JPH02237858A - Brake hydraulic pressure controller for vehicle - Google Patents

Abstract

PURPOSE:To obtain a sufficient brake pressure by installing an opening/closing valve between the hydraulic pressure chamber of an auxiliary hydraulic pressure generating means and a brake device and installing a unidirectional hydraulic pressure transmission means in the intermediate part of a hydraulic passage leading from a hydraulic pressure feeding source to the brake device through a hydraulic pressure feeding source hydraulic pressure control means. CONSTITUTION:When a high hydraulic pressure can not be obtained from a hydraulic pressure feeding source 2 because of the trouble of a hydraulic pump 11, etc., in brake application, opening/closing valve 911 and 912 are opened according to the lowering of the hydraulic pressure in an oil passage 71 communicating to a hydraulic pressure feeding source hydraulic pressure control means 3. Therefore, the control hydraulic pressure generated by an auxiliary hydraulic pressure generating means 6 directly acts onto the brake devices BFL-BRR, and a brake power can be secured. Since, in this case, unidirectional hydraulic pressure transmission means 4FL-4RR are interposed between the brake devices BFL-BRR and the control means 3, the release of the brake pressure of the brake devices BFL-BRR to the control means 3 side is prevented. Further, if the hydraulic pressure feeding source 2 fails, the brake hydraulic pressure directly acts onto the right and left rear wheels from the hydraulic pressure generating means 6, and a sufficient brake power can be secured.

Description

Detailed description of the invention A6 Object of the invention (1) Industrial application field
6. Related to a brake hydraulic pressure control device in which a hydraulic pressure supply source hydraulic control means capable of controlling hydraulic pressure from a hydraulic pressure supply source according to the amount of braking operation is interposed (2) Conventional technology Conventionally, such a device has been developed by, for example, It is publicly known from Publication No. 52-187 and the like.

(3) Problems to be Solved by the Invention In the conventional system, the braking pressure of the brake device is controlled by the hydraulic pressure control means of the hydraulic supply source. If for some reason there is a malfunction and sufficient supply source oil pressure cannot be secured,
7-It is difficult to apply sufficient braking pressure to the key device 2: It becomes difficult.

The present invention has been developed in view of the above circumstances. It is an object of the present invention to provide a brake hydraulic pressure control device capable of obtaining sufficient braking pressure even when sufficient source hydraulic pressure cannot be secured.

B. Structure of the Invention (1) Means for Solving the Problems The device of the present invention has an operating screw 1, which is interlocked and connected to a flake pedal and is slidably fitted into a housing so as to move forward in response to a braking operation. In response to the forward movement IJ of the operating screw 1, a hydraulic chamber is formed in the housing with the front end surface of the operating screw 1 facing the front end surface of the operating screw 1 in order to shrink the -ζ volume. -4 An opening/closing valve that is interposed between the hydraulic chamber of the generating means and the brake device and opens and closes in response to the output hydraulic pressure of the hydraulic pressure supply source hydraulic control means; It is installed in the middle of the hydraulic path leading to the brake device via the hydraulic pressure source, and enables hydraulic transmission of the output hydraulic pressure from the hydraulic pressure control means to the brake device when the hydraulic pressure from the hydraulic pressure source is normal, and when the hydraulic pressure from the hydraulic source is abnormally low. A four-directional hydraulic pressure transmission means is provided, which disables the flow of hydraulic oil from the device to the hydraulic pressure supply source side.

(2) Effect According to the above configuration, during normal braking, the oil pressure from the oil pressure supply source is controlled by the oil pressure source oil pressure control T stage and given to the brake device, and the oil pressure supply source becomes malfunctioning. Sometimes, when the on-off valve opens, hydraulic pressure from the auxiliary hydraulic pressure generating means is applied to the brake device, and when the on-off valve opens, the hydraulic pressure of the brake system is prevented from escaping to the hydraulic pressure supply source by the one-way hydraulic transmission means. Therefore, sufficient braking pressure can be obtained.

(3) Example? Below, an embodiment in which the present invention is applied to a front wheel drive vehicle will be described with reference to the drawings.

The left front wheel and right front wheel of the vehicle are equipped with the left front wheel braking device BFt and the right front wheel play 4: device B F II, respectively, and the left rear wheel and right rear wheel are equipped with a left rear wheel brake. A brake device WB*t and a right wheel brake device BIIl are respectively installed. On the other hand, the brake pedal 1 is supplied with hydraulic pressure 'tI. A hydraulic pressure supply source hydraulic control stage 3 is connected to control the hydraulic pressure of the oil pressure source 2 according to the amount of braking operation, and during normal braking, the hydraulic pressure from the hydraulic oil supply source hydraulic control stage 3 is transmitted to the one-way hydraulic pressure transmission means 4FLl4. ■C pressure is increased and given to each front wheel brake system iZBrt, B■,
After the hydraulic pressure from the hydraulic pressure supply source hydraulic control stage 3 is controlled by the proportional pressure reducing valve 5, the hydraulic pressure is transferred to the one-way hydraulic pressure transmission means 4 II+. ，
The pressure is increased at 41R and the brake system for each rear wheel i1fB*
t, given to Bm+i.

In addition, the hydraulic pressure supply source hydraulic pressure control means 3 includes a brake valve? le 1
The auxiliary hydraulic pressure generation means 6 that outputs the amount of depression (the amount of pressure applied to the lever) are interlocked and connected. Hydraulic pressure is applied to each block ii!tByL, BFIl.
B■-, B■c4 can be obtained. Inflow valves 77F+-, 7■ and outflow valves F'8F+.
．． , 8■ and both rear wheels' front brake device B RLI
B ++t+6 Common number 1'Inflow valve 7,
l and outflow valve 8, each brake device B, . ,B■
Anti-lock control is performed by holding or reducing the braking hydraulic pressure of +B)l t+B*m, and the inflow valve 9 for 1.Luxigon control and the outflow valve 10 for traction control Ill are used to perform anti-lock control. When braking, each brake device i?npt, Bllll, B.I..B
*i+control a oil} E can be increased to perform [・lactic 5in control].

Hydraulic supply R2 is connected to hydraulic bomb j1 that pumps hydraulic oil from reservoir R and its hydraulic bomb l1δ.
2 and a pressure switch 13 for controlling the operation of the hydraulic bomb l1.

The hydraulic pressure supply source hydraulic control means 3 has one axial end connected to the end wall 15a.
a first housing 15 forming a first cylinder hole 16 that is closed by a pressure screw 17 that is slidably fitted into the first cylinder hole 1G; A spring 18 is compressed between the first housing 15 and the pressure screw 1/n 17 to bias the hydraulic pressure supply R2 to the side.
an annular manual hydraulic pressure chamber 19 which communicates with the input hydraulic pressure chamber 19 and is defined between the pressure piston 17 and the first housing 15; An annular output hydraulic chamber 20 defined between the housing 15
and an anti-fungal screw t which is connected to the brake pedal 1 and allows relative sliding in the axial direction 2 and is fitted into the pressure piston l7.
21, pressure screws 17 and anti-cavity screws 1 and 2.
The first and second control hydraulic chambers 22a and 2 are provided between
2b, the inlet valve 2 (3, upper and An output L1 valve 24 is provided.

On the outer surface of the pressure screw 1・n 17, the 18% 7 ring 15
Two annular grooves are provided to define an input oil pressure chamber 19 and an output oil pressure chamber 20 between the pressure piston 17 and the inner surface of the input oil pressure chamber 19 and the output oil pressure chamber 20, respectively. Each space between the first housings 15 is sealed. Further, a spring chamber 25 is formed between the pressure piston 17 and the other end of the first housing 15, and the spring 18 housed in the spring chamber 25 is activated by the pressure screw 1'7.
is biased in one axial direction (to the right in the drawing).In the first housing 15, there is a pressure screw connected to the input hydraulic chamber 19 regardless of the axial position of the pressure screw 17. Ruin Kabo }2
6. Output bows 1 and 27 leading to the output hydraulic chamber 20 and release bows 1 and 2 leading to the spring chamber 25 are provided,
The input bow 26 is connected to the hydraulic supply source 2, and the release bow 1
= 2 8 beams are connected to the server.

The pressure screw 1-17 has an open end 1 and a screw 1 at one end in the axial direction.
Four bottom sliding holes 29 are drilled coaxially, and the countercapiston 21 is slidably fitted into the sliding holes 29. The tip of a pressing rod 30 which is driven by the brake pedal 1 is connected to the rear end of the brake piston 21, and the brake pedal 1 drives the brake pedal 1 in the axial direction.

A first control hydraulic chamber 22a is defined between the tip of the pressure piston 21 and the closed end of the sliding hole 29, and the inner surface of the pressure piston l7 is closer to the rear end and the outer surface of the pressure piston l7 is closer to the rear end. An annular second control hydraulic chamber 22b is defined therebetween. In addition, a communication passage 31 is provided in the reaction force sensor 1-21 to communicate between the first and second control hydraulic chambers 2:la, 22b, and the first control hydraulic chamber 22a is always connected to the output hydraulic chamber 20. communicated. In the first control hydraulic chamber 22a, the first
A spring 32 is housed therein to elastically bias the anti-mold stone 21 in a direction in which the volumes of the second control hydraulic chambers 22a, 22b increase.

The large mouth valve 23 communicates with the manual hydraulic chamber 11 [C] through the inner surface of the sliding hole 29 (D I), which communicates with the valve hole 33 bored in the pressure piston l7 and the communication path 31. The valve hole 34 is formed in the anti-cavity stone 21 while being open to the outside surface.7 When both the valve holes 33 and 34 are shifted in the axial direction, the valve becomes closed, and both valve holes Valve hole 33,3
When the valves 4 and 64 are in corresponding positions, the valve is said to be in an open state. Also, the exit valve 24 communicates with the spring chamber 25 and opens inward in the sliding hole 29? 1 and 2 pressure screws 1 and 7
The valve fitting 352 is drilled in the valve hole 352, and the valve hole 3G is drilled in the 9 cavities 1 and 2l. hole 35,3
When the position of 6 is 1, the valve is not in the closed state, and when both the valve holes 35 and 36 are in the corresponding position, the valve is in the open state.

Therefore, it is not shown on the IA plane, 1:・Uni pressure crack 1・N 1■ is at the backward limit position U', and anti-capiz 1■ 7 2 1
f) Backward 1'lJ position 1, when this is done: 'Inlet valve 23
is in the closed state and the outlet valve 24 is in the open state, and from the second state, anti-mold! -'/2 When 1 moves forward, the outlet valve 24 closes j7 and then the inlet valve 2.3 opens. As a result, the first and second control hydraulic chambers 22a.
When the FE force at 22h increases and the pressure screw 17 moves forward relative to the anti-cavity screw 21 (7), the exit valve 24
opens and the large mouth valve 23 closes.

In this way, in the hydraulic pressure supply source hydraulic control stage 3, the anti-cavity 1, 2, and
and pressure screws 1 and 17 alternately move relative to each other, and
From this, the output hydraulic pressure chamber 20 generates a hydraulic pressure proportional to the amount of depression of the play 1 - the pedal l. 1, the pressure piston 21 comes into contact with the pressure screw 1. Pushed forward motion Oj
do.

The auxiliary hydraulic pressure generation stage 6 is known as a tandem type mask cylinder, and the hydraulic pressure supply source hydraulic control stage 3
The second housing 40 is integrated with the first housing 15. This second housing 40 is provided with a second cylinder hole 42 which is coaxial with the first cylinder hole 16 with a partition wall 41 in between.
iJ fa is occluded. The second cylinder hole 42 has a first actuating piston 44 on the front side that forms a first hydraulic chamber 43 between the front end wall and a second actuating piston 44 .
The second actuating screw 1/46 forming the hydraulic chamber 45 is fitted with the sliding screw, and the space between the front end wall of the second housing 40 and the first actuating screw 1/44 is fitted. A spring 47 is interposed to bias the first operating piston 44 toward the rear side, and the first operating piston 44 and the second operating piston 46
A spring 48 that biases the second operating screw I 46 toward the moving side is interposed between the two. Further, the second housing 40 includes a first output board [38] connected to the first oil chamber 43, and a second output board [38].
Kawaguchi {chamber 451, this passage (1 and 3 second output ports) will be drilled.

The front end of a piston rod 50 extending rearward is fixed to the second actuating screw 1/46, and this screw 1/1/1 piece 50 is movable in an oil-tight manner on the partition wall 41. ;1
1 through, hydraulic supply source hydraulic control hand H: 3 4S 薯゛9
The front end of the pressure screw [-l7! ．． 1'' The front end of the pressure bottle 17a coaxially protruding is screwed into the screw 1 [J.
．． 'Abutted coaxially. 7 Therefore, the advance of the pressure screw 1 and the pressure screw 7 in the hydraulic control stage 3 of the hydraulic supply source Lt
．． ;Lth;　OJ screw》74G is also pressed forward 6, ゛J'.

The inner surface of the second cylinder hole 42 and the first working piston 44
Between C and 2 is the sleeve refueling room! A connection boat 52 is provided in the second housing 40 to connect the replenishment oil chamber 51 to the reservoir R. Or 2, or the first operating screw 1
・A cup seal 53 that contacts the inner surface M of the second cylinder hole 42 is fitted in the second cylinder hole 446, and the power pusher seal 53 and the first operating piston 44 are closer When the first oil pressure chamber 43 is depressurized, it is configured to allow the flow of oil from the supply oil chamber 5J to the first oil JT chamber 43. Furthermore, the partition wall 4l and the second {J + movement 1・n4
; 1,,': (A side oil supply chamber 54 is defined, and a second
The housing 40 has a fitting that allows the sleeve oil supply chamber 54 to communicate with the reservoir R. Bau l-55 will be established. Also, the second operating screw 1 46C: is the 2nd =: cylinder hole 42
The force of sliding contact with the inner surface of the bushing seal 5 [5] is fitted, and this force is caused by the force between the bushing seal 56 and the second actuating piston 4 (; means the pressure of the second hydraulic chamber 45 is lower than that of the sleeve oil supply chamber 54). The bow 4' is configured to allow flow of hydraulic oil from the sleeve oil supply chamber 54 to the second hydraulic chamber 45.

At the front of the first operating piston L'/44, a valve mechanism 58 that is driven to open and close by a stopper pin 57 fixed to the second housing 40 is connected to the first operating hydraulic chambers 4, 3 and the supply oil chamber 52. When the first actuating screw 1/n 44 returns to the retract limit, this valve mechanism 5B is pressed by the collar pin 5'/ to open the valve 1. Ru. Also, the second operating screw 1.n.1 [j? Part 1. ,t,
A valve mechanism 60 that is driven to open and close by a stop collar pin 59 connects the second hydraulic pressure chamber 45 and the supply oil chamber 54.
, the switch I.../babin 59, which is arranged to block the
The valve mechanism 60 is substantially integrated into the second housing 40, and opens when the second moving piston 1...46 returns to the retracting limit.

With this auxiliary hydraulic pressure generating means 6, C:1, the depression number of the brake pedal 1. The second operating screw I/N 46 is pushed forward by the advance of the pressure screw I/N 17 in response to this;
The volumes of their hydraulic chambers 43. ．． The braking oil pressure generated at i5 is output from the first and second output ports 38 and 39, respectively.

One-way hydraulic transmission means 4F+. ,4■+4RL1
4 RB, from oil pressure supply source 2 to brake gear device B, , B, B, through oil F-U: supply source hydraulic control stage;
! ．． , B■ Is there a one-way oil installed in the middle of the hydraulic path? Transmission means 4 FI. ．． 1 4FT1 is the hydraulic pressure supply source hydraulic control fit "F" between the brake and brake devices BFL, B (7,', and the -force direction hydraulic pressure transmission means 4111-+4in is the proportional pressure reducing valve 5 and the brake device iRB+u ., B■, 4 ports of the two one-way hydraulic pressure transmission means, 4■.41.-,4uM are Q.2 when the hydraulic pressure from the hydraulic pressure supply a2 is normal. Oil g.
---K device B rL, B FN, B +i. −
, B■t is transmitted, but the oil pressure of the 8 oil JiF supply source 2 is abnormally low.
Fl,, B r=+, B II+-, B
Prevents the hydraulic oil from flowing backwards from the RR to the hydraulic pressure supply source 2 side11
, L, the functions to be obtained are -14, and the configuration of the same is basically J1.

-Force direction hydraulic pressure transmission stage f 4FL has input 'E3 X1 and output chamber 64? While facing both ends, the free piston 65 is fitted into the cylinder body 6G, and the spring 6 forces the noli screw 1-65 toward the input chamber 63 side.
7 are housed in the output chamber 64. Moreover, the pressure receiving area S of the free piston 65 facing the input chamber 63 is the output chamber 6
41 is set larger than the pressure receiving area S2.

Such a one-way hydraulic transmission with 1,000 stages 4,... According to the configuration, the hydraulic pressure acting on the input chamber (i3) is increased and the hydraulic pressure applied to the Y-output chamber (
; It is possible to output from 4 and output chamber 64
The hydraulic pressure does not flow to the input chamber 63 side, and the output chamber 64
is connected to the brake device 13F.

i.e. BR1 NOKI IBrt, BFR, BR
I-. The Bml+ includes a cylinder body 68 and a screw 69 slidably fitted into the cylinder body 68, and has a brake defined between the cylinder body 68 and the piston 69. The braking force is generated by the movement of the piston 69 in accordance with the hydraulic pressure acting on the hydraulic chamber 70.
The output chamber 64 communicates with a brake hydraulic pressure chamber 70 8? Wheel brake device BP+-. Force-direction hydraulic pressure transmission means 4p corresponding to BFR (input chamber [53 of 4FR includes inflow valve 7
FL, 7 vn and effluent valve 8 FL+ 8FE
+ are connected in parallel 2, respectively, and one-way hydraulic transmission stage 4 corresponds to rear wheel brake devices B, l, -Bllll+.
R i. ．． The output ports 1 and 72 of the proportional pressure reducing valve 5 are commonly connected to the input chamber 63 of the r 4 R I1, and the input ports 1 and 73 of the proportional pressure reducing valve 5 are connected to the slag, the large valve 7 i1, and the outflow valve 8. connected in parallel.

The inflow valve 7 FLI 7 FPI, 7, is a solenoid valve that shuts off the excitation I4, and the sludge outlet valve 8F+. ,8F■,
8l is a solenoid valve that becomes conductive when excited. The outflow valve 8r+8Fll is connected to the one-way hydraulic transmission means 4Fl. ．． ，
Between input chamber 63 of 4Fll and reservoir R6. ″′
The outflow valve 8,l is the inlet port of the proportional pressure reducing valve 5.
- 7 3 and the reservoir R. Also, inflow valve 7F+. , 7■ are interposed between the input chamber 63 and the oil passage 71 of the one-way hydraulic transmission means 4, I, 4■, and the inflow valve 74 is interposed between the input chamber 1 and 73 of the proportional pressure reducing valve 5 and the oil passage 71. will be established.

The proportional pressure reducing valve 5 has a conventionally well-known structure,
The valve body 74 has the output port 72 and the input port 73, and both ends are connected to an output hydraulic chamber 75 that passes through the output port 72 and an input hydraulic chamber 76 that communicates with the input port 73a. At the same time, a screw Fn 77 is slidably fitted into the valve body 74, and the screw Fn 77 is removed.
According to the movement of the spring 7}3 housed in the manual hydraulic chamber 76 to force the input hydraulic pressure chamber 76 toward the hydraulic chamber 75 side, and the output hydraulic chamber 75 side of the screw I/N 7゛7, the input hydraulic chamber 76 and the output Hydraulic chamber 7
A valve mechanism 79 is provided on the screw 77 for communication between the
Equipped with. Input hydraulic chamber of piston 77゛゛7
The sweat receiving area facing the output hydraulic chamber 6 is set to be 75 mm smaller than the pressure receiving area facing the output hydraulic chamber.

According to the proportional pressure reducing valve 5, after the hydraulic pressure input from the input valve 173 to the input hydraulic chamber 76 exceeds a certain value determined by the spring 7B, the hydraulic pressure of the input cylinder 1.73, that is, the input hydraulic pressure chamber 7G, becomes proportional. The oil passage 71 is reduced in pressure and output from the output bow }72 through a cutoff valve 81.
The output port 27G5'' of the hydraulic control stage 3 is connected to the hydraulic supply source. b) Valve hole 83,' bored in one end wall of the switching valve zero body 82
．． ．． When the valve body 84 capable of closing the valve hole 83 is placed at one end a, the other end faces the pilot chamber 85, and the switching valve body 826 is slidably fitted into the switching screw. [
86, the switching valve body 82 and the switching screw 1 in order to bias the switching piston 1 and the switching screw 1 86 toward the bypass chamber 85 side.
- a spring 87 interposed between the springs 86;

A valve chamber 88 that can communicate with the valve hole 83 is defined between one end wall of the switching valve main body 82 and the switching screw 86, and a spring 87 is housed in the valve chamber 88. The switching valve main body 82 also communicates with a valve chamber 88 and has a hydraulic pressure supply source hydraulic control means 3.
Eight inlet boats communicating with the output boats 27 are drilled.

According to this switching valve 81, when the oil pressure in the pilot chamber 85 is lower than a certain value, the switching piston 86 moves toward the pilot chamber 85 side to a position where the valve body 84 opens the valve hole 83. When the valve is open and the oil pressure in the pilot chamber 85 exceeds the predetermined value, the switching piston 86 moves to the valve body 8.
4 to close the valve hole 83 and close the valve. Therefore, by controlling the oil pressure in the pilot chamber 85, it is possible to switch between communication and disconnection between the output ball 27 of the oil pressure supply source oil pressure control means 3 and the oil passage 71.

The traction control inlet valve 9 is an electromagnetic valve that becomes in communication when excited, and is interposed between the pilot chamber 85 and the hydraulic pressure supply source 2. In addition, the outflow valve 1 for traxilan control
Reference numeral 0 denotes a solenoid valve that is cut off during excitation, and is interposed between the pilot chamber 1, the chamber 85, and the reservoir R. Therefore, when 1. traction control inflow valve 9 and 1. traction control outflow valve 10 are demagnetized, switching valve 8
1 is open because the oil pressure in the pilot chamber 85 is low, and when the inlet valve 9 for controlling the traction valve 9 and the outlet valve 10 for controlling the traction valve 10 are energized, the switching valve 81 is opened.
The valve is closed in response to the high oil pressure from the oil pressure supply source 2 acting on the chamber 85.

The Traxigin control inflow valve 9 and Traxigin control outflow valve 10 are connected to the oil passage 71 via a one-way valve 90 that bypasses the switching valve 81. The one-way valve 9
0 allows the hydraulic oil to flow toward the oil path 71 side, and the traction control inflow valve 9 and the traction control comb ? When the valve 10 is in the energized state, the hydraulic pressure supply source 2 communicates with the oil passage 71 .

The first output boat 38 of the auxiliary hydraulic pressure generating means 6 is connected to the on-off valve 9
1. The right front wheel brake device B■ and the left rear wheel brake device B■. The second output boat 39 is connected to a left front wheel brake device BFI and a right rear wheel brake device B■ via an on-off valve 91■. Both on-off valves 91,,91. have the same configuration, and only the configuration of one of the on-off valves 91 will be described below.

Open/close valve 91. This includes a cylindrical on-off valve zero body 92 with both ends closed, a pair of valve holes 93 bored in one end wall of the on-off valve main body 92, and a valve body 94 capable of closing the valve holes 93. An opening/closing piston 96 is provided at one end and is slidably fitted into the opening/closing valve main body 92 with the other end facing the pilot chamber 95.
5 side, the on-off valve zero body 92 and the on-off screw l.
and a spring 97 interposed between the springs 96 and 96.

A valve chamber 98 that can communicate with the valve hole 93 is defined between one end wall of the on-off valve main body 92 and the on-off piston 96.
A spring 97 is housed in 8. Further, an inlet port 99 is bored in the on-off valve zero body 92 and communicates with the valve chamber 98 and the first output ports 1 and 38.

According to this opening/closing valve 91, when the oil pressure in the pilot chamber 95 is lower than a certain value, the opening/closing piston 96 moves toward the pilot chamber 95 to the position where the valve body 94 opens the valve hole 93, thereby opening the valve. As soon as the oil pressure in the pilot chamber 95 exceeds the predetermined value, the opening/closing screw 96 moves to close the valve hole 93 with the valve rest 94, thereby closing the valve.

Moreover, one valve hole 93 is connected to the output chamber 64 of the one-way hydraulic transmission means 4■, and the other valve hole 93 is connected to the one-way hydraulic transmission means 4■. Pressure transmission means 4
It communicates with the output chamber 64 (2), and both valve holes 93 communicate with the brake oil LF chamber 70 of the brake device BFII+BIIL. Also, the birosoto chamber 95 is the oil passage 7I.
It will be communicated to. Therefore, when the oil pressure in the oil passage 7l, that is, in the pilot chamber 95, is high, the on-off valve 91 is closed and the first
When the output balls 1 and 3B and the brake devices B, B, and LL are cut off and the oil pressure in the oil passage 71 becomes low, the on-off valve 91.
When the valve is opened, communication is established between the lth output BO[.38, play 1', device 3, and BIIL.

In addition, the on-off valve 91■ closes when the oil pressure in the oil passage 71 is high, thereby blocking the connection between the first output balls 1 and 38 and the brake device Y3FL+BIll, and when the oil pressure in the oil passage 71 becomes low, the on-off valve closes. 91. When the valve was opened, the first output boat and the brake system H B F+. ．． ．． Communication is established between B and ■.

The first output boat 38 of the auxiliary hydraulic pressure generating means 6 and the on-off valve! ] l, input 7 to } 9 9, the second output bow 1-39 of the auxiliary hydraulic pressure generation stage 6, the input cylinder 1 and 99 of the on-off valve 91, and the hydraulic pressure supply source hydraulic control stage f 3 Between the output port 27 and the switching valve 810 input [Kobo } 89, a hollow 21 blade h +/- 101 is connected.

This Akiem Lake 101 includes an Aiemu Lator Honkyu 102 which is basically formed into a cylindrical shape with both ends closed, and a first
A first pressure accumulator chamber 103 that communicates with the output boats 1 and 38, a second N pressure chamber 104 that communicates with the three second output boats, and a back pressure chamber 105 that communicates with the output boats 1 and 27 are defined between the accumulator main body 102 and While forming the accumulator body 10
Aki 1 muller vis l/n 1 slidably fitted to 2
06, and the accumulator main body 102 in order to energize the accumulator 106 in the direction of contracting the volumes of the first and second pressure accumulating chambers 103, 104 and increasing the volume of the back pressure chamber 105. and accumulator services 1 to 106
and a reaction spring l07 interposed between the two.

Inside the accumulator main body 1.02, a first sliding hole 108, a second sliding hole 109, and a third sliding hole 110 are coaxially connected to each other in order from one axial end to the other end. The inner diameter of each sliding hole 10B=110 is the second
The inner diameter of the sliding hole 109>the inner diameter of the first sliding hole 108>the inner diameter of the second sliding hole 110. On the other hand, the first sliding hole 106 is
A medium diameter portion 106a is slidably fitted into the second sliding hole 109, a large diameter portion 106b is slidably fitted into the third sliding hole 110. small diameter portion 106C
and are connected coaxially and in this order. Thus, the IM pressure chamber 103 is defined between the end wall of the first sliding hole l08 and the end surface of the medium diameter portion 106a, and the second pressure accumulation chamber 104
The back pressure chamber 105 is defined in an annular shape between the step between the first and second sliding holes 108 and 109 and the step between the medium diameter section 106a and the large diameter section 106b. It is defined between the end wall and the end surface of the small diameter section 106C. Also the second
A spring chamber 111, which is open to the atmosphere, is defined between the stepped portion between the third sliding holes 109 and 110, and between the large diameter portion 106b and the small diameter portion 106c, and a spring chamber 111 is defined between the large diameter portion 106b and the small diameter portion 106c. is housed in the spring chamber 111. Moreover, the reaction spring 107 is set so that its spring constant increases as the load increases.

Next, the operation of this embodiment will be explained. First, assuming a normal braking operation with the hydraulic pressure supply source 2 operating normally, the inflow valves 7FL+ 7Fl1-7,l and the outflow valves 8FL+ 8FN, 8n are in a demagnetized state (the state shown in the figure). There is also 1. Inflow valve 9 for luxigon control and I. Outflow valve 10 for traction control? There are several magnetic states (states shown). 1. Therefore, the switching valve 81 is controlled by the valve L7, and the output bow 1/27 of the hydraulic pressure control stage 3 of the hydraulic supply source communicates with the oil 1 heat 71. One-way hydraulic transmission means 4
FL+ 4Fl+ input chamber 636 connected state ζ
As well as the inflow valve 7. and through the proportional filtration valve 5 L2
One-way hydraulic transmission with 1,000 steps 4 ■. It is in state B connected to the input chamber 63 of 4R,l.

When the brake pedal 1 is depressed in such a state, the hydraulic pressure from the hydraulic pressure supply source 2 is controlled by the hydraulic pressure supply source hydraulic control means 37 according to the amount of pedal operation, and the controlled hydraulic pressure is output from the output ball l-27. It is Accumu 1/Ichiya 101
It acts on the back pressure chamber 105 as well as on the oil passage 71. 1. Therefore, the oil pressure from the output boat 27 is increased in the direction oil river transmission stage 4■,,4■. At the same time, the hydraulic pressure reduced by the proportional pressure reducing valve 57 is further transferred to the - direction hydraulic pressure transmission Ef stage 4,,I. , 4RI1 and applied to the fan 1 cylinders WB, It, B-.

? Each block 1/- key device BFI-, BF=
, B■. + 4 ports of unidirectional hydraulic transmission means corresponding to B111. 4F3,4■. 41111 acts, and even if the output oil pressure of the oil pressure supply source 2 is set relatively low, each brake device BFI, ~B■ is sufficient. It becomes possible to obtain. Therefore, the load on the oil field supply source 2 is reduced, and it is possible to downsize the oil field supply source 2, that is, to downsize the hydraulic bomb 11 and the gear 1 muller 12. Also, one-way hydraulic transmission means 4 F L + 4 F II + 4 II
At L * 4 * 11, each block 1,/- key device B F L * B F I
Since the hydraulic circuit from the input chamber 63 to the hydraulic pressure supply source 2 is isolated from I r 13R +- *B Equipment BFL+ BFl1+ BIILr B
■Words that have a negative impact on? .

During this braking, the braking force of the left and right rear wheels must be lower than that of the left and right front wheels, and each time the hydraulic pressure from the hydraulic pressure supply source hydraulic control stage 3 is reduced by the proportional pressure reducing valve 5, the braking force of the left and right rear wheels is controlled. The power is lower at a fixed ratio than the left and right front wheels.

By the way, in response to the depression operation of brake pedal 1, the first
When the second operating screws 1-44 and 46 are driven, braking oil pressure is also output from the first and second output ports 38 and 39 of the auxiliary oil pressure generation stage 6. However, the oil pressure in the oil passage 7l is Due to the height, the on-off valve 91. ，
91 ■ is closed, and 7 1st and 2nd output boats 3
The volumes of the first and second N pressure chambers 103 and 104 of the hydraulic pressure accumulator 101 from 8.39 are increased, thereby ensuring the stroke of the brake pedal 1. Moreover, the first and second output boats 3
Compared to 8.39, only one muller 101 is required, which contributes to a reduction in the number of parts.

In addition, the reaction force spring 107 of the accumulator 101 is set so that the spring constant increases as the load increases. This can improve the braking operation feeling. Moreover, since the hydraulic pressure controlled by the hydraulic pressure supply source hydraulic control 3 is introduced into the back pressure chamber 105, the reaction force spring 107 can be made smaller and the Akiemulator 101 can be made smaller. compared to directly introducing the back pressure chamber 105 into the back pressure chamber 105.
The initial braking operation of the brake pedal 1 can be made smooth by increasing the oil pressure according to the braking operation.

During such braking, what is the pressing force of brake pedal 1? When the wheel becomes too large and the wheels are about to lock, the inflow valves 7FL, 7 corresponding to the wheels that are about to lock are
■． 75 is excited to cut off the oil passage 71 and the one-way hydraulic transmission means 4 FL'' and 4■.

This suppresses an increase in braking force to prevent the wheels from becoming locked. If the wheels are still likely to lock, open the corresponding outflow valve 8 FL+
The tendency of the wheels to lock can be eliminated by energizing 8Fll+8Il to connect the input chambers 63 of the one-way hydraulic transmission means 4■ to 4o to the reservoir R and lowering the restraining pressure. Assume that during the above braking, high oil pressure cannot be obtained from the oil pressure supply source 2 due to a failure of the hydraulic pump 11 or the like. In this case, the on-off valves 91+ and 91g open in response to a decrease in the oil pressure in the oil passage 7l connected to the oil pressure supply source oil pressure control stage 3. Therefore, the braking hydraulic pressure generated in the auxiliary hydraulic pressure generation stage 6 acts directly on each brake brake device BFL-B, thereby making it possible to secure braking force. At this time, the one-way hydraulic transmission means 41 to 411I1 are connected to each brake device B.
Since it is interposed between FL~B, lM and the hydraulic pressure supply source hydraulic control means 3, each brake equipment i1F B y t~
The braking pressures B and 1R do not escape to the hydraulic pressure supply source hydraulic pressure control means 3 side.

Moreover, braking oil pressure acts on the left and right rear wheels via the proportional pressure reducing valve 5 during normal braking, whereas the oil pressure supply source 2 acts on the left and right rear wheels.
In the event of a malfunction, the braking hydraulic pressure from the auxiliary hydraulic pressure generating stage 6 acts directly, so that sufficient braking force can be ensured.

Next, a hydraulic circuit connects the first outputs 1 and 3B of the auxiliary hydraulic pressure generating means 6 to the right front wheel brake system YtBF and the left rear wheel brake system BIL, and the second output of the auxiliary hydraulic pressure generating means 6. Ball L.39 and left front wheel brake device B
FI and right rear wheel brake system ffBts+? It is assumed that braking is performed when a hydraulic pressure failure has occurred in one of the connected hydraulic circuits and the hydraulic pressure supply source 2 is malfunctioning. In this case, the hydraulic pressure generated by the auxiliary hydraulic pressure generating means 6 causes the brake system [B
FL) B It is possible to secure the braking force on one side of the IR, and at that time, the movement of the countercapiston 106 in the accumulator 101 is made smaller than when both of the hydraulic circuits are normal, and the brake pedal stroke is reduced by 10. can be suppressed from increasing. When braking is performed after the braking operation is completed, the on-off valves 91+ and 91g are opened due to a decrease in the oil pressure in the oil passage 71, and the output chambers 64 in each one-way hydraulic pressure transmission means 4FL to 4o are transferred to the reservoir R via the auxiliary oil pressure generation means 6. can be communicated with. As a result, in response to the movement of the free screw l/n 65 toward the input chamber 63 in the one-way hydraulic transmission means 4rt-4, a negative force is applied to the output chamber 64. This eliminates the need to provide a special reservoir for this purpose.

Furthermore, when the engine is not braking, when the driving force of the engine becomes excessive and the drive wheels are about to slip excessively, the inflow valve 9 for the traction control and the outflow valve 10 for the traction control are energized, and the left and right driven wheels are excited. The inflow valve 7 corresponding to the rear wheel is energized.

As a result, the switching valve 81 closes, and the high hydraulic pressure from the hydraulic pressure supply source 2 acts on the input chamber 63 of the one-way hydraulic transmission means 4 FLI 4 v*, and the brake systems IBFL and BFII of the left and right front wheels, which are the driving wheels, act on the input chamber 63 of the one-way hydraulic transmission means 4 FLI 4 v *. Braking force is generated and excessive slip is avoided. After this, the inflow valve 1vI. + 7rll and outflow valve 8F1. With 8■ excitation and demagnetization control,
Braking force can be controlled.

In the above embodiment, the free piston 65 is slidably fitted into the cylinder body 66 to form a one-way oil pump. Transmission means 4F
．． , 4 ■. 4-t, 4- as hydraulic supply source hydraulic control means 3 and each brake device BFL+ BFII+B IL+
However, as another embodiment of the present invention,
A check valve that only allows flow of hydraulic oil from the hydraulic pressure supply R2 side is used as a one-way hydraulic pressure transmission means, and the hydraulic pressure supply source hydraulic control means 3 and each brake equipment IBFLI BFRI Bil
+. , BUR, or between the hydraulic pressure supply source 2 and the hydraulic pressure supply source hydraulic control means 3, and may be closed due to a decrease in the output hydraulic pressure of the hydraulic pressure supply source 2 or the output hydraulic pressure of the hydraulic supply source hydraulic control stage 3. The opening/closing valve may be interposed between the hydraulic pressure supply source hydraulic control means 3 and each brake unit BFLB* Bi+L, Baa with a one-way hydraulic transmission stage, and furthermore, the hydraulic pressure supply source hydraulic control f When the output oil pressure of stage 3 is high, the hydraulic pressure supply source hydraulic pressure control stage 3 and each brake device B■. B■. When the output oil pressure of the hydraulic supply source hydraulic control 1,000-stage 3 is low, the state in which B■, , B, and 1a are connected, and the hydraulic pressure supply source hydraulic control 1,000-stage ζ} and each brake l/single-key device B FL, B FR. B RLI B
It is also possible to use a switching valve that is configured to be able to switch between a state in which B is cut off and a state in which B is cut off to function as an on-off valve and a one-way hydraulic transmission means in the claims.

C. Effects of the Invention As described above, in the device of the present invention, an operating piston interlocked and connected to a brake pedal is slidably fitted into a housing so as to move forward in response to a braking operation, and auxiliary hydraulic pressure generating means in which a hydraulic chamber is formed in the housing by rounding the front end surface of the actuating piston in order to contract the volume; a hydraulic pressure supply source interposed between the hydraulic chamber of the auxiliary hydraulic pressure generating means and the brake device; An on-off valve that opens in response to a decrease in the output oil pressure of the oil pressure control means; is provided in the middle of the hydraulic path from the oil pressure supply source to the brake device via the oil pressure supply source oil pressure control means to supply oil pressure when the oil pressure from the oil pressure source is normal. The source oil pressure control means output oil pressure is configured to enable oil pressure transmission to the brake system, and also to disable the flow of hydraulic oil from the brake device to the oil pressure supply source side-4 when the oil pressure supply source oil pressure drops abnormally. and a one-way hydraulic transmission means;
When the hydraulic pressure supply source is malfunctioning, the on-off valve is opened, the hydraulic pressure of the brake device is prevented from escaping to the hydraulic pressure supply source side by the one-way hydraulic pressure transmission means, and the hydraulic pressure from the auxiliary hydraulic pressure generating means is applied to the brake device. Sufficient braking force can be obtained.

[Brief explanation of drawings]

The drawing is a hydraulic circuit diagram showing an embodiment of the present invention. ? ···break pedal, pressure supply pond pressure control means; ...One-way hydraulic transmission means, 91.9■...Opening/closing valve, 4 ? ...Hydraulic supply source, 3...Oil 4FL, 4■,4■,,4■ 6... Auxiliary hydraulic pressure generating means, 0...Housing, 43,

Claims (1)

[Claims] In a brake hydraulic control device in which a hydraulic pressure supply source hydraulic control means is interposed between a hydraulic pressure supply source and a brake device and is capable of controlling hydraulic pressure from the hydraulic supply source according to a braking operation amount, An actuating piston that is interlocked and connected to the brake pedal is slidably fitted into the housing, and a hydraulic chamber is formed within the housing with the front end of the actuating piston facing in order to contract its volume in response to the forward movement of the actuating piston. auxiliary hydraulic pressure generating means; an on-off valve that is interposed between the hydraulic chamber of the auxiliary hydraulic pressure generating means and the brake device and opens in response to a decrease in the output hydraulic pressure of the hydraulic pressure supply source hydraulic control means; It is provided in the middle of the hydraulic path leading to the brake device via the source hydraulic pressure control means, and enables the hydraulic pressure transmission of the output hydraulic pressure of the hydraulic source hydraulic pressure control means to the brake device when the hydraulic source hydraulic pressure is normal, and also controls the hydraulic pressure source hydraulic pressure. A braking hydraulic pressure control device comprising: one-way hydraulic pressure transmission means configured to disable flow of hydraulic fluid from a brake device to a hydraulic pressure supply source when abnormally low.