JPH0415567Y2 - - Google Patents

Description

[Detailed explanation of the invention] A. Purpose of the invention (1) Industrial application field The invention generates braking oil pressure according to the output oil pressure from the first output port of a tandem master cylinder having a pair of output ports. a brake hydraulic modulator for the right front wheel and a brake hydraulic modulator for the left rear wheel, configured to generate brake hydraulic pressure for the right front wheel and a brake hydraulic pressure modulator for the left rear wheel, and a brake for the left front wheel configured to generate braking hydraulic pressure according to the output hydraulic pressure from the second output port of the master cylinder. A hydraulic modulator and a brake hydraulic modulator for the right rear wheel, and a control fluid for the brake hydraulic modulator for the left and right front wheels and the brake hydraulic modulator for the left and right rear wheels to reduce the braking hydraulic pressure when the wheels are about to lock up. The present invention relates to a so-called two-system X-piping type vehicle brake hydraulic control system including an antilock control valve means for controlling supply and release of pressure.

(2) Prior Art Conventionally, in this type of vehicle brake hydraulic control device, the oil passages that lead the output hydraulic pressure from the first and second output ports of the master cylinder to each brake hydraulic modulator are complicated. Ori,
For example, as disclosed in Japanese Unexamined Patent Publication No. 58-194648, the oil passage from the first output port to the front right wheel brake hydraulic modulator and the rear left wheel brake hydraulic modulator is bifurcated in the middle. It was configured to be connected to both modulators, respectively, and the two modulators were respectively disposed in separate casings.

(3) Problems to be solved by the invention The present invention was proposed in view of the above circumstances, and it is designed to rationally arrange each brake oil pressure modulator and simplify the oil path that leads the output oil pressure of the master cylinder to each modulator as much as possible. It is an object of the present invention to provide a brake hydraulic control device for a vehicle, which is also as easy to process as possible.

B. Structure of the invention (1) Means for solving the problem In order to achieve the above object, according to the present invention, in the vehicle brake hydraulic control device of the above type,
The brake hydraulic modulator for the right front wheel and the brake hydraulic pressure modulator for the left rear wheel have a first communication path that communicates between the input hydraulic chambers of both modulators, and a first communication path that communicates the input hydraulic chambers of one of the modulators with the input hydraulic chamber of the first modulator. The front left wheel brake hydraulic modulator and the right rear wheel brake hydraulic modulator are arranged in parallel in a common casing in which a first inlet oil passage communicating with the oil passage connected to the port is bored on the same axis, and the brake hydraulic modulator for the left front wheel and the brake hydraulic pressure modulator for the right rear wheel are a second communication path that communicates between the input hydraulic chambers of both modulators;
The input hydraulic chamber of one of the modulators is connected to the second
and a second inlet oil passage that communicates with the oil passage connected to the output port of the first inlet oil passage are arranged in parallel in a common casing that is bored on the same axis as the second inlet oil passage.

(2) Function A common inlet oil passage for guiding the output hydraulic pressure from each output port of the tandem master cylinder to a corresponding pair of hydraulic modulators, and a communication passage between the pair of hydraulic modulators, Since the modulators can be drilled on the same axis in a common casing in which they are arranged side by side, the efficiency of these machining operations can be improved. Moreover, since the above-mentioned inlet oil passage, communication passage, and the hydraulic modulator itself between them function as a branch joint that distributes the output oil pressure from each output port to a corresponding pair of hydraulic modulators, the oil passage from each output port to the casing is There is no need for special branch piping in the middle of the pipe.

(3) Embodiment An embodiment of the present invention will be described below with reference to the drawings. First, in FIG. 1, oil passages 2a and 2b are connected to a pair of output ports 1a and 1b of a tandem master cylinder _M The output oil pressure from one output port 1a is supplied to the right front wheel brake oil pressure modulator M _fr and the left rear wheel brake oil pressure modulator M rl via the oil passage 2a, and the output oil pressure from the other output port 1b is supplied to the oil pressure modulator M fr and the left rear wheel brake oil pressure modulator M _rl . It is supplied to the left front wheel brake hydraulic modulator M _fl and the right rear wheel brake hydraulic modulator M _rr via path 2b. The brake hydraulic modulators for the left and right front wheels M _fl , M _fr adjust the brake hydraulic pressure corresponding to the output hydraulic pressure of the master cylinder M _c to the brakes for the left and right front wheels B _fl , B _fr
The brake hydraulic modulators M _rl and M _rr for the left and right rear wheels apply braking hydraulic pressure proportionally reduced from the output hydraulic pressure of the master cylinder M _c to the brakes for the left and right rear wheels B _rl and B _rr . act to give.

In addition, in order to reduce the braking hydraulic pressure when each wheel is about to lock up, a control hydraulic pressure source 5, a reservoir R, brake hydraulic modulators _Mfl , _Mfr for the left and right front wheels, and a brake hydraulic pressure modulator for the left and right rear wheels are also provided. Anti-lock control valve means 6a, 6b are interposed between the brake hydraulic modulators M _rl and M _rr . i.e. brake hydraulic modulator for left and right front wheels
The antilock operation of M _fl and M _fr is controlled by the operation of one antilock control valve means 6a,
Brake hydraulic modulator for left and right rear wheels M _rl ,
The antilock operation of M _rr is controlled by the operation of the other antilock control valve means 6b.

In FIGS. 2 to 4, the brake hydraulic modulators M _fl , M _fr , M _rl , and M _rr are provided in a common casing 7 . Furthermore, the brake hydraulic modulators M _fl , M _fr for the left and right front wheels and the brake hydraulic modulators M _rl , M _rr for the left and right rear wheels are arranged parallel to each other. In addition, there are brake hydraulic modulators in the same hydraulic system, that is, a brake hydraulic modulator for the right front wheel M _fr and a brake hydraulic modulator for the left rear wheel M _rl to which hydraulic pressure is supplied from one output port 1a of the master cylinder M _c ,
The brake hydraulic modulator for the left front wheel M _fl and the brake hydraulic modulator M _rr for the right rear wheel, to which hydraulic pressure is supplied from the other output port 1b of the master cylinder M _c , are arranged so that they are adjacent to each other on a parallel straight line. M _fl , M _fr , M _rl ,
M _rr is arranged. Furthermore, one anti-lock control valve means 6a is disposed on the extension of a straight line connecting the brake hydraulic modulators M _fl and M _fr for the left and right front wheels, and the brake hydraulic modulators for the left and right rear wheels
The other anti-lock control valve means 6b is disposed on the extension of a straight line connecting M _rl and M _rr , and both anti-lock control valve means 6 a, 6 b are integrally supported by a mounting portion 85 provided on the side of the casing 7. and their anti-lock control valve means 6a, 6b.
A reservoir R is disposed on top of the reservoir R.

Each brake hydraulic modulator M _fl , M _fr , M _rl ,
M _rr extends vertically and is arranged parallel to each other, and is a brake hydraulic modulator for the left and right front wheels.
The configurations of M _fl and M _fr are basically the same, and the configurations of the brake hydraulic modulators M _rl and M _rr for the left and right rear wheels are the same as the brake hydraulic modulators M _fl and M for the left and right front wheels, except for a part. It is basically the same as _fr .
Therefore, the structure of the brake hydraulic modulator M _fl for the left front wheel will be described in detail below, and the brake hydraulic modulator M _rr for the right rear wheel will be described as follows: brake hydraulic modulator M _fl for the left and right front wheels,
Only the parts that are different from M _fr will be explained, and the main parts corresponding to the front left wheel brake hydraulic modulator M _fl will be illustrated with the same reference numerals.

In FIG. 5, the left front wheel brake hydraulic modulator M _fl is constructed by assembling components from above into a bottomed cylinder hole 8 that is bored in the casing 7 and has an open upper end. That is, cylinder hole 8
A disk-shaped partition wall 9 and a cylindrical sleeve 10 are fitted inside. The partition wall 9 is fitted into the cylinder hole 8 with an O-ring 11 interposed between it and the inner surface of the cylinder hole 8, and the sleeve 10 is inserted into the cylinder hole 8 with an O-ring 13 interposed between it and the inner surface of the cylinder hole 8. 8 will be inserted. A stepped portion 12 facing upward is provided in the middle of the cylinder hole 8. Further, a lid member 14 is attached to the casing 7 corresponding to the open end of the cylinder hole 8, and the partition wall 9 and the sleeve 10 are clamped and fixed between the lid member 14 and the step portion 12. Note that the sleeve 10 may be integrated with the partition wall 9.

By fixing the partition wall 9 and the sleeve 10 in the cylinder hole 8, the partition wall 9 is formed in the casing 7.
A first cylinder portion 15 located below the partition wall 9 and a second cylinder portion 16 located above the partition wall 9 are formed concentrically.

A first piston 17 is slidably connected to the first cylinder portion 15 , an input hydraulic pressure chamber 18 is defined between the first piston 17 and the partition wall 9 , and a control chamber 19 is defined between the bottom of the casing 7 and the first piston 17 . defined.

An annular oil passage 28 is defined between the lower outer surface of the partition wall 9 and the inner surface of the cylinder hole 8, and an oil passage 20 is bored in the partition wall 9 to communicate between the input hydraulic chamber 18 and the annular oil passage 28. will be established. Further, the casing 7 is provided with an inlet oil passage 21 that opens at the side surface 7a on the left front wheel brake hydraulic modulator M _fl side and communicates with the annular oil passage 28 . Furthermore, the annular oil passage 2 is also connected to the brake hydraulic modulator M _rr for the right rear wheel.
8 is provided, and the annular oil passage 28 and the annular oil passage 2 of the brake hydraulic modulator M _fl for the left front wheel are provided.
8 through a communication passage 29, and this communication passage 29 is bored in the casing 7 on the axial extension of the inlet oil passage 21. Therefore, casing 7
At the time of machining, the inlet oil passage 21 and the communication passage 29 are bored at the same time. Moreover, the open end of the inlet oil passage 21 is connected to an oil passage 2b that continues to the output port 1b of the master cylinder M _c . Therefore, the output hydraulic pressure from the output port 1b is supplied to the input hydraulic chambers of both brake hydraulic modulators M _fl and M _rr .

A second piston 22 having the same diameter as the first piston 17 is slid into the second cylinder portion 16 , an output hydraulic chamber 23 is defined between the second piston 22 and the partition wall 9 , and the second piston 22 and the lid member 14 are provided with an output hydraulic pressure chamber 23 . A spring chamber 24 is defined therebetween. An oil passage 25 is bored in the sleeve 10 so as to constantly communicate with the output hydraulic pressure chamber 23, and an oil passage 25 is bored in the side wall of the casing 7 to connect it to an oil passage 3b (see Fig. 1) leading to the left front wheel brake B _fl . The drilled outlet oil passage 26 is similar to the oil passage 25.
is bored in the output hydraulic chamber 23 via the outlet oil passage 2.
6 is opened in the side surface 7a of the casing 7 on the same side as the inlet oil passage 21.

The lid member 14 is basically formed into a cylindrical shape with a bottom, and its open end is screwed into the open end of the cylinder hole 8 and abuts against the sleeve 10. Moreover, the lid member 1
A hole 27 is bored at the closed end of 4.

A through hole 31 is bored in the center of the partition wall 9 between the input hydraulic chamber 18 and the output hydraulic chamber 23, and a piston rod 33 is inserted into the through hole 31 with an O-ring 32 interposed between the two. It is inserted so that it can move freely in the axial direction. The first piston 17 is integrally provided at the bottom of the piston rod 33, and the second piston 22 is sealed at the top of the piston rod 33 to allow relative axial movement within a limited range. It is attached with the member 34 interposed between the two. Further, a step portion 35 facing upward is integrally provided at the upper part of the piston rod 33, and a receiving member 36 that comes into contact with this step portion 35 is attached to the piston rod 33 by a nut 37.
is fixed to the top edge of the

The second piston 22 is integrally provided with a cylindrical portion 38 extending toward the partition wall 9, and this cylindrical portion 38
Corresponding to this, the piston rod 33 has an output hydraulic chamber 23.
A locking hole 39 is bored along one diameter line, and is in continuous communication with the. In addition, the locking hole 39 has a cross-sectional shape of an elongated oval along the axial direction of the piston rod 33, and is connected to the rod 4 fixed at one or both ends to the cylindrical portion 38 of the second piston 22.
0 is inserted into the locking hole 39. Therefore, the second piston 22 is allowed to move relative to the piston rod 33 within the range in which the rod 40 can move along the axial direction of the piston rod 33 within the locking hole 39.

A flange portion 42 is provided on the piston rod 33 on the side closer to the partition wall 9 than the first piston 17 , and this flange portion 42 contacts the partition wall 9 to restrict upward movement of the piston rod 33 . Also, the first piston 17
A sealing member 43 is fitted between the flange 42 and a blind lid 44 attached to the lower end of the piston rod 33.
A seal member 45 is provided between the first piston 17 and the first piston 17.
are fitted, and both seal members 43 and 45 come into sliding contact with the inner surface of the first cylinder portion 15. Furthermore, the second piston 22 has an annular fitting groove 4 in a portion near the partition wall 9.
6 is provided, and a seal member 47 that comes into sliding contact with the inner surface of the second cylinder portion 16 is fitted into this fitting groove 46 .

The receiving member 36, that is, the piston rod 33 and the lid member 1
A first spring 48 is interposed between the first piston 17 and the first piston 4 , and the spring force of the first spring 48 biases the piston rod 33 downward, that is, in a direction in which the first piston 17 moves away from the partition wall 9 . Also, between the receiving member 36, that is, the piston rod 33, and the second piston 22, the first spring 4 is provided for exerting a spring force to relatively move the second piston 22 toward the partition wall 9.
A second spring 52 having a smaller set load than spring 8 is interposed.

The partition wall 9 is provided with a first valve mechanism 53 that communicates and blocks communication between the input hydraulic chamber 18 and the output hydraulic chamber 23. The first valve mechanism 53 has a valve chamber 54 which is connected to the input hydraulic pressure chamber 18 and is provided in the partition wall 9.
a valve hole 55 provided across the output hydraulic chamber 23; a spherical valve body 56 housed within the valve chamber 54 to open and close the valve hole 55; A drive rod 57 facing into the output hydraulic chamber 23 and a spring 58 biasing a valve body 56 housed in the valve chamber 54 toward the valve hole 55 are provided. A conical valve seat 59 whose diameter becomes smaller toward the valve hole 55 side is provided on the end surface of the valve chamber 54 on the valve hole 55 side. Further, the length of the drive rod 57 is the same as that of the second piston 2.
2 is displaced to the maximum extent toward the partition wall 9, the second piston 22 is pressed by the pressing portion 60 provided at the tip of the cylindrical portion 38, and the valve body 56 is pushed against the valve seat 59.
The value is set to a value sufficient to move the target away from the target.

Further, a second valve mechanism 61 is provided within the piston rod 33. This second valve mechanism 61 includes a valve chamber 62 that is always in communication with the input hydraulic pressure chamber 18, and a piston rod 33.
A cylindrical valve seat member 64 having a valve hole 63 concentric with
, a passage 65 concentrically connected to the valve hole 63 and communicating between the valve hole 63 and the locking hole 39 , and a spherical valve body 66 accommodated in the valve chamber 62 to open and close the valve hole 63 .
and a spring 67 that urges the valve body 66 toward the valve hole 63.
and a drive rod 68 inserted through the passage 65 and the valve hole 66 to press the valve body 66 and open the valve hole 63.

The valve chamber 62 is formed by fitting the valve seat member 64 into a bottomed hole concentrically formed in the lower end of the piston rod 33 and closing the open end of the bottomed hole with the blind cover 44. and a blind lid 44. The seal between the valve chamber 62 and the passage 65 is achieved by press-fitting and fixing the valve seat member 64 into the bottomed hole. It is also possible to intervene. A valve body receiver 69 that receives the valve body 66 is housed in the valve chamber 62 so as to be movable in the axial direction of the piston rod 33 , and the spring 67 supports the blind lid 44 and the valve body receiver 69 .
It is interposed between. Further, a communication hole 70 that communicates between the valve chamber 62 and the input hydraulic pressure chamber 18 is bored in the piston rod 33 .

The length of the drive rod 68 is the same as that of the valve body 66 in the closed state.
When one end is in contact with the locking hole 39, the other end projects into the locking hole 39 by a certain length. Therefore, the second piston 22 is connected to the receiving member 3.
When the valve element 66 of the second valve mechanism 61 moves away from the valve seat member 64 and opens relative to the piston rod 33 over a certain distance in a direction away from the valve seat member 64 and closer to the partition wall 9.

Regarding the brake hydraulic modulator M _rr for the right rear wheel, the pressure receiving area or outer diameter of the first piston 17' is determined to be smaller than the pressure receiving area or outer diameter of the second piston 22, and the first cylinder The inner diameter of the portion 15' becomes smaller. Moreover, the set load of the first spring 48' is set larger than that of the first spring 48 of the brake hydraulic modulator M _fl for the left front wheel, and the first spring 48' is larger than the first spring 48. Lid member 1 accordingly
4' is also enlarged.

The other structure of the brake hydraulic modulator M _rr for the right rear wheel is basically the same as that of the brake hydraulic modulator M _fl for the left front wheel.
6' is opened in the side surface 7a of the casing 7 adjacent to the outlet oil passage 26 of the front left wheel brake hydraulic modulator _Mfl , and this outlet oil passage 26' has an oil passage 4b (leading to the right rear wheel brake _Brr) . (see Figure 1) are connected.

The brake hydraulic modulator M _fr for the right front wheel and the brake hydraulic modulator M _rl for the left rear wheel are also configured in the same manner as described above, with an inlet oil passage 71 communicating with the annular oil passage 28 of the brake hydraulic modulator M _fr for the right front wheel. The outlet oil passages 72 and 72', which communicate with the output oil pressure chambers 23 of both brake hydraulic modulators M _fr and M _rl , respectively, refer to the inlet oil passage 21.
The outlet oil passages 26 and 26' are opened at the side surface 7a of the casing 7. An oil passage 2a is connected to the inlet oil passage 71, and oil passages 3a and 4a are connected to the outlet oil passages 72 and 72', respectively.

The lower part of the casing 7 includes a supply oil passage 73a communicating with the control chamber 19 of the brake hydraulic modulators M _fl and M _fr for the left and right front wheels, and a control chamber for the brake hydraulic modulators M _rl and M _rr for the left and right rear wheels. A supply oil passage 73b communicating with 19 is bored in a straight line and in parallel, and these supply oil passages 73a, 73b
One end of the opening is closed with lids 74a and 74b.
Both oil supply passages 73a, 73b are for supplying control hydraulic pressure to each control chamber 19, and the other ends of the oil supply passages 73a, 73b are connected to a control hydraulic pressure source via anti-lock control valve means 6a, 6b. Connected to 5.

Referring again to FIG. 1, the control fluid pressure source 5 consists of a hydraulic pump P that pumps control fluid, such as hydraulic oil, from a reservoir R, and an accumulator A _c .
Hydraulic pump P is driven as necessary during vehicle operation. Further, the control hydraulic pressure source 5 is provided with a hydraulic pressure sensor S for detecting failures and oil pressure failures of the hydraulic pump P, as well as the start and stop of driving the hydraulic pump P.

The anti-lock control valve means 6a, 6b consists of first solenoid valves V1a, V1b which are closed during normal times and second solenoid valves V2a, V2b which are open during normal times, and when each wheel is about to lock, 1st
The solenoid valves V1a and V1b are driven to open, and the second solenoid valves V2a and V2b are driven to close.

The first solenoid valves V1a and V1b are supply oil passages 73a,
73b, and the second solenoid valve V2
a, V2b are provided in the middle of return oil passages 75a, 75b that branch from the supply oil passages 73a, 73b and reach the reservoir R between the first electromagnetic valves V1a, V1b and the control chamber 19.

Further, the first solenoid valves V1a, V1b and the second solenoid valves V2a, V2b have a cylindrical housing 76a,
The housings 76b are arranged in a stacked manner, and a reservoir R is disposed above the housings 76a and 76b.

Each brake hydraulic modulator M _fl , M _fr , M _rl ,
A cap 7 is fitted to the upper end of the casing 7 so as to cover the lid members 14 and 14' of the M _rr , and support parts 78a and 78b each having an arc-shaped cross section with an open top are mounted on the upper surface of the cap 77. will be provided. Each support portion 78a, 78b includes a solenoid valve V1a, V2a of both anti-lock control valves 6a, 6b;
Connection members 79a and 79b for connecting wiring to V1b and V2b are fitted and held, respectively.

Next, the operation of this embodiment will be explained. First, the brake hydraulic modulators M _fl and M _fr for both front wheels will be explained.
To explain the operation of the piston rod 33, when the brake pedal 83 is not operated and the brake pedal 83 is not operated, the piston rod 33 is moved downward by the spring force of the first spring 48, and the second piston 22 is in contact with the partition wall 9. There is. Therefore, in the first valve mechanism 53,
The drive rod 57 is pressed by the pressing portion 60 of the second piston 22, and the valve body 56 is separated from the valve seat 59 to open the valve. Therefore, from the output port 2 of the master cylinder 1, the oil passage 3, the inlet oil passage 21, the oil passage 20, the input oil pressure chamber 18, the valve chamber 54, the valve hole 55, the output oil pressure chamber 23, the oil passage 25, the outlet oil A hydraulic path is formed via the passage 26 and the oil passage 6 to the wheel brake 5. This makes it possible to very easily fill the brake hydraulic system with hydraulic oil, similar to a brake hydraulic system not equipped with a brake hydraulic control device for anti-lock control. That is, in the past, there was a hydraulic path from the master cylinder M _c to the input hydraulic chamber 18 and a hydraulic path from the output hydraulic chamber 23 to the wheel brakes B _fl , B _{fr .}
Whereas it was necessary to fill the hydraulic oil separately from the hydraulic path up to the front wheel, the braking hydraulic path from the master cylinder M _c to the brakes B _fl and B _fr for both front wheels is now established. master cylinder
By filling hydraulic oil from the M _c side, filling of hydraulic oil to both brakes B _fl and B _fr is completed.

When the brake pedal 83 is used to perform a brake operation, the output ports 1a and 1b of the master cylinder M _c
The braking hydraulic pressure from the brake is supplied to both brakes B _fl and B _fr via the hydraulic path. At this time, since the control fluid pressure from the control fluid pressure source 5 is not supplied to the control chamber 19, the second piston 22 remains displaced to the maximum extent toward the partition wall 9 by the spring force of the first spring 48.
The first valve mechanism 53 remains open. In this way, the braking oil pressure is transferred from the master cylinder M _c to each brake.
Since it is directly supplied to B _fl and B _fr , the piston stroke switch that was conventionally installed to detect brake hydraulic pressure leakage can be omitted, and the system can be used in the same way as a brake hydraulic system that does not have an anti-lock control function. Hydraulic leakage can be detected.

If the braking force becomes excessive during brake operation and the wheels are about to lock, the second solenoid valve V2
Since the first solenoid valve V1a is closed and the first solenoid valve V1a is opened, the antilock control hydraulic pressure from the control hydraulic pressure source 5 is supplied to the control chamber 19. As a result, the first piston 17 and the piston rod 33 are pressed upward against the downward force generated by the first spring 48 and the hydraulic pressure of the input hydraulic chamber 18 . At this time, the second piston 22 moves upward together with the piston rod 33 while in contact with the receiving member 36 until the upward force due to the hydraulic pressure of the output hydraulic chamber 23 and the downward force due to the second spring 52 are balanced. Along with this, the second piston 22 separates from the partition wall 9, so the valve body 57 of the first valve mechanism 53
is seated on the valve seat 59 and closed, cutting off the supply of braking hydraulic pressure to both brakes _Bfl and _Bfr , and increasing the volume of the output hydraulic pressure chamber 23. As a result, the brake hydraulic pressure is reduced and the wheels are prevented from locking up.

Here, the operation during excessive anti-lock control such as when driving on a rough road or when the control hydraulic pressure source 5 is out of order will be explained. First, during non-braking, the first piston 17 and the piston rod 33 move upward against the spring force of the first spring 48 as the control fluid pressure in the control chamber 19 increases, but the second piston 22 moves upward. The upward movement is restrained by the second spring 52, and the second piston 22 moves downward relative to the piston rod 33. As a result, in the second valve mechanism 61, the rod 40 integrated with the second piston 22 presses the drive rod 68, and the valve body 66 separates from the valve seat member 64 to open the valve. Therefore, the input hydraulic pressure chamber 18 and the output hydraulic pressure chamber 23 are communicated with each other, and the inside of the output hydraulic pressure chamber 23 is prevented from becoming a negative pressure that would be inconvenient for practical use. At this time, the relative movement between the second piston 22 and the piston rod 33 is until the rod 40 comes into contact with the side wall of the locking hole 39, and from then on, the second piston 22 moves upward together with the piston rod 33.

When a braking operation is performed in such a state, the braking oil pressure supplied from the master cylinder M _c to the input oil pressure chamber 18 is transferred to the output oil pressure chamber 2 through the second valve mechanism 61.
3, and both brakes are connected via oil passages 3a and 3b.
Acts on B _fl and B _fr . At this time, if the upward force of the second piston 22 due to the hydraulic pressure of the output hydraulic pressure chamber 23 becomes larger than the downward force due to the spring force of the second spring 52,
The second piston 22 moves relative to the piston rod 33 until both are balanced, and the same operation as during braking described above is performed.

Next, assume that the control fluid pressure in the control chamber 19 abnormally increases during braking. In this case, the piston rod 33 moves upward, and accordingly, the second piston 22 receives the upper power from the hydraulic pressure of the output hydraulic chamber 23 and the second
It moves upward together with the piston rod 33 until the downward force due to the spring force of the spring 52 is balanced. When the piston rod 33 further moves upward, the second piston 22 moves upward as the hydraulic pressure in the output hydraulic chamber 23 decreases.
3, and the second valve mechanism 61 opens. This prevents the oil pressure in the output oil pressure chamber 23 from dropping to a negative pressure that would pose a practical problem. Further, since the amount of oil in excess of the amount of oil required to be removed from the input hydraulic chamber 18 for proper anti-lock is led to the output hydraulic chamber 23, the brake pedal 83 is subjected to more kickback than is required for anti-lock control. It will never occur.

Brake hydraulic modulator for both rear wheels M _rl , M _rr
The brake hydraulic modulator for both front wheels basically operates in the same way as the above-mentioned brake hydraulic modulators M _fl and M _fr .
The pressure receiving area of the first piston 17' is the second piston 2
Since it is set smaller than the pressure receiving area of 2,
Braking oil pressure reduced in proportion to the oil pressure in the input oil pressure chamber 18 can be output from the output oil pressure chamber 23, and functions as a proportional pressure reducing valve. Therefore, the output hydraulic pressure of the master cylinder M _c is proportionally reduced and supplied to both rear wheel brakes B _rl and B _rr .

In such a brake hydraulic control device, a brake hydraulic modulator for the right front wheel is supplied with hydraulic pressure from one output port 1a of the master cylinder M _c .
Brake hydraulic modulator for M _fr and left rear wheel
M _rl , the left front wheel brake hydraulic modulator M _fl and the right rear wheel brake hydraulic modulator M _rr , which are supplied with hydraulic pressure from the other output port 1b, are arranged on a straight line parallel to each other, and each output A common inlet oil passage 71; 21 for guiding the output hydraulic pressure from the ports 1a; 1b to the corresponding pairs of hydraulic modulators _Mfr , _Mrl ; _Mfl , _Mrr , and each pair of hydraulic modulators _Mfr. , M _rl ; M _fl , M _rr
Since the communication passages 29 and 29 can be formed in a straight line in the casing 7, it is possible to simplify the oil passage and facilitate processing as a whole.

Also, brake hydraulic modulator for left and right front wheels.
M _fl , M _fr , one anti-lock control valve means 6a, and brake hydraulic modulators for left and right rear wheels.
Since M _rl , M _rr and the other anti-lock control valve means 6b are arranged on a straight line parallel to each other, the supply oil passages 73a and 73b can be provided in a straight line, which also makes the oil passage simple. This allows for easier processing and processing.

Furthermore, the inlet oil passages 21, 71 and the outlet oil passage 2
6, 26', 72, and 72' are opened on the same side surface 7a of the casing 7, so that the side surfaces of the casing 7 other than the side surface 7a may be surrounded by other objects when mounted on a vehicle. This is advantageous in terms of layout.

Moreover, each modulator M _fl , M _fr , M _rl , M _rr
Since the cylinder is constructed by assembling the components into the cylinder hole 8 which is open at the top, the cylinder can be inspected and cleaned while being mounted on the vehicle.

Additionally, anti-lock control valve means 6a, 6b
are integrated into the casing 7, the reservoir R is arranged above the anti-lock control valve means 6a and 6b, and the connecting members 79a and 79b are fixedly supported by the cap 77, so that the whole structure is compact. be able to.

C. Effects of the invention As described above, according to the invention, in the two-system X-piping type vehicle brake hydraulic control system, the brake hydraulic modulator for the right front wheel and the brake hydraulic pressure modulator for the left rear wheel are controlled by the input hydraulic pressure of both modulators. The first communication passage that communicates between the chambers and the first inlet oil passage that communicates the input hydraulic pressure chamber of one of the modulators with the oil passage that connects to the first output port of the tandem master cylinder are arranged on the same axis. The brake hydraulic modulator for the left front wheel and the brake hydraulic modulator for the right rear wheel are arranged in parallel in a common casing bored in a line, and the brake hydraulic modulator for the left front wheel and the brake hydraulic pressure modulator for the right rear wheel have a second communication passage that communicates between the input hydraulic chambers of both modulators, and Since the input oil pressure chamber of one modulator and the second inlet oil passage which communicates with the oil passage connected to the second output port of the same master cylinder are arranged in parallel in a common casing that is bored on the same axis, Both hydraulic modulators are provided with a common inlet oil passage for guiding the output hydraulic pressure from each output port of the tandem master cylinder to the corresponding pair of hydraulic modulators, and a communication passage between the pair of hydraulic modulators. It is possible to perform drilling on the same axis in a common casing, and these machining operations can be performed extremely quickly and accurately. Since it has a branch joint function that distributes the output hydraulic pressure from each output port to a corresponding pair of hydraulic modulators, there is no need for special branch piping in the middle of the oil path from each output port to the casing.
Overall, the oil passage structure can be simplified and workability improved, which can greatly contribute to cost reduction.

[Brief explanation of the drawing]

The drawings show one embodiment of the present invention, and Fig. 1 is an overall hydraulic system diagram, Fig. 2 is an overall front view, Fig. 3 is a plan view of Fig. 1, and Fig. 4 is a diagram of Fig. 2. The right side view and FIG. 5 are enlarged sectional views taken along the line V-V in FIG. 2. 1a, 1b...first and second output ports, 6
a, 6b...Antilock control valve means, 7...Casing, 7a...Side surface, 8...Cylinder hole, 2
1, 71... Second, first inlet oil passage, 29... Communication passage, 26, 26', 72, 72'... Outlet oil passage,
B _fl , B _fr , B _rl , B _rr ... Wheel brake, M _c ... Master cylinder, M _fl ... Brake hydraulic modulator for left front wheel, M _fr ... Brake hydraulic modulator for right front wheel, M _rl ... Left Brake hydraulic modulator for rear wheel, M _rr ...Brake hydraulic modulator for right rear wheel.

Claims (1)

[Claims for Utility Model Registration] (1) First output port 1 of tandem type master cylinder M _c having a pair of output ports 1a and 1b.
A brake hydraulic modulator M _fr for the right front wheel and a brake hydraulic modulator _Mrl for the left rear wheel are configured to generate braking hydraulic pressure according to the output hydraulic pressure from the master cylinder M c from the second output port 1b of the master cylinder M _c . A front left wheel brake hydraulic modulator M _fl and a right rear wheel brake hydraulic modulator M _rr are configured to generate braking hydraulic pressure according to the output hydraulic pressure, and the above-mentioned brake hydraulic modulator M rr is configured to reduce the braking hydraulic pressure when the wheels are about to lock. Brake hydraulic modulator for left and right front wheels M _fl , M _fr and left,
Brake hydraulic modulator for right rear wheel M _rl , M _rr
In the vehicle brake hydraulic control device comprising antilock control valve means 6a and 6b for controlling the supply and release of control hydraulic pressure to the brake hydraulic pressure, the right front wheel brake hydraulic modulator M _fr and the left rear wheel brake hydraulic modulator M _rl are , a first communication passage 29 that communicates between the input hydraulic chambers 18 of both modulators M _fr and M _rl , and an oil passage that connects the input hydraulic chamber 18 of one of the modulators M _fr to the first output port 1a. 2a, and the brake hydraulic modulator for the left front wheel _Mfl and the brake hydraulic modulator for the right rear wheel _Mrr. is the input hydraulic chamber 18 of both modulators M _rl and M _rr .
The second communication passage 29 that communicates with each other and the second inlet oil passage 21 that communicates the input hydraulic chamber 18 of one of the modulators M _fl with the oil passage 2b that connects to the second output port 1b are connected to each other. A brake hydraulic control device for a vehicle, characterized in that it is installed in parallel in a common casing 7 bored on the same axis. (2) Each of the brake hydraulic modulators M _fl , M _fr ,
The inlet oil passages 21 and 71 of M _rl and M _rr and the outlet oil passages 26, 26', 71 and 71' connected to each wheel brake B _fl , B _fr , B _rl and B _rr are provided on one side 7a of the casing 7. A vehicle brake hydraulic control device according to claim (1) of the utility model registration, characterized in that the device is opened. (3) Each of the brake hydraulic modulators M _fl , M _fr ,
Utility model registration claim (1) characterized in that M _rl and M _rr are constructed by incorporating components into a bottomed cylinder hole 8 that extends vertically and is bored in the casing 7. The vehicle brake hydraulic control device described above.