JPS60107445A - Hydraulic pressure brake gear - Google Patents

Abstract

(57) [Summary] This bulletin contains application data before electronic filing, so abstract data is not recorded.

Description

Detailed Description of the Invention "Industrial Application Field" The present invention provides an auxiliary energy supply device, a mask cylinder provided with a booster piston actuated by the auxiliary energy supply device, and a mask cylinder formed in the mask cylinder, The present invention relates to a hydraulic brake device having a pressure chamber that slidably accommodates the booster piston, and a wheel brake cylinder.

[Prior Art] In the above-described hydraulic brake system, the effective area for pressurizing the wheel brake cylinder does not change even when the auxiliary energy supply system fails. Therefore, in the event of a failure of the auxiliary energy supply, a very high force must be applied to the brake pedal in order to slow down the wheels.

[Problems to be solved by the invention] 5- The purpose of the invention is to improve the conventional hydraulic brake,
To provide a fluid pressure brake device capable of obtaining a predetermined braking force even if the force of pressing a brake pedal is reduced.

[Means for Solving the Problems] The present invention provides that when the auxiliary energy supply device is normal, the effective area of the booster piston that pressurizes the inside of the wheel brake cylinder is the same as that of the booster piston when the auxiliary energy supply device is malfunctioning. It is characterized in that the effective area is larger than the effective area of . Therefore, when the auxiliary energy supply device malfunctions, the effective area of the booster piston becomes smaller and the travel distance of the booster piston and brake pedal becomes larger, so even if the force with which the brake pedal is depressed is reduced, the desired braking force can be obtained. be able to.

In an embodiment of the invention, the end of the master cylinder is provided with a brake valve that allows pressure medium to flow out of the auxiliary energy supply device and is actuatable by a brake pedal, and the pressure medium passes through a check valve. flow into the pressure chamber, the mask cylinders being in communication with each other via a hydraulically switchable valve that is open when unpressurized and controlled by a brake valve, and the mask cylinder is in communication with the housing and the booster piston via a hydraulically switchable valve that is open when not pressurized and is controlled by a brake valve. a first chamber and a second chamber defined by the pressure medium, and when the booster piston moves to bring the first chamber and the second chamber into communication, a portion of the pressure medium is
A part of the pressure medium flows from the first chamber into the second chamber and flows out into the pressure chamber communicating with the wheel brake cylinder through said check valve, when the auxiliary energy supply device is malfunctioning. At this time, the first and second chambers are in communication with the reservoir. Also, a solenoid valve is disposed in a brake circuit connected to the mask cylinder to control fluid pressure in the wheel brake cylinder, and the wheel brake cylinder is in communication with a return circuit connected to the reservoir.

The mask cylinder is a tandem mask cylinder including two pressure chambers, and a floating piston is disposed between the two pressure chambers. 1
Even if one brake circuit fails, brake slip can be controlled in other brake circuits.Furthermore, according to an embodiment of the present invention, the first and second chambers are opened when not pressurized. , communicates with the reservoir via a hydraulically controlled directional control valve.

A valve arrangement is further provided, the valve arrangement including a valve seat that slides between the first and second stoppers under fluid pressure, and a valve body with a spring connected thereto. a first valve that controls communication between the first pressure chamber and the second pressure chamber;
A closure member is formed and includes a control member fluidically abutting the third stopper and a valve seat secured to the housing, the control member controlling communication between the third pressure chamber and the second pressure chamber. a first spring supported between the housing and the valve seat; and a second spring supported between the valve seat and an extension of the control member passing through the other valve seat.
and a spring.

According to an embodiment of the invention, a distance until the closing member seats on the valve seat is smaller than a distance until the extension of the control member abuts the valve body.

After the valve seat and the valve body have moved a predetermined distance, the extension part of the control member is away from the valve body when, on the one hand, the control member rests against the stopper, but on the other hand, the closing member of the control part When the valve body is seated on the other valve seat, the valve body is pushed by the extension.

The valve structure is a quick-make valve.

"Example" Hereinafter, one embodiment of the present invention will be described based on the drawings.

As shown in FIG. 1, the hydraulic brake device according to the present invention includes a unit 1, a first valve device 2, an auxiliary energy supply device 3, and a second valve device 4, each surrounded by a dotted line. has.

This first valve device 2 is a 2-point, 2-position control valve 14, 15, 16, 17, 18, 19, 20, 2 which is a solenoid valve.
1. Control valves 14.15.16.17 are of the normally open type, and control valves 18.19, 9-20.21 are of the normally open type. The brake cylinders of the right front wheel 10 and the left rear wheel 11 are connected to the brake circuit (2), and the brake cylinders of the left front wheel 12 and the right rear wheel 13 are connected to the brake circuit (2). Furthermore, these brake cylinders can communicate with a return circuit connected to the reservoir 4. Sensors (not shown) measuring the rotational speed of the wheels are connected to control valves 14.15.16.17.18.19 to control brake slip.
．． It is necessary for the control circuit that sends the control signal at 20.21.

The unit 1 includes a brake valve 22, a pressure chamber 24.
25, 26, the pressure chamber 26 has a first chamber 27 and a second chamber 28. The brake valve 22
constitutes a small power brake booster. When the brake pedal 29 is depressed, the brake pedal 29
The force F applied to the bushing rod 30 and the bushing 10 through the rod piston 31 causes the mutual joints to tighten together with the bolt 3.
The force transmitted to the lever 32.33 is transmitted to the two levers 32.33 connected by the brake valve 22.
is transmitted to the control piston 35 of. The force required to move the booster piston 40 of the brake valve 22 is significantly greater than the force required to move the control piston 35, and the force F causes the lever 32 to pivot and move the control piston 3.
5 moves to the left in FIG. 1, the auxiliary energy supply device 3 communicates with the booster chamber 39 via the inlet 37 and the internal bore 38 in the control piston 35. When the brake is not applied, the booster chamber 39 is in communication with the reservoir 41 via the opening 36, but just before the auxiliary energy supply device 3 is connected to the booster chamber 39, the opening 36 is connected to the control piston 35. The booster chamber 39 is closed and the communication between the booster chamber 39 and the reservoir 41 is cut off. Accordingly, the fluid pressure within the booster chamber 39 increases, causing the booster piston 40 to move to the left and forcing the bush rod piston 31 to move to the right due to its effective area.

The auxiliary energy supply device 3 has a pump 45 driven by a motor, a filter 47 and an accumulator 48 connected to the reservoir 41 via a relief valve (not shown). A check valve 46 is connected to prevent the pressure medium flowing out from 45 from flowing backward.

The fluid pressure in the accumulator 48 and the auxiliary energy device 3 other than the accumulator 48 is monitored by two fluid pressure alarm switches. The first fluid pressure alarm switch is for warning the upper limit of the fluid pressure boundary value,
When this fluid pressure alarm switch alarms, it indicates an error in the auxiliary energy supply device 3, the chamber connected to the auxiliary energy supply surface 3, or the brake circuit.

When the second fluid pressure alarm device that alarms the lower limit of the fluid pressure boundary value does not alarm, brake slip can be controlled.

As will be explained below, the pressure chamber 24.25.26 is defined by a booster piston 40, a piston 55 fixed to the housing, a 70-ring piston 54, and a wall of the hanging. The small diameter portion 50, which has a shape and an effective area Fl of this booster piston 40, is connected to the unit 1 of the housing.
The booster piston 40 is slidable against the side wall.
The large diameter portion 51 having an effective area F2 is slidable in a stepped bore 49 formed on the tandem mask cylinder 23 side of the housing.

The pressure chamber 25 communicating with the brake circuit I has a recess 52 extending in the axial direction and opening at one end side of the large diameter portion 51.
It is formed by closing the recess 52 with a floating piston 54 that is slidably provided on the opening side of the recess 52 . Due to the sleeve 58 acting as a check valve, no pressure medium can flow out from the pressure chamber 25 into the pressure chamber 27;
and the pressure medium is transferred from the pressure chamber 27 to the pressure chamber 25.
flow into. Radial bore 53 and booster piston 4
Pressure medium flows out of the pressure chamber 25 into the brake circuit (2) via the annular groove (2). The pressure chamber 24, which communicates with the play 13-main circuit (■), has a peripheral surface formed by a small diameter portion of a stepped bore 49, and is connected to the pressure chamber 24.
4 is closed in a sealed state by a piston 55, and the other end is a slidable floating piston 54.
It is closed in a sealed state. The piston 55 and the floating piston 54 are formed to have the same radius.

The end face of the piston 55 remote from the pressure chamber 24 is acted upon by fluid pressure. On the circumferential surface of the piston 55,
A sleeve 56 is provided which acts as a check valve and allows pressure medium to flow into the pressure chamber 24 . Since the floating piston 54 does not have a stepped part, the effective area F3 of the floating piston 54 projecting into the pressure chamber 24.25 is equal. The first chamber 27 of the pressure chamber 26 includes the inner surface of the large diameter portion 60 of the stepped bore 490, the end surface of the large diameter portion 51 of the booster piston, the shoulder 60 of the stepped bore 49, and the outer peripheral surface of the floating piston 54. It is formed by the following.

The second chamber 28 of the pressure chamber 26 has a stepped bore 4
the inner surface of the two large diameter portions 60; the shoulder portion of the stepped portion of the booster piston 40; the inner surface of the housing facing the shoulder portion of the booster piston 40; and the small diameter portion 5 of the booster piston 40.
0 outer surface. As will be described later, the first chamber 27 of the pressure chamber 26 is connected to the second chamber 27 via a conduit.
The chamber 28 can be communicated with.

The valve device 4 includes a controllable coupling valve 70 shown enlarged in FIG. 2, a check valve 71, a directional control valve 72.73 controllable by fluid pressure, and a control valve 14.15. .17.1
8.19.20, 21, and a two-position switching valve 74 for controlling the supply of pressure medium and reducing the fluid pressure, and this control valve 74 is a solenoid valve. The achievement valve 70 has a horizontally symmetrical shape. In the bore 75 having a plurality of stepped portions on the left and right sides from the plane of symmetry, a ball-shaped valve body 83.83'
is biased by a compression spring connected to both valve bodies 83, 83'. A valve seat 86 that slides between a first stopper 84 and a second stopper 85, and a first stopper 84'
and a second stop 85', the valve seats 86' each have a central passage and a second, first compression spring 87, 88 and a second, first compression spring, respectively. 87', 88', these compression springs 87, 87- also bias control members 89 and 89'. The cold parts 90,90' each seat on valve seats 91,91' fixed to the housing.

The valve seats 86, 86- are compressed by the compression springs 88, 88' respectively supported by the housing, so that the valve bodies 83, 83'
, that is, in the direction of the plane of symmetry in FIG.

One end of the compression spring 87, 87' is connected to the valve seat 86.
86-, and the other ends of the compression springs 87, 87' abut extensions 89, 89-, respectively.

The control members 89,89- are connected to the pressure chambers 92,92, respectively.
- has an end face defining one end side in a sealed state, and the diameter of each of these end faces is larger than the diameter of the valve seat 91,91'. When there is no pressure medium in the pressure chambers 92, 92', the control members 89, 89' each have a second compression spring 87
．． Due to the spring force of 87', it is brought into contact with a third stopper 93,93' fixed to the housing. At this time, the closed portion 90.90' of the control member 89.89- is
They are each a distance S1 from the valve seats 91 and 91-. The extension portion 94.94' of the control member 89.89' is connected to the valve seat 9.
L 91- can be passed through and abutted against the valve body 83, 83'.

The control member 89, 89' rests on the stop 93, 93', and the valve seat 86, 86' respectively contacts the first stop 84, 84'.
-, the extensions 94,94' are separated from the valve body 83,83- by a distance S2, respectively, and the valve seat 86,86' is at a distance S2. Only 1lS3 second stopper 85
．． It is far from 85'. Valve seat 86.86' is distance 111
When it has moved by ts3 and is in contact with the second stopper 85.85', the distance 1IltS2 becomes small. valve seat
86.86- moves by a distance [83] and comes into contact with the second stopper 17 = 85.85', and the closing portions 90, 90' touch the valve seat 9
When in contact with 1.91-, the valve body 83.83-
The respective extensions 92,92' do not seat the valve seats 86,86', leaving the valve open.

Boats 95,96,96-198,98' are each connected to bore 75. Boat 95 has valve seat 86.86
- is connected to a pressure chamber 100 formed between. The boat 96.96' is connected to a pressure chamber 101.101' formed between the two passages. The boat 97.97- is connected to a pressure chamber 92.29', and the boat 98.98' is connected to a pressure chamber 102.102- which is closed by a closing part 90.90=. The function of the coupling valve 70 will be described later, and the unit 1 is connected to the valve device 2 as described later.

From the pressure chamber 39 of the brake valve 22, a line 110 connects directly to the control port of the directional control valve 72 and directly to the first port of the switching valve 74. control valve 74
From the second boat of
It is connected to the control port 1 of the control valve 73 via the conduit 112. Ports 98, 98- of the coupling valve 70 are connected to the reservoir 41 via lines 113, 114, respectively, and to the first bow 1 of the control valve 72 are connected to the reservoir 41 via lines 114. ing. Port 96 of coupling valve 70
- is connected to the end face of the piston 55 on the side remote from the pressure chamber 24 via a conduit 115. Achievement valve 70
The port 97' of the pressure chamber 2 is connected to the pressure chamber 2 via the conduit 116.
4, port 97 is connected to pressure chamber 25 via conduit 117.

The conduit 118 is connected from the port 96 via the check valve 71 to a conduit 119, which is connected to the second
and a first chamber 27 of the pressure chamber 26 . A conduit 120 branching from the conduit 119 is connected to a first port of the control valve 73 that is in communication with the second chamber 28 of the control chamber 26 and is connected to the first port of the control valve 73 and the second chamber 28 of the control chamber 26 . Communication with the chamber 28 is controlled by this control valve 73. A check valve 71 located between the two ports of the control valve 72 allows pressure medium to flow through the line 11.
9 into the conduit 118.

When this hydraulic brake system is not activated, the opening of the central valve of pressure chamber 24 is connected to line 115, port 9.
6', passage closed by the closing portion 90-, port 98-1
and communicates with the reservoir 41 via a conduit 113.

Additionally, the central valve opening of pressure chamber 25 is connected to first chamber 27, line 119, control valve 72, and line 114.
It communicates with the reservoir 41 via. Brake slip control of this brake device will be described later. This fluid pressure brake device initially operates in a state where brake slip control is not performed.

When the brake pedal 29 is depressed, the control piston 35
Pressure medium from the auxiliary energy supply device 3 flows into the booster chamber 39 via the booster chamber 3
As the fluid pressure within 9 increases, this increased fluid pressure causes booster piston 40 to move to the left in FIG. Fluid pressure within the three booster chambers is communicated via line 110 to the pressure chamber of directional control valve 72, which causes directional control valve 72 to open. Further, when brake slip is not controlled, the switching valve 74 will not open even if fluid pressure is transmitted to the port of the control valve 74. Therefore, since fluid pressure is not transmitted to the control port of the control valve 73,
The directional control valve 73 remains open.

As the booster piston 40 moves to the left, pressure medium from the first chamber 27 flows into the second chamber 28 via the control valve 73, which opens the line 119.1201. These first and second chambers 27,28 are necessary for a hydraulic brake system. The flow rate of the pressure medium flowing from the first chamber 27 to the second chamber 28 depends on the distance of movement of the booster piston 40 and the flow rate of the pressure medium flowing into the second chamber 28.
It is determined by the circumferential surface that forms the . Further, the pressure 21-medium whose flow rate is determined by the moving distance of the booster piston 40 and the circumferential surface forming the pressure chamber 25 is transferred from the first chamber 27 through the sleeve 58.
into the pressure chamber 25. The flow of pressure medium into the pressure chamber 25 causes a rapid movement of the 70-ring chamber 54 compared to the movement of the booster piston 40. When the brakes are applied, fluid pressure in the wheel brake cylinders in each wheel increases.

In this state, the quick-make valve 70 operates as follows. Via lines 116.117, pressure medium flows from the pressure chambers 24.25 into the pressure chambers 92-192, so that the closing parts 90', 90 are seated on the valve seats 91', 91, respectively. Since the switching valve 74 is closed, no pressure medium flows into the port 95, so that the spring 88.88-
Due to the spring force of , the valve seat 86.86- remains in contact with the first stop 84.84'. Port 96.
Since no pressure medium flows into the valve seat 86.96-.
The passages formed in each of 86' are closed.

Below, the fluid pressure valve 22- with controlled brake slip The operation of the rake device will be explained.

Control valve 18.19.20.2 by the signal from the control circuit
When any one control valve 1 is energized, the switching valve 7
4 is opened, pressure medium flows into the control port of the directional control valve 73 via the line 111, 112, so that the directional control valve 73 is closed.

At the same time, pressure medium flows into the pressure chamber 100 of the coupling valve 70 via the port 95 . Therefore, the valve seat 86.8
6- is the compression spring 8 with the valve bodies 83 and 83-, respectively.
The second stopper 85.85 moves in the opposite direction to the biasing direction of the second stopper 85.88'. Since the closing portion 90.90- is seated on the valve seat 91.91-, the valve body 83.8
3- are in contact with the extension portions 94 and 94-, respectively, and the valve body 83
．． 83- is removed from the valve seat 86, 86'. Therefore, pressure medium flows from the booster chamber 39 into the pressure chamber 100 via the line 110, the switching valve 74, the line 111 and the port 95; 'Boat 96', conduit 11
5 and a sleeve 56 designed as a check valve into the pressure chamber 24 of the brake circuit (2). The pressure medium flowing into the pressure chamber 100 flows through the port 96, the conduit 118, the check valve 71, and the first chamber 27 on the other hand.
, and via a sleeve 58 configured as a check valve.
It flows into the pressure chamber 25 of the brake circuit (2). Pressurization of the wheel brake cylinder is possible with both brake circuits ■ and ■. When the direction control valve 73 is closed, communication between the second chamber 28 and the booster chamber 39 is cut off, and the position of the brake pedal 29 is maintained as it is.

Here, it is assumed that one of the brake circuits (■) and (2), for example, the brake circuit (■) has failed.

When there is no brake slip control and the brake is operating, the switching valve 74 and the direction control valve 72 are closed and the direction control valve 73 is open, so the port 9 of the coupling valve 70 is closed.
5. No fluid pressure is transmitted to the pressure chamber 92-. At this time, the control member 89- is brought into contact with the stopper 93' by the spring 87', and the closing portion 90- is separated from the valve seat 91', so that the pressure chamber 101-1102-
is in communication with the reservoir 41. Furthermore, the valve body 83' is seated on the valve seat 86-, and the valve seat 86- is brought into contact with the stopper 84' by the biasing force of the spring 88'. Brake operation is possible in brake circuit (2). These conditions are the same even when the brake circuit (2) is out of order.

Furthermore, if brake circuit (2) fails while brake slip is being controlled, the following situation will occur.

The switching valve 74 is opened and the directional control valves 72,73 are closed, so that the pressure medium in the booster chamber 39 flows into the port 95 of the completion valve 70. And pressure chamber 9
2- is not pressurized, the control member 89- is pressed against the stopper 9.
Contact with 3-. Due to the fluid pressure in the pressure chamber 100, the valve seat 86- is moved together with the valve body 83- to the second stopper 85'.
The valve seat 86' moves in the direction of the second stopper 85'.
comes into contact with. At this time, the extension member 94- is still attached to the valve body 83.
-, the valve body 83' is seated on the valve seat 25-86-. In this hydraulic brake system, it is important that the outflow of the pressure medium to the brake circuit (2) through the valve seat 86' can be blocked. These conditions also apply when the brake circuitry malfunctions.

Here, a case where the auxiliary energy supply device 3 breaks down will be explained.

Since no pressure medium flows into the control port of the directional control valve 72.73, the directional control valve 72.73 is open. The first chamber 27 and the second chamber 28 communicate with the reservoir 41 via the open direction control valve 72 and the conduit 114, so that the pressure medium flows into the pressure chamber 26.
The water flows into the reservoir 41 from there. In this state, it is easy to move the brake pedal 29 and increase the fluid pressure in the wheel brake cylinder communicating with the pressure chamber 24.25. Let me briefly explain this function again.

As described above, if the auxiliary energy supply device 3 is not malfunctioning, the brake piston 40 has an effective area F in the axial direction.
It moves due to the pressure applied to 1. The effective area F1 of this 26- is equal to the sum of the effective area F3 defining the pressure chamber 25 and the effective area Fl-F3 defining the pressure medium flowing into the pressure chamber 25 via the sleeve 58. When the auxiliary energy supply device 3 is out of order, the pressure medium whose flow rate is determined by the circumference of the effective area F1-F3 and the moving distance of the booster piston 40 flows into the reservoir 41, so that the booster piston 40 is not activated. It has only an effective area F3 smaller than the area F1. At the same time, in this hydraulic brake device, a smaller effective area,
Greater travel of the booster piston 40, less force on the brake pedal, and the 30% wheel deceleration required when the auxiliary energy supply fails can be obtained. .

[Brief explanation of drawings]

FIG. 1 is a block diagram showing an embodiment of the hydraulic brake device of the present invention, and FIG. 2 is an enlarged view showing the achieving valve of FIG. 1.

Claims (9)

[Claims] (1) an auxiliary energy supply device; a mask cylinder equipped with a booster piston operated by the auxiliary energy supply device; a pressure chamber formed within the mask cylinder and slidably housing the booster piston; and a wheel. In a fluid pressure brake device having a brake cylinder, when the auxiliary energy supply device is normal, the effective area of the booster piston that pressurizes the inside of the wheel brake cylinder is equal to the effective area of the booster piston when the auxiliary energy supply device is malfunctioning. A hydraulic brake device characterized by being larger. (2) A brake valve is provided at the end of the master cylinder to allow pressure medium to flow out from the auxiliary energy supply device and to be actuatable by a brake pedal, and the pressure medium flows into the pressure chamber via a check valve. , the mask cylinders are in communication with each other via hydraulically switchable valves that are open when unpressurized and are controlled by a brake valve, and the mask cylinders are in communication with each other through valves that are open when unpressurized and are switchable by hydraulic pressure controlled by a brake valve, and the mask cylinders are in communication with each other through a hydraulically switchable valve that is open when unpressurized and is controlled by a brake valve. a chamber and a second chamber, and when the booster piston moves and the first chamber and the second chamber communicate with each other, a portion of the pressure medium is transferred from the first chamber to the second chamber. The other part of the pressure medium flows into the pressure chamber which communicates with the wheel brake cylinder via the check valve, and when the auxiliary energy supply device fails, the first and second chambers 2. The hydraulic brake device according to claim 1, wherein the hydraulic brake device communicates with the reservoir. (3) Claims characterized in that the mask cylinder is a tandem mask cylinder including two pressure chambers, and a floating piston is disposed between the two pressure chambers. The fluid pressure brake device according to item 2. (4) A solenoid valve is disposed in a brake circuit connected to the mask cylinder to control the fluid pressure in the wheel brake cylinder, and the wheel brake cylinder is in communication with a return circuit connected to the reservoir. A fluid pressure brake device according to claim 2 or 3, characterized in that: (5) The valve controllable by fluid pressure is a directional control valve that is opened when not pressurized and is controlled by fluid pressure. The fluid pressure brake device according to item 1. (6) A valve component is provided, the valve component includes a valve seat that slides between the first and second stoppers by fluid pressure, and a valve body connected to a spring. a first valve that controls communication between the first pressure chamber and the first pressure chamber; a control member in which a closing member is formed and abuts against a third stopper by fluid pressure; and a valve seat fixed to the housing. a second valve that controls communication between the third pressure chamber and the second pressure chamber; a first spring supported between the housing and the valve seat; a valve seat; and another valve. and a second spring supported between the control member and the extension portion of the control member passing through the seat. Hydraulic brake system. (7) The distance until the closing member seats on the valve seat is smaller than the distance until the extended portion of the control member comes into contact with the valve body. Hydraulic brake system. (8) After the valve seat and the valve body have moved a predetermined distance, when the control member is in contact with the stopper,
Claims characterized in that the extension part of the control member is spaced apart from the valve body, but on the other hand, when the closing member of the control part is seated on the other valve seat, the valve body is pushed by the extension part. The fluid pressure brake device according to item 7. (9) The fluid pressure brake device according to claim 8, wherein the valve device is an achievement valve.