve 111 and drives the master cylinder 114 with the electronic control negative pressure booster 115.
It is composed of

The master cylinder 114 is a well-known one in the related art. The master cylinder 114 has a cylindrical cylinder body 116 having both ends closed, and is slidably fitted to the cylinder body 116 and has a front end wall (FIG. 13). Between the left end wall)
First output piston 117 forming output hydraulic chamber 119
And a second output hydraulic chamber 120 which is slidably fitted to the cylinder body 116 and between the first output piston 117.
And a cylinder body 116 and a first output piston 1 in a first output hydraulic chamber 119.
17, a first return spring 121 which exerts a spring force to urge the first output piston 117 rearward in the axial direction (to the right in FIG. 13), and a second return spring 121 in the second output hydraulic chamber 120. A second return spring 122 provided between the output pistons 117 and 118 to exert a spring force for urging the second output piston 118 rearward in the axial direction (to the right in FIG. 13); The pressure chamber 119 communicates with the output hydraulic pressure passage 2A, and the second output hydraulic pressure chamber 120 communicates with the output hydraulic pressure passage 2B.

The electronic control negative pressure booster 115 amplifies the brake operating force input from the input rod 123 connected to the intermediate portion of the brake operating member 30, and
24 to move the output rod 124 forward.
Is coaxially connected to the center of the rear surface of the second output piston 118 of the master cylinder 114.

In order to adjust the amplification degree in the electronically controlled negative pressure booster 115, the electromagnetic switching valve 111 is provided with a front side negative pressure chamber and a rear side variable pressure chamber in the electronically controlled negative pressure booster 115 (both in FIG. (Not shown), a state in which the negative pressure from the intake negative pressure section of the engine is introduced, a state in which the pressure in the negative pressure chamber and the pressure in the variable pressure chamber are maintained, and a state in which the negative pressure is introduced into the negative pressure chamber and It is possible to switch between three states, that is, the state where the atmosphere is introduced.

Further, an operation force detector 73 for detecting a brake operation force is provided at an intermediate portion of the input rod 123.
Is interposed.

The output synthesizing means 113 includes the master cylinder 1
14 second output piston 118 and cylinder body 116
An annular input hydraulic chamber 125 facing the back of the second output piston 118 is formed between the second output piston 118 and the cylinder body 116. Thus, the input pressure chamber 125 is provided with the pressure control chamber 48 of the pressure control valve means 14.
Is communicated.

According to the actuator 112 and the output synthesizing means 113, the electronically controlled negative pressure booster is operated by switching the electromagnetic switching valve 111 irrespective of the hydraulic pressure of the input hydraulic chamber 125 in the output synthesizing means 113. According to the brake operation force amplified in 115, the first
And both output pistons 117 and 118 move forward so as to reduce the volume of the second output hydraulic chambers 119 and 120, and the hydraulic pressure of both output hydraulic chambers 117 and 118 is reduced to the output hydraulic paths 2A and 2.
B. When the hydraulic pressure acts on the input hydraulic chamber 125 in the output synthesizing means 113, the hydraulic pressure for further driving the output pistons 117 and 118 forward from the position determined by the electronic control negative pressure booster 115 is applied to the second output piston 118. Therefore, the actuators 11 and 120 are actuated from both output hydraulic chambers 119 and 120.
The brake hydraulic pressure is output by combining the hydraulic pressure determined by the operation 2 and the hydraulic pressure determined by the hydraulic pressure acting on the input hydraulic chamber 125.

The output hydraulic pressure path 2A is connected to the accumulator 13 via the electromagnetic on-off valve 45 and the check valve 46. By switching the electromagnetic switching valve 111 of the actuator 112 without requiring a braking force, the output hydraulic pressure path 2A is switched. The hydraulic pressure output from the first output hydraulic chamber 119 is accumulated in the accumulator 13.

According to the seventh embodiment, the same effects as in the sixth embodiment can be obtained. In addition, the actuator 112 including the master cylinder 114 and the electronically controlled negative pressure booster 115 that performs an amplification operation in accordance with the switching operation of the electromagnetic switching valve 111 is a conventional brake device in which a driver performs a brake operation with his / her foot. Since it is used only by adding the accumulator 13, the pressure regulating valve means 14, and the output synthesizing means 113, application to a conventional brake device is easy.

As an eighth embodiment of the present invention, as shown in FIG. 14, a pressure adjusting valve means 14 is provided between the input hydraulic chamber 125 and the accumulator 13 of the output synthesizing means 113, instead of the pressure regulating valve means 14 in the seventh embodiment. a normally closed solenoid valve 79, it may be used composed of pressure regulating valve unit 78 in a normally open solenoid valve 80 provided between the input hydraulic pressure chamber 125 and the reservoir R _2.

Although the embodiments of the present invention have been described in detail, the present invention is not limited to the above embodiments, and various design changes can be made without departing from the present invention described in the appended claims. It is possible to do.

For example, instead of the configuration in which the hydraulic pressure in the output hydraulic chamber 18 is increased as the actuator 12 and the piston 17 of the output synthesizing means 15 move forward, the piston 17 directly operates the wheel brake, That is, the friction member of the wheel brake may be directly operated by the piston 17. In this case, the actuator 12
And the number of output synthesizing means 15 is provided as many as the number of wheel brakes.

Instead of the transmission mechanism 20 having the driven gear 23 and the driving gear 24, the piston 1
7 may be moved.

[0106]

As described above, according to the present invention, it is possible to prevent the mass consumption of electric energy while reducing the size of the actuator, and it is not necessary to set the output hydraulic pressure on the hydraulic pressure source side high. Since the power supply system, the input system, and the actuator system do not need to be duplicated, the overall configuration can be simplified, and an increase in cost and weight can be avoided.

[Brief description of the drawings]

FIG. 1 is a hydraulic circuit diagram showing an overall configuration of a vehicle brake device according to a first embodiment.

FIG. 2 is a hydraulic circuit diagram showing a configuration of a brake hydraulic pressure generator.

FIG. 3 is a sectional view taken along line 3-3 in FIG. 2;

FIG. 4 is an enlarged sectional view showing a part of the actuator.

FIG. 5 is an enlarged sectional view of the pressure regulating valve means.

FIG. 6 is a diagram showing a hydraulic pressure combining characteristic by an output combining means.

FIG. 7 is a diagram showing another example of the hydraulic composition characteristics by the output composition means.

FIG. 8 is a hydraulic circuit diagram corresponding to FIG. 2 of the second embodiment.

FIG. 9 is a hydraulic circuit diagram corresponding to FIG. 2 of the third embodiment.

FIG. 10 is a hydraulic circuit diagram corresponding to FIG. 2 of a fourth embodiment.

FIG. 11 is a hydraulic circuit diagram showing an overall configuration of a vehicle brake device according to a fifth embodiment.

FIG. 12 is a hydraulic circuit diagram showing an overall configuration of a vehicle brake device according to a sixth embodiment.

FIG. 13 is a hydraulic circuit diagram showing an overall configuration of a vehicle brake device according to a seventh embodiment.

FIG. 14 is a hydraulic circuit diagram showing an overall configuration of a vehicle brake device according to an eighth embodiment.

[Explanation of symbols]

11 ... Electric motor as electric actuating part 12,92,112 ... Actuator 13 ... Accumulator as hydraulic pressure source 14,78 ... Pressure regulating valve means 15,93,113 ... Output synthesizing means _BFL , _BFR , _BRL , _BRR: Wheel brake

Claims (1)

[Claims] An electric operating part (11, 111) that operates in response to an electric input and includes the electric operating part (1).
In a vehicle brake device including an actuator (12, 92, 112) capable of outputting a braking force in accordance with the operation of a hydraulic pressure source (1, 111), a hydraulic pressure source (13) and a hydraulic pressure source (1
Pressure regulating valve means (14, 78) for regulating the output hydraulic pressure of 3)
And the output of the actuator (12, 92, 112) and the output hydraulic pressure of the pressure regulating valve means (14, 78) can be combined and applied to the wheel brakes (B _FL , B _FR , B _RL , B _RR ). A vehicle brake device comprising an output synthesizing means (15, 93, 113).