JP2588768B2 - Braking hydraulic control device - Google Patents

Description

DETAILED DESCRIPTION OF THE INVENTION A. Object of the Invention (1) Field of Industrial Application The present invention relates to a brake hydraulic control device.

(2) Prior Art Conventionally, as such a brake hydraulic pressure control device, as disclosed in Japanese Utility Model Laid-Open No. Sho 62-77068, for example, a hydraulic pressure output from a master cylinder in accordance with the amount of depression of a brake pedal is controlled by hydraulic pressure. It is controlled by a braking hydraulic pressure control device and supplied to the brake device.

(3) Problems to be Solved by the Invention However, it is difficult to say that the above-described conventional hydraulic braking hydraulic control device has a complicated configuration and can perform precise control.

In view of this, the present applicant has already proposed a braking hydraulic pressure control device in which the hydraulic pressure from a hydraulic pressure supply source is electrically controlled and applied to a braking device (Japanese Patent Application No. 63-1550). According to such a brake hydraulic pressure control device, it is possible to precisely control the brake hydraulic pressure with a simple configuration, but when the hydraulic supply source fails, the brake hydraulic pressure cannot be obtained.

The present invention has been made in view of such circumstances,
The brake hydraulic pressure is controlled by electrical control to simplify the configuration and enable more precise braking pressure control.
In addition, it is an object of the present invention to provide a brake hydraulic pressure control device that can obtain a brake hydraulic pressure by depressing a brake pedal when a hydraulic supply source fails.

B. Configuration of the Invention (1) Means for Solving the Problems The device of the present invention provides communication with a hydraulic supply source and an oil tank,
An electric hydraulic pressure adjusting means connected to a brake device for applying a hydraulic pressure corresponding to the hydraulic pressure in the output chamber, the piston being connected to a brake pedal; Braking hydraulic pressure generating means slidably fitted to the cylinder body with the brake hydraulic pressure generating chamber facing the end face opposite to the pedal; and a hydraulic chamber communicating with the brake hydraulic pressure generating chamber facing one end face and supplying hydraulic pressure. A spool valve body having a hydraulic pressure source hydraulic chamber communicating with the source facing the other end surface, and a position on the hydraulic pressure source hydraulic chamber side capable of connecting the hydraulic chamber to a brake device and the hydraulic chamber side for shutting off between the brake device and the hydraulic chamber. And a switching valve means slidably fitted to the main body so as to be movable between the positions described above.

Further, according to the present invention, a release port communicating with the oil tank is provided in the main body of the switching valve means, and the spool valve element is configured to communicate the hydraulic chamber with the release port at a position on the hydraulic chamber side. Is a second feature.

Further, a third feature of the present invention is that the output chamber of the electric hydraulic pressure adjusting means is connected to the oil tank via the switching valve means.

(2) Operation According to the configuration of the first feature, it is possible to electrically control the hydraulic pressure of the output chamber in the electric hydraulic pressure adjusting means,
A braking oil pressure corresponding to the oil pressure in the output chamber can be applied to the brake device. In addition, in the event of a failure in the hydraulic supply source, the hydraulic pressure generated in the brake hydraulic pressure generation chamber in response to the depression of the brake pedal in the brake hydraulic pressure generation means acts on the brake device via the switching valve means that switches according to the failure of the hydraulic supply source. Can be done.

Further, according to the second feature, it is possible to connect the brake hydraulic pressure generation chamber to the oil tank during normal operation of the hydraulic pressure supply source, so that the brake pedal can be depressed without any trouble.

Further, according to the third feature, it is possible to rationalize the piping route to the oil tank.

(3) Embodiment Hereinafter, an embodiment of the present invention will be described with reference to the drawings. First, in FIG. 1 showing a first embodiment of the present invention, a brake value for a left front wheel mounted on a left front wheel and a right front wheel of a vehicle, respectively. Modulators 1 _FL , 1 _FR as electric hydraulic pressure adjusting means are individually interposed between B _FL and a brake device B _FR for the front right wheel, a hydraulic supply source S and an oil tank T, respectively. common and a left rear wheel brake device B _RL and the right rear wheel brake device B _RR respectively mounted on the right rear wheel, two brake device B _RL between the hydraulic supply source S and the oil tank T, the B _RR A modulator 1 _R as an electric hydraulic pressure adjusting means is interposed, and these modulators 1
Each of the brake devices B _FL , B _FR , B _RL , B _RR by the operation of _FL , 1 _FR , 1 _R
Is supplied with braking hydraulic pressure.

Each of the brake devices B _FL , B _FR , B _RL , and B _RR includes a cylinder 2 and a piston 3 slidably fitted in the cylinder 2, and is defined between the cylinder 2 and the piston 3. The movement of the piston 3 according to the braking oil pressure supplied to the braking oil pressure chamber 4 generates a braking force.

Hydraulic control source S comprises a pumping gels hydraulic pump P and the hydraulic oil from the oil tank T, the accumulator A ₁ which is connected to the hydraulic pump P, and a pressure switch PS for controlling the operation of the hydraulic pump P, respectively .

The modulators 1 _FL , 1 _FR , 1 _R are arranged side by side in parallel with each other on a common housing 5, and the modulators 1 _FL , 1 _FR , 1 _R have basically the same configuration. since, and explained in detail hereinafter structure of the modulator 1 _FL, it omitted the detailed description is with respect to the modulator 1 _FR, 1 _R.

The housing 5 has a single input port 6 connected to the hydraulic supply S via a one-way valve 9 that allows only the flow from the hydraulic supply S, and a single release port communicating with the oil tank T. 7 and three output ports 8 leading to the brake hydraulic chamber 4
_FL, 8 _FR, 8 _R and is provided, the output port 8 _FL, 8 _FR are arranged individually corresponding to the front-wheel brake device 8 _FL, 8 _FR, residual output port 8 _R is the rear-wheel brake The devices B _RL and B _RR are provided so as to be commonly used.

The modulator _1FL includes a spool 10 slidably fitted to the housing 5 and a linear solenoid 11 attached to the housing 5 to press the spool 10 in the axial direction. The output chamber 17 is linked to and connected to the
Is formed. Thus, the spool 10 changes the state of communication between the input port 6 and the output chamber 17 communicating with the hydraulic pressure source S and the state of communication between the output chamber 17 and the release port 7 by the thrust of the linear solenoid 11 applied to one axial end. The switching is performed according to a change in the axial position due to the magnitude relationship with the hydraulic pressure of the output chamber 17 acting on the other axial end.

A cylinder hole 12 is formed in the housing 5, and the spool 10 is slidably fitted in the cylinder hole 12. The linear solenoid 11 is mounted on the outer surface of one side (left side in FIG. 1) of the housing 5, and a driving rod 15 of the linear solenoid 11 is formed in the housing 5 through one end of a cylinder hole 12. Is inserted coaxially into the cylinder hole 12 from the insertion hole 16. The other end of the spool 10 and the cylinder hole 12
An output chamber 17 is defined between the output chamber 17 and the other end wall. The output chamber 17 houses a return spring 18 for urging the spool 10 toward one end in the axial direction, that is, toward the linear solenoid 11. Therefore, the drive rod 15 is always in contact with one end of the spool 10, and the spool 10 and the linear solenoid 11 are linked and connected.

The spool 10 has lands that form an annular groove 24 therebetween.
25 and 26 are provided. On the inner surface of the cylinder hole 12, there is formed an annular recess 28 which can communicate between the release port 7 and the annular groove 24.
And an annular recess 29 capable of communicating between the input port 6 and the annular groove 24 are provided at intervals in the axial direction. Further, the spool 10 has an opening at the end face on the output chamber 17 side and an annular groove 24.
The annular recess 28 is closed by the land 25 when the spool 10 is in the hydraulic supply position to move the spool 10 to the right to communicate the annular recess 29 with the annular groove 24, and the hydraulic supply position The spool 10 moves to the left and the annular recess 28
The annular concave portion 29 is closed by the land 26 when in the hydraulic release position communicating with 24, and both annular concave portions 28 and 29 are closed by the lands 25 and 26 at the intermediate position between the hydraulic supply position and the hydraulic release position. .

That is, the spool 10 has a hydraulic supply position for supplying the hydraulic pressure from the hydraulic supply source S to the output chamber 17 by connecting the annular groove 24 communicating with the output chamber 17 via the communication passage 27 to the annular recess 29, and 24 is communicated with the release port 7 to move the output chamber 22 in the axial direction between a hydraulic release position where the output chamber 22 communicates with the oil tank T, and the push of the linear solenoid 11 acting on one axial end of the spool 10 is performed. The pressure acts toward the hydraulic pressure supply position, and the hydraulic pressure applied to the other axial end of the spool 10 by the hydraulic pressure of the output chamber 17 acts toward the hydraulic pressure release position.

The other end wall of the cylinder hole 12 is provided with a protrusion 30 which is in contact with the other end surface of the spool 10 and can close the communication hole 27, and the other end wall is displaced from the protrusion 30. The output chamber 17 is connected to a brake device _BFL via an oil passage 31 formed in the brake chamber _BFL . Thus, the projection 30 is provided between the output chamber 17 and the brake device B _FL
When the hydraulic pressure failure occurs in the hydraulic path between the spool 10 and the spool 10 moves to the right as much as possible, it abuts on the other end surface of the spool 10 to close the communication hole 27. 11 _FR , 11 _R, that is, the brake devices B _FR , B _RL , B _RR are prevented from being affected by the hydraulic pressure failure.

In Figure 2, the linear solenoid 11 of the modulator 1 _FL is to generate a thrust in accordance with the input electrical quantity. That is, the near solenoid 11 _FL generates a thrust corresponding to the excitation current I _{1 to} I ₅ or the voltage when the resistance is constant, and in a certain stroke range, the excitation current is I. The thrust F generated by the linear solenoid 11 when the constant is K is represented by F = KI.
The hydraulic pressure of the output chamber 17 is set to Pw, and the spool facing the output chamber 17
When the pressure receiving area of 10 is Sc, the hydraulic pressure f acting on the spool 10 is represented by f = Sc · Pw. Therefore, F = K
When I> Sc · Pw, the spool 10 moves to the right hydraulic supply position, and when F = KI <Sc · Pw, the spool 10 moves to the left hydraulic release position.

As described above, when the spool 10 moves in the axial direction according to the magnitude relationship between the thrust F and the hydraulic pressure f, hydraulic oil is supplied to the output chamber 17 from the hydraulic pressure source S or the hydraulic pressure in the output chamber 17 is released. Therefore, the hydraulic pressure Pw is given by the following equation.

Pw = (K / Sc) · I (1) That is, the hydraulic pressure Pw is proportional to the supply current I to the linear solenoid 11, and the hydraulic pressure Pw of the output chamber 17 is arbitrarily determined by the current supplied to the linear solenoid 11. The control hydraulic pressure according to the hydraulic pressure Pw of the output chamber 17 can be applied to the brake hydraulic chamber 4 of the brake device _BFL .

Meanwhile, the brake device _{B FL, B FR, B RL} , the B _RR, each modulator I _FL, I _FR, auxiliary hydraulic supply device in parallel with the I _R
33 is connected.

The auxiliary hydraulic pressure supply device 33 includes a braking hydraulic pressure generation unit 34,
It comprises first switching valve means 35 and second switching valve means 36.

The braking oil pressure generating means 34 is configured by a piston 39 slidably fitted in a cylinder hole 38 provided in a cylinder body 37, and the brake pedal 32 is connected to the piston 39. Thus, the cylinder body 37 on the side opposite to the brake pedal 32
A braking hydraulic pressure generation chamber 40 is defined between the piston and the piston 39,
A spring 41 for urging the piston 39 in a direction to increase the volume of the brake hydraulic pressure generation chamber 40 is housed in the brake hydraulic pressure generation chamber 40.

That is, the cylinder hole 38 has a large diameter hole 38a and a small diameter hole 38b.
Are formed coaxially to form a step 38c therebetween, and the piston 39 slides into the large diameter portion 39a and the small diameter hole 38b which are slidably fitted in the large diameter hole 38a. The small-diameter portion 39b movably fitted is coaxially connected, and the braking hydraulic pressure generation chamber 40 is formed between the large-diameter portion 39a of the piston 39 and the step portion 38c. The spring 41 has a stepped portion 38c and a large diameter portion 3.
It is contracted between 9a.

The first switching valve means 35 comprises a first spool valve body 44 slidably fitted in a first main body 43,
The main body 43 is provided integrally with the cylinder body 37 of the braking hydraulic pressure generating means. Further, a cylinder hole 45 extending in parallel with the cylinder hole 38 is formed in the first main body 43, and the first spool valve body 44 is slidably fitted in the cylinder hole 45.

A first hydraulic chamber 48 is defined between one end wall of the cylinder hole 45 and the first spool valve body 44, and a first hydraulic chamber 48 is defined between the other end wall of the cylinder hole 45 and the first spool valve body 44. 1st hydraulic source hydraulic chamber
49 is defined. The first hydraulic chamber 48 communicates with the braking hydraulic pressure generation chamber 40 through the communication hole 47.
A spring 50 for urging the first spool valve body 44 in a direction to increase the volume of the hydraulic chamber 48 is housed therein.

The first main body 43 is provided with a hydraulic power source port 51 communicating with the first hydraulic power source hydraulic chamber 49, and this hydraulic power source port 51 is connected to the hydraulic power source S. Therefore, the first hydraulic source hydraulic chamber
Hydraulic oil from the hydraulic supply source S is supplied to 49 and hydraulic pressure from the hydraulic supply from the hydraulic supply source S acts on the first spool valve body 44 to the left. The hydraulic pressure due to the generated hydraulic pressure acts rightward, the first spool valve element 44 moves left when the hydraulic supply source S is normally operating, and the hydraulic supply source S fails and the When the hydraulic pressure in the first hydraulic pressure source hydraulic chamber 49 decreases, the first spool valve body 44 moves to the right.

On the outer surface of the first spool valve body 44, annular grooves 52, 53, 54 are provided at intervals from one another in order from the first hydraulic chamber 48 side. On the inner surface of the cylinder hole 45, annular concave portions 55, 56, 57, and 58 are sequentially provided from the first hydraulic chamber 48 side with a space therebetween. The first spool valve body 44 is provided with a passage 59 for communicating the first hydraulic chamber 48 with each of the annular grooves 52 to 54. In addition, the annular recess 55 is located at a position to communicate with the first hydraulic chamber 48 at the right movement position of the first spool valve body 44, the annular recess 56 is located at the annular groove 52 at the right movement position of the first spool valve body 44, and the annular recess 57 is provided. Is arranged to communicate with the annular groove 53 when the first spool valve element 44 moves to the right, and the annular recess 58 is arranged to communicate with the annular groove 54 when the first spool valve element 44 moves to the left.

A connection port 60 communicating with the first hydraulic chamber 48 is formed in the first main body 43, and the connection port 60 communicates with the release port 7. The first main body 43 has output ports 61, 62, 63 communicating with the annular recesses 55, 56, 57, and a release port 64 communicating with the annular recess 58.
And the output port 61 is connected to the brake devices B _RL and B
_RR , output port 62 to brake device B _FR , output port 6
3 is connected to the brake device _BFL , and the release port 64 is connected to the oil tank T.

In the first switching valve means 35, when the hydraulic pressure of the first hydraulic pressure source hydraulic chamber 49 is high in a state where the hydraulic pressure supply source S is operating normally, the first spool valve body 44 is moved to the left moving position as shown in FIG. In this state, the first hydraulic chamber 48, that is, the release port 7 and the brake hydraulic pressure generating chamber 40 are communicated with the oil tank T, and the hydraulic pressure in the first hydraulic power source hydraulic chamber 49 decreases due to the failure of the hydraulic supply source S or the like. then the first spool valve body 44 is moved rightward to the first hydraulic chamber 48 and the oil tank T brake hydraulic pressure generating chamber 40 is the output ports 61 to 63 i.e. the brake system with between is interrupted with B _FL, B _FR , B _RL and B _RR .

The second switching valve means 36 has one end face of a second hydraulic chamber communicating with a reaction chamber 65 defined facing the end face of the piston 39 in the braking hydraulic pressure generating means 34 and a second hydraulic pressure communicating with the hydraulic supply source S. A second spool valve body 67 having a source hydraulic chamber 66 facing the other end face is slidably fitted to the second main body 68.

The second main body 68 is provided integrally with the cylinder body 37 of the braking oil pressure generating means 34 and the first main body 43 of the first switching valve means 35. The second main body 68 includes a second spool valve body 67.
The cylinder hole 6 coaxially connected to the small-diameter hole portion 38b of the cylinder hole 38 in the braking hydraulic pressure generation means 34 so that the cylinder hole 6 can be slidably fitted.
9 is formed with a larger diameter than the small diameter hole 38b. Thus, the reaction chamber 65 is defined between the piston 39 and one end surface of the second spool valve body 67, and the second hydraulic chamber and the reaction chamber 65 are defined as a common chamber. The second hydraulic source hydraulic chamber 66 is provided with the other end surface of the second spool valve body 67 and the second main body 68.
The first main body 43 and the second main body 68 of the first switching valve means 35 have a communication hole 70 for communicating the first hydraulic power source hydraulic chamber 49 with the second hydraulic power source hydraulic chamber 66. Is drilled.

An annular recess is formed on the inner surface of the cylinder hole 69 in order from the reaction chamber 65 side.
The second spool valve body 67 is provided with an annular groove 73 on the outer surface thereof. In addition, a communication passage 74 for communicating the reaction chamber 65 with the annular groove 73 is formed in the second spool valve 67. The second main body 68 has an annular recess.
Connected port 75 is drilled leading to 71, the connection port 75 are monkey connected to the accumulator A _2. Further, a passage 76 communicating with the annular concave portions 58, 72 is formed in the first and second main bodies 43, 68.

In the second switching valve means 36, when the hydraulic pressure from the hydraulic pressure source S is acting on the second hydraulic pressure source hydraulic chamber 66, the second spool valve element 67 is at the left-moving position. Communicates with the annular recess 71, and the reaction chamber 65 is an accumulator.
It communicates with the A _2. When the hydraulic pressure from the hydraulic pressure source S decreases, the second spool valve body 67 moves to the right movement position due to the hydraulic pressure of the reaction chamber 65. In this state, the annular groove 73 communicates with the annular recess 72, and therefore the reaction chamber 65 It will communicate with the oil tank T via the annular recess 72, the passage 76, the annular recess 58 and the release port 64.

Next, the operation of this embodiment will be described. First, it is assumed that a brake operation is performed by depressing the brake pedal 32 in a state where the hydraulic pressure source S is normally operating and the linear solenoid 11 is also normally operating. . At this time, since the hydraulic pressure from the hydraulic supply source S acts on the first and second hydraulic source hydraulic chambers 49, 66 of the first and second switching valve means 35, 36 in the auxiliary hydraulic supply device 33, both spools The valve bodies 44 and 67 are moving to the left in FIG. 1, and the release port 7 and the brake hydraulic pressure generation chamber 40 are connected via the first hydraulic chamber 48, the passage 59, the annular groove 54, the annular recess 58 and the release port 64. To the oil tank T and the reaction chamber
65, communication passage 74, annular groove 73 communicates with the accumulator A ₂ via the annular recess 71 and the connection port 75. Thus while receiving a reaction force from the accumulator A ₂ will be the braking operation by depressing the brake pedal 32, it is possible to obtain a sense of braking operation.

On the other hand, the amount of depression of the brake pedal 32 is detected by a detector (not shown), and an electric quantity corresponding to the depression operation amount is applied to the linear solenoid 11, whereby the linear solenoid 11 exerts a thrust corresponding to the braking operation amount. It will be, that the output chamber 17 of the modulator 1 _FL hydraulic pressure corresponding to the hydraulic that amount of braking operation corresponding to the thrust is generated, the hydraulic pressure in the output chamber 17 is applied to the braking oil pressure chamber 4 of the brake device B _FL Accordingly, a braking force corresponding to the braking operation amount can be obtained by the brake device _BFL .

When the failure of the hydraulic supply source S is oil pressure from the hydraulic pressure supply source S decreases, the hydraulic pressure generated in the output chamber 17 of the modulator 1 _FL becomes difficult, the communication passage 27 the spool 10 is maximally moved in the output chamber 17 side Closed. On the other hand, in the auxiliary hydraulic pressure supply device 33, the hydraulic pressure in the first and second hydraulic pressure source hydraulic chambers 49, 66 decreases, so that the spool valve bodies 44, 67 in the first and second switching valve means 35, 36 in FIG. Moves to the right and brake oil pressure generation chamber 40
Communicates with the respective output ports 61, 62, 63, so that the brake oil pressure generated in the brake oil pressure generating chamber 40 in response to the depression of the brake pedal 32 directly acts on each of the brake devices _BFL , _BFR , _BRL , _BRR. Therefore, the braking hydraulic pressure can be reliably obtained despite the failure of the hydraulic pressure supply source S.

In addition, when the hydraulic pressure source S fails, the second switching valve means 36 of the auxiliary hydraulic pressure supply device 33 uses the second spool valve element 67.
Connection port 75 leading to the accumulator A ₂ by rightward movement is blocked reactionary chamber 65, since the recoil chamber 65 will be communicated with the oil tank T, is possible to prevent the ineffective stroke of the brake pedal 32 is generated it can.

The release port 7 is connected to the connection port 60 of the first switching valve means 35.
, It is possible to simplify the hydraulic path to the oil tank T.

In the first embodiment, the cylinder body 37 of the braking hydraulic pressure generating means 34 of the auxiliary hydraulic pressure supply device 33, the first main body 43 of the first switching valve means 35, and the second main body 68 of the second switching valve means 36 are integrated. However, they may be configured separately. In this case, the second hydraulic chamber communicating with the reaction chamber formed facing the end face of the piston 39 in the braking hydraulic pressure generating means 34 is provided with the second hydraulic chamber in the second switching valve means 36. It is formed facing one end of the spool valve body 67.

FIG. 3 shows a second embodiment of the present invention, and portions corresponding to the first embodiment are given the same reference numerals.

When the hydraulic pressure from the hydraulic pressure source S drops abnormally for some reason and the modulators 111 _FL , 11 _FR , 11 _R do not operate normally, the brake hydraulic pressure according to the braking operation amount is changed to the respective brake devices B. A supplementary hydraulic pressure supply device 33 'for supplying _FL , _BFR , _BRL , and _BRR has a piston 39' connected to the brake pedal 32 and a brake hydraulic pressure generation chamber 40 'on the end face opposite to the brake pedal 32. And a brake hydraulic pressure generating means 34 'slidably fitted to the cylinder body 37'
A spool valve element 44 ′ having a hydraulic chamber 48 ′ communicating with 40 ′ facing one end face and a hydraulic source hydraulic chamber 49 ′ communicating with the hydraulic supply source S facing the other end face is slidably fitted to the main body 43 ′. And switching valve means 35 '.

The braking oil pressure generating means 34 'is configured such that a piston 39' is slidably fitted in a cylinder hole 38 'provided in a cylinder body 37'.
32 are linked. Thus, on the opposite side of the brake pedal 32, between the cylinder body 37 'and the piston 39', a braking hydraulic pressure generation chamber is provided.
40 'is defined, and a spring 41' for urging the piston 39 'in a direction to increase the volume of the brake hydraulic pressure generation chamber 40' is housed in the brake hydraulic pressure generation chamber 40 '.

The main body 43 'of the switching valve means 35' is provided integrally with the cylinder body 37 'of the braking oil pressure generating means 34'. The main body 43 'has a cylinder hole 45' extending in parallel with the cylinder hole 38 '. The spool valve body 44 'is provided with the cylinder bore.
It is slidably fitted to 45 '.

A hydraulic chamber 48 'is defined between one end wall of the cylinder hole 45' and the spool valve body 44 'and communicates with the brake hydraulic pressure generating chamber 40', and a spring 50 'is housed in the hydraulic chamber 48'. Is done. A hydraulic pressure source hydraulic chamber 49 'communicating with the hydraulic pressure source S is defined between the other end wall of the cylinder hole 45' and the spool valve body 44 '.

Annular grooves 52, 53, and 54 are provided on the outer surface of the spool valve body 44 'at intervals. On the inner surface of the cylinder hole 45 ', annular concave portions 55, 56, 57, 58 are provided with a space therebetween. A passage 59 is formed in the spool valve body 44 'to allow the hydraulic chamber 48' to communicate with each of the annular grooves 52-53.

Output port 6 leading to annular recesses 55, 56, 57 on body 43 '
1, 62, 63 and a release port 64 communicating with the annular recess 58 are drilled, the output port 61 is connected to the brake devices B _RL and B _RR , the output port 62 is connected to the brake device B _FR , and the output port 63 is connected to the brake device. The _BFL and the release port 64 are connected to the oil tank T, respectively.

In the switching valve means 35 ', when the hydraulic pressure in the hydraulic pressure source hydraulic chamber 49' is high while the hydraulic pressure source S is operating normally, the spool valve body 44 'is in the left-moving position as shown in FIG. In this state, the hydraulic chamber 48 ',
0 'is communicated with the oil tank T, and when the hydraulic pressure in the hydraulic pressure source hydraulic chamber 49' decreases due to a failure of the hydraulic pressure supply source S or the like, the spool valve body 44 'moves to the right and the brake hydraulic pressure generating chamber 40' and the hydraulic chamber
48 each output port 61 to 63 i.e. the brake device 'and the oil tank T brake hydraulic pressure generating chamber 40 together between is cut off with _{the' B FL, B FR, B} RL, communicates with the B _RR.

Therefore, according to the second embodiment, similarly to the first embodiment, even if the hydraulic pressure from the hydraulic pressure supply source S or abnormally decreases for some reason, the hydraulic pressure generated in the brake hydraulic pressure generation chamber 40 'is reduced by each brake device. _BFL , _BFR , _BRL , and _BRR can be supplied to _BRR to reliably obtain a braking force.

In the above embodiments, the modulator 1 _FL, I _FR, hydraulic each brake device B _FL in the output chamber 17 in the _{I R, B FR, B RL} , but so as to act directly on B _RR, the output chamber 17 and Means for generating a braking oil pressure corresponding to the oil pressure of the output chamber 17 may be interposed between the brake devices B _FL , B _FR , B _RL , and B _RR .

C. Effects of the Invention As described above, according to the first aspect of the present invention, it is possible to electrically control the braking hydraulic pressure by simplifying the configuration of the electric hydraulic pressure adjusting means, and furthermore, when the hydraulic supply source fails. The hydraulic pressure generated in the brake hydraulic pressure generation chamber of the brake hydraulic pressure generation means can be supplied to the brake device via the switching valve means, and it is possible to reliably obtain the brake hydraulic pressure even when the hydraulic supply source fails.

Further, according to the second feature of the present invention, the brake pedal can be depressed smoothly when the hydraulic pressure supply source is operating normally.

Further, according to the third aspect of the present invention, it is possible to simplify the hydraulic piping path to the oil tank and contribute to piping rationalization.

[Brief description of the drawings]

1 and 2 show a first embodiment of the present invention. FIG. 1 is a hydraulic control circuit diagram, FIG. 2 is a characteristic diagram of a linear solenoid, and FIG. 3 is a second embodiment of the present invention. FIG. 2 is a hydraulic control circuit diagram corresponding to FIG. 1 of the example. 1 _FL , I _FR , I _R …… Modulator as electric type hydraulic adjustment means, 17 …… Output room, 32 …… Brake pedal, 34,34 '……
Braking oil pressure generating means, 35, 35 '... switching valve means, 37, 37' ...
... Cylinder body, 39,39 '... Piston, 40,40' ... Brake hydraulic pressure generation chamber, 43,43 '... Main body, 44,44' ... Spool valve body, 48,48 '... Hydraulic chamber, 49,49 '…… Hydraulic source hydraulic chamber, 64
…… Release port, B _FL , B _FR , B _RL , B _RR …… Brake device, S …… Hydraulic supply source, T …… Oil tank

Claims (3)

(57) [Claims] An electric chamber which is electrically connected to a hydraulic supply source and an oil tank and has an output chamber which can be electrically controlled to be shut off, and which is connected to a brake device for applying a hydraulic pressure corresponding to the hydraulic pressure of the output chamber. Hydraulic pressure adjusting means; brake hydraulic pressure generating means, wherein a piston connected to the brake pedal is slidably fitted to the cylinder body with the brake hydraulic pressure generating chamber facing the end face opposite to the brake pedal; A spool valve body having a hydraulic chamber communicating with the generation chamber facing one end face and a hydraulic source hydraulic chamber communicating with a hydraulic supply source facing the other end face has a hydraulic pressure source side that can communicate the hydraulic chamber with a brake device. Switching valve means slidably fitted to the main body so as to be movable between a position and a position on the hydraulic chamber side for shutting off between the brake device and the hydraulic chamber. Control device. 2. A switching port means is provided on a main body thereof with a release port communicating with an oil tank, and a spool valve element is configured to communicate the hydraulic chamber with the release port at a position close to the hydraulic chamber. The brake hydraulic pressure control device according to item (1), characterized in that: 3. The braking hydraulic pressure control device according to claim 1, wherein the output chamber of the electric hydraulic pressure adjusting means is connected to the oil tank via the switching valve means.