JPS61205545A - Hydraulic brake gear - Google Patents

Abstract

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

Description

Detailed Description of the Invention [Industrial Field of Application] The present invention relates to a pedal-actuated braking force booster that has a booster piston and a booster chamber that forms an auxiliary pressure proportional to the pedal effort, and that is coupled to a master cylinder. The present invention relates to a hydraulic brake device including an auxiliary pressure supply mechanism and a wheel mechanism coupled to a master cylinder.

[Prior art] A hydraulic brake device with the above structure is disclosed in German Patent Publication 3.
108908.9. In a conventional braking force booster, the piston of the master cylinder is disposed in the inner bore of the first cylinder, and together with the booster piston, the piston of the master cylinder is disposed in the inner bore of the first cylinder.
form a partition. The master cylinder piston and booster piston are connected to each other via a tappet. The end face of the booster piston proximate the pedal defines a booster chamber within the housing for coaxial movement with a pedal actuated piston rod, and a lever assembly for actuating the brake valve is articulated with the piston rod. .

By applying a force to the piston rod and activating the brake valve, said pressure moves the booster piston and the piston of the master cylinder connected to this booster piston in the direction of actuation of the brake pressure booster, thereby increasing the pressure of the master cylinder. Creates a pressure corresponding to the working chamber. A wheel brake is connected to the working chamber of the master cylinder, and the pressure thus built up decelerates the vehicle accordingly.

When the booster chamber is pressurized, pressure is similarly applied to the piston rod connected to the brake pedal, and the vehicle driver can sense the pedal feel corresponding to the pedal depression force as feedback information.

[Problems to be Solved by the Invention] When the overall overlap of the vehicle is large, the pressure increase ratio is increased,
It is necessary to maintain the pedal effort and pedal travel distance within a predetermined range. If the booster fails, the distance the pedal travels is short and the pedal effort becomes extremely large. SUMMARY OF THE INVENTION Accordingly, it is an object of the present invention to provide a brake device that operates by reducing the effective area of the master cylinder when the booster fails.

[Means for Solving the Problems, Actions and Effects] According to the present invention, a rapid supply cylinder is provided, the rapid supply cylinder slidably supports a stepped piston provided with two lands, and a large a stepped inner bore having a pressure chamber disposed on the land portion side of the diameter, a supply chamber disposed on the land portion side of the small diameter, and an elastic member acting on the stepped piston in a pressure direction; , wherein the pressure chamber communicates with the booster chamber via a coupling pipe or the like, and the supply chamber is connected to one or both of the working chamber and the brake pipe of the master cylinder via the pressure pipe. The braking device achieves the above objectives.

First, if the braking force booster is working normally,
A piston with two lands operates in conjunction with a sensing member held and guided within the housing of the rapid feed cylinder. The sensing element forms part of an electrical switch inserted in the electrical circuit of a warning device or electronic device for monitoring and controlling brake slip.

In a brake system of the slip control type, a multi-directional control valve is arranged in the brake line, and in a first switching position, this multi-directional control valve controls the pressure from the working chamber of the master cylinder to the wheel cylinder of the wheel brake. In a second switching position, the pressure fluid passage from the working chamber to the wheel brake is blocked, while allowing fluid to flow back from the wheel brake to the working chamber. For this purpose, for example, the multi-directional control valve is switched by means of an electronic device for slip monitoring, and for this purpose the directional control valve is designed as an electrically actuated valve.

The annular chamber formed by the two lands of the stepped piston and the stepped bore of the rapid feed cylinder communicates with the booster chamber via a pressure line, which pressure line has an annular chamber and a feed reservoir. Preferably, a multi-way control valve is provided which acts as an inlet valve connecting the two in the second switching position.

In order to supply pressure fluid from the rapid supply cylinder to the brake circuit, the annular chamber is connected to the brake line via a pressure line, while a shut-off valve is inserted in the pressure line.

Similarly, the supply chamber, which is formed by the small diameter land portion of the stepped piston having two land portions and the stepped inner bore of the rapid feed cylinder, and which contains an elastic member acting on the stepped piston, is connected to the pressure pipe. Through 1. This is advantageous in that it is connected to the brake line of the brake line.

In another embodiment, the booster chamber and the pressure chamber of the rapid feed cylinder are connected to each other by I! A non-return valve is arranged in the coupling line connecting the brake valve, and the sliding member for controlling the brake valve operates together with a valve body, via which the brake valve is connected to the pressure chamber.

In this embodiment, a mechanically actuated multi-way control valve is interposed in a pressure fluid line communicating the valve chamber with the rapid delivery cylinder, the actuating member of said valve being coupled to the II sliding member of the brake valve. Preferably.

The valve body controlling the flow of pressurized fluid from the booster chamber to the pressure chamber of the rapid feed cylinder moves a valve member, e.g. Advantageously, the axial bore of the sliding member is opened or closed, and the valve ball member is movable within the bore of the housing due to said position.

Furthermore, the valve body for controlling the flow of the pressure fluid is provided with a valve hole communicating with a coupling line connected to the rapid supply cylinder, and the said valve hole is connected to the valve body and the control sliding member via a valve groove. and a valve chamber formed by a bore, and further communicates with a supply reservoir through a groove in the housing.

In a preferred embodiment, the valve ball member of the valve body is held concentrically with respect to the axial bore of a control slide longitudinally slidably supported within the housing while opening the valve chamber. The valve groove that connects to the valve hole in the valve body terminates within the valve chamber outside the area of the valve ball member.

In a particularly compact and easy-to-manufacture embodiment, a recess is provided in the booster housing flush with the inner hole of the control sliding member;
a valve member and a valve body having a valve groove, the valve body being retained within the recess and including at least one valve bore extending transversely to the bore and communicating with the valve groove; communicates via a connecting line with a groove in the housing that is connected to the pressure chamber.

Although the present invention can be configured in various embodiments,
Figure 2 schematically depicts two embodiments.

[Example] In FIG. 1, a housing 1 is provided with a cylinder inner hole 2. As shown in FIG. This cylinder inner hole 2 has a small diameter inner hole portion 38 and a large diameter inner hole portion 39. The two master cylinder pistons 40 , 41 are guided in a sealed manner in a small diameter bore 38 , and the booster piston 4 is guided in a sealed manner in a large diameter bore 39 , which booster piston 4 is guided in a sealed manner in a small diameter bore 38 . is combined with Thus, two master cylinder pistons 40.41 are supported in the master cylinder 3, each master cylinder piston being connected via a housing boat 42.43 and a brake line to a wheel brake 14° 15.16.17 of the vehicle. be done. This wheel brake device is basically installed as an option.

The end of the booster piston 4 close to the pedal is provided with an extension 44, and the side close to the pedal is provided with an enlarged head 4.
It is said to be 5. The head 45 and the extension 44 are each supported with an axial play S in a sleeve 10 which forms part of the piston rod 8 which is connected to the brake pedal 46 . sleeve 10
is provided with an annular collar 47 extending axially outwardly;
This collar 47 rests against a shoulder 48 of the housing 1 in the brake release position shown.

A sliding member 9 is guided in a sealed manner inside the sleeve 10 and is connected to an actuating rod 11 which is directly connected to the brake pedal 46 . In the brake release position, the right end of the sliding member 9 abuts against the stepped portion 49 of the sleeve 10, as shown, and the brake release position of the braking force booster is particularly limited.

The housing of the brake booster 5 further includes an inner hole 50,
Inside this inner hole 50 is a sliding member 51 for controlling the brake valve 6.
is supported so as to be slidable in the axial direction. This control sliding member 51 has a substantially cylindrical shape and has an axial inner hole 52.
This axial bore 52 is connected to an unpressurized supply reservoir 55 via a housing groove 53 and a radial bore 54 in the brake release position. Therefore, atmospheric pressure is present in the booster chamber 7, as in the brake release position of the hydraulic braking force booster. Furthermore, the control slide member 51 has a radial groove 56 through which a groove 57 in the housing communicates with the auxiliary pressure source 13 when the control slide member 51 moves a predetermined distance. It communicates with the booster chamber 7.

The control sliding member is pressed in advance in the brake release direction by a pressing spring 58.

On the right side in the figure, the end of the first louver 59 abuts against the end of the control sliding member 51, and the other end of the second louver 59 is engaged in the recess 60 of the sleeve 10. The second lever 62 is connected to the second lever 59 via a rotational coupling part 61, and the upper end of the second lever on the upper side as seen in the figure is supported in a stationary state within the housing 1, and the lower end is supported by the sliding member 9. recess 8
9. This sliding member is slidable in the axial direction relative to the sleeve 1° in the brake activation direction, and a compression spring 63 is provided between the left end of the sliding member 9 and the sleeve 10 as seen in the figure. It is being pinched.

Booster piston 4 is connected to master cylinder piston 41 via tappet 64 .

An annular chamber 65 is formed between the tappet 64, the booster 4, the master cylinder piston 41 and the housing 1, which is permanently connected to the unpressurized supply reservoir 55 via a groove 66 in the housing. The master cylinder piston 41 is sealed with a sealing sleeve 67 and, in the brake release position shown, the central valve 6
9 is connected to the working chamber 26 of the master cylinder 3 through a central inner hole 68 including
is the reservoir 5 that is not pressurized when the brake is applied.
5 and the working chamber 26 is cut off. The master cylinder piston 40 together with the housing 1 likewise encloses an annular chamber 71 which is in constant communication with the unpressurized supply reservoir 55 via a groove 72 in the housing. Also in the master cylinder piston 40, the seal sleeve 7
3 is arranged, and this sleeve 73 makes it possible to close the breathing hole 74 when the master cylinder piston 40 moves, thereby applying pressure to the working chamber 27 of the master cylinder 3.

The first return spring 76 is held between the bottom 75 of the cylinder bore 38 and the master cylinder piston 40. Correspondingly, the return spring 77 is arranged between the two master cylinder pistons 40,41.

The booster chamber 7 is connected to the pressure chamber 21 of the rapid feed cylinder 18 via a housing groove 78 and a connecting line 24 . This rapid supply cylinder 18 has a stepped inner hole 19, and a stepped piston 20 having two land portions is supported in the stepped inner hole 19 so as to be openable against the pressing force of an elastic member 23. ing. The supply chamber 22 has a stepped piston 2
It is formed by a small-diameter land portion 95 or a small-diameter step portion 95 of 0 and the left side portion of the rapid feed cylinder 18, and is connected to the working chamber 26 of the master cylinder 3 via a pressure line 25. A directional control valve 79 is disposed in the coupling conduit 24, and a conduit 8o including a cutoff valve 81 is connected in parallel to the directional control valve 79.

Next, the operation of the above brake device will be explained in detail.

First, to explain the state in which the brake is released, all movable members are in the illustrated positions. The booster chamber of the hydraulic braking force booster communicates with an unpressurized supply reservoir 55 via a control sliding member 51 and a housing groove 53. Therefore, no force is acting on either the piston rod 8 or the booster piston 4, and
Wheel brake 14 coupled to master cylinder 3
゜15, 16, 17 has the same pressure as atmospheric pressure.

When a force F acts on the brake pedal 46, the sliding member moves to the left against the pressing force of the compression spring 63, and the second lever 62 tilts clockwise about the fulcrum 83 in the housing 1. A seal that seals the booster piston 4 and the master cylinder piston 40, and a return spring 7
6.77, the lower side of the louver 59 as seen in the diagram initially experiences relatively strong resistance. Therefore, the upper end of the lever 59 (as seen in the figure) moves the brake valve control slide 51 to the left, which initially closes the housing groove 53 of the brake valve 6 and boosts the booster. The chamber is separated from a reservoir 55 for unpressurized supply. When the force acting on the brake pedal 46 increases, the control sliding member 51
moves further so that the housing groove 57 overlaps the radial groove 56 of this pivot member 51. As a result, pressurized fluid flows into the booster chamber 7 from the pressure source 13 and acts on the small effective area portion of the sliding member 9 and the booster piston 4. As a result, the booster piston 4 moves inside the inner hole 39 to the left in the figure, and moves relative to the sleeve. At this stage of brake engagement, a relatively small reaction force is sensed from the brake pedal 46, which reaction force is due to the pressure in the booster chamber 7 and the effective area of the sliding member. In this case, the effect of the compression spring 63 can be ignored since it is sized to overcome the friction of the seal between the sliding member 9 and the sleeve 10 during the release phase of the brake.

When the pressure in the booster chamber 7 of the hydraulic booster reaches a predetermined level, the booster piston 4 moves to Il! Overcoming the frictional force, the master cylinder piston 41 together with the master cylinder piston 41 starts to move in the working direction, creating a hydraulic pressure in the working chamber 26 of the master cylinder 3, which is applied via the brake line 29 to the wheel brakes 16, 17, respectively. Supplied. On the other hand, the pressure fluid in the working chamber 26 of the master cylinder 3 moves the master cylinder piston 41 in the working direction, so that a pressure is likewise created in the working chamber 27 of the master cylinder 3 and is It is transmitted to the wheel brakes 14.15. Similarly, when a predetermined pressure is built up in the booster chamber 7 of the hydraulic booster 5, the booster piston 4 moves relative to the sleeve 10 through a distance of axial play S, limited by the diameter of the sleeve 10. Due to the full surface area acting, the pressure in the working chamber 26,27 of the master cylinder 3 increases only when the reaction force at the brake pedal 46 increases. Therefore, when the actuation force on the brake pedal 46 is increased, the actuation 11 of the master cylinder 3
The pressure in 26.27 is built up depending on the pressure in the booster to 7 and the wheel brakes 14, 15.16.1 of the vehicle
7 directly.

Releasing the brake has the opposite effect.

Initially, the sleeve 10 moves in the release direction together with the sliding member 9 and the head 45 formed integrally with the booster piston 4
remains in contact with the left end of the sleeve 10 as seen in the figure.

When the pressure in the booster chamber 7 of the hydraulic booster decreases further, the annular collar 47 abuts against the shoulder 48 of the housing 1;
Therefore, the booster piston 4 has a return spring 76,77
As a result, the head 45 moves in the brake release direction by a distance of the play S, and the right front surface (as viewed in the figure) of the head 45 comes into contact with the sleeve 10 again.

In the event of a failure of the pressure source 13, the working chamber 26.27 of the master cylinder 3 and the wheel brakes 14. Although pressure can be built up, the sliding member 9 has to move a free distance relative to the sleeve 10 until it abuts this sleeve 1o. After this, the master cylinder piston 41 is mechanically moved in the actuation direction via the sleeve 10.

As a result, pressure is created in the working chamber 27 in the manner described above. Therefore, even if the pressure source 13 fails, the brake operation is possible. In this case, booster piston 4
The pre-formed play between the sleeve 10 and the sleeve 10 does not affect the movement of the pedal.

The pressure in the booster chamber 7 is controlled by a housing groove 78,
A bypass pipe 80 including the coupling pipe 24 and the cutoff valve 81
The large-diameter land portion or shoulder portion 96 of the stepped piston 20 moves to the left against the pressing force of the elastic member 23 and enters the supply chamber 21 through the rapid supply cylinder 18. The pressure fluid in 22 is forced through the small diameter step from the pressure line 25 into the working chamber 26 and is therefore displaced by the master cylinder piston 40.41 of 211 when the brake is applied in the non-fault condition. The pressure fluid in the working chamber 26.27 of 211 is connected to the brake line 28.29.
In addition to being supplied with pressure fluid within the supply chamber 22. However, if the pressure in the booster chamber 7 drops below a predetermined level, for example due to a failure of the auxiliary pressure source 13, the stepped piston 20 remains in its initial position on the right side.
The pressure fluid in the supply chamber 22 is not used for braking action. The capacity of the feed chamber 22, which is moved by a stepped piston 20 having two lands, is configured such that the transmission by the rapid feed cylinder 18 can be varied, and when the booster device is not faulty, the volume of the feed chamber 22 is moved by the stepped piston 20. acts as a master cylinder with a large effective diameter (e.g. 24 mm) and the booster fails or the rapid feed cylinder 18
When the master cylinder 3 is not in operation, the master cylinder 3 acts as a master cylinder having a relatively small diameter piston (for example, a piston with a diameter of 20 mm). This transmission change allows the vehicle to decelerate even after a booster failure (pedal travel distance increases), even if it acts like a master cylinder with a large diameter piston in the non-failure state. ).

The brake system shown in FIG.
It is different from what is shown in the figure.

Furthermore, the annular chamber 84 formed between the two lands or shoulders 95, 96 of the stepped piston 20 and the stepped bore 19 is connected to the brake line 36 via a pressure line with a shutoff valve 86. The braking force booster 31 is connected to
The directional control valve 8 is connected to the booster chamber 35 of the
8 from the position shown, the surface of the large diameter shoulder 96 of the stepped piston 20 acts to move the stepped piston 20 to the left due to the pressure in the booster chamber 35. When the direction control valve (large mouth valve) 88 is switched, the annular chamber 84 is connected to the pipe line 8.
It is connected to the booster W35 via 7, and is annular! The supply reservoir 97 connected to 184 is isolated from the booster chamber 35 . The directional control valve 99,100 and the directional control valve (inlet valve) 88 arranged in the brake line 36,37 can be actuated by a brake slip monitor and control electronics, which are not shown in detail. It is possible.

Reference numeral 82 in FIG. 2 designates an electric switch which is actuated via a sensing member 101 which abuts a small diameter shoulder 95 of the stepped piston 20 and which, in the event of a booster failure, Since the stepped piston 20 remains in its initial position (on the right side) even though the pedal 46 is depressed and moves the actuating rod 11, this switch indicates a failure of the booster 31 (e.g. a brake light, not shown in detail). preferred in that it operates in conjunction with a laser switch).

When the illustrated device is used as part of a brake device equipped with a slip tllIwJ device, when the wheels are temporarily locked, pressure fluid is transferred from the auxiliary pressure supply source 13 to the booster chamber 35, the directional control valve 88 and the pressure pipe. Road 33.86
．． 87 to the brake line 36.37, for which purpose the directional control valve 99.100 is simultaneously switched into the closed position. The valves required to reduce the pressure in the wheel brake cylinder and return pressure fluid into the supply reservoir 55 are not shown in detail.

According to FIG. 3, the housing of the braking force booster 5 further has an inner bore 50 in which a sliding member 51 for controlling the brake valve 6 is supported so as to be slidable in the axial direction. This control slide 51 is of substantially cylindrical design and has an axial bore 52 which is pressurized via a housing groove 53 and a radial bore 54 in the brake release position. The supply reservoir 106 is connected to

Therefore, atmospheric pressure is applied in the booster chamber 7, as in the brake release position of the hydraulic braking force booster.

Further, the control sliding member 51 has a radial groove 56, and when the control sliding member 51 is moved a predetermined distance, a housing groove 57 communicating with the pressure supply source 13 via the radial groove 56 opens. It becomes possible to connect to the booster chamber 7. This control sliding member is pressed in advance in the brake release direction by a compression spring 58.

At the left end of the control sliding member 51 in the drawing, there is a valve chamber 1.
14 is disposed, and this valve chamber 14 is connected to the housing groove 1.
12 and a return line 109 to the supply reservoir 106
communicate with. A through hole-shaped recess 119 with an enlarged diameter is provided on an extension of the inner hole 50, and a valve body 110 is held within this recess 119. This valve ball member 11 is attached to the axis of the control sliding member 51. Acts in conjunction with direction bore 52. The valve body 110 has a valve groove 118 , which connects the valve chamber 114 to the valve bore 120 and the housing groove 121 .

One end of a first louver 59 abuts against the end of the control sliding member 51 on the right side as viewed in FIG. Second lever 6
2 is connected to the second lever 59 via a rotational coupling 61, the upper end of this second lever as seen in the figure is supported stationary within the housing 1, and the lower end is slidable. It engages within the recess 122 of the member 9. This sliding member 9 is the sleeve 1
The compression spring 63 is clamped between the left-hand end of the sliding member 9 in the drawing and the sleeve 10.

The master cylinder piston 41 has a sealing sleeve 67
In the illustrated brake release position, a breathing hole 70 is provided adjacent to the front side of the sealing sleeve 67 in the operating direction, forming a connection to the actuating cylinder 26 of the master cylinder via the through hole 113. , interrupting hydraulic communication between the supply reservoir 106 and the actuation reservoir 26, which is not pressurized when the brakes are applied. The master cylinder piston 40 together with the housing 1 likewise surrounds an annular chamber 71 which is in constant communication with the unpressurized reservoir 55 via the housing groove 72 . A sealing sleeve 73 is also provided in the master cylinder piston 40, and the master cylinder piston 40 is
The breathing hole 74 can be closed when the master cylinder 3 is displaced, thus putting pressure on the actuating cylinder 27 of the master cylinder 3. The first return spring 76 is held between the bottom 75 of the cylinder bore 38 and the master cylinder piston 40. Similarly, the second return spring 77 is arranged between the two master cylinder pistons 40,41.

Booster chamber 7 is connected to pressure chamber 21 of quick-feed cylinder 8 via housing groove 121 and connecting line 116 . The supply chamber 22 formed by the small-diameter shoulder 95 of the stepped piston 20 and the left-hand part of the rapid supply cylinder 18 is connected to the working chamber 26 of the master cylinder 3 via a pressure line 105.
Alternatively, it is coupled to the working chamber 27.

Hereinafter, the operation mode of the brake device shown in the third factor will be explained in detail.

First, when the brake is released, all movable members occupy the positions shown. Booster chamber 7 of hydraulic booster
communicates with the pressureless supply reservoir 106 via the control slide 51, the housing groove 112 and the return line 123. Therefore, no force is acting on either the piston rod 8 or the booster piston 4, and the wheel brake 1 connected to the master cylinder 3
Atmospheric pressure acts on 4.15 and 16.17.

When the pedal force F acts on the brake pedal 46, the sliding member 9
moves to the left against the compression spring 63, thereby causing the second lever 62 to tilt clockwise about the stationary fulcrum 83 of the housing 1.

Booster piston 4 and master cylinder piston 4
0.41 and return spring 76
．． 77, the lower end of the louver 59 is initially subjected to a relatively strong reaction force. Therefore, the upper end of the lever 59 (as viewed in the figure) moves the brake valve control sliding member 51 to the left, which sliding member 51 first closes the housing groove 53 of the brake valve 6 and the booster chamber 7 is separated from the pressureless supply reservoir 106. When the pedal force acting on the brake pedal 46 increases, the control sliding member 5
1 moves further, and the housing groove 57 becomes the control sliding member 5.
It overlaps with the radial groove 56 of No. 1.

As a result, the pressure fluid flows into the booster chamber 7 from the pressure 1113, and the small diameter effective area of the sliding member 9 and the booster 4
Pressure acts on the

When the pressure in the booster chamber 7 of the hydraulic booster reaches a predetermined level, the booster piston 4 overcomes friction and starts moving the master cylinder piston 41 in the operating direction, and hydraulic pressure is formed in the operating chamber 26 of the master cylinder 3. This hydraulic pressure is applied to the wheel brake 1 via the brake pipe 29.
Delivered on 6.17.

When the booster is not out of order, the control pressure in the booster chamber is supplied to the pressure chamber 21 of the rapid feed cylinder 18 through the axial bore 52, the valve chamber 114, the valve body 11o1 housing groove 121, and the coupling pipe 116. , stepped piston 2
The effective diameter portion of the large-diameter shoulder portion 96 formed as described above allows the stepped piston 20 to move to the left against the pressing force of the elastic member 23 to drain the pressurized fluid in the supply chamber 22. The pressure fluid in the two working chambers 26, 27 is forced into the working chamber 26 from the pressure line 105 through the small diameter shoulder 95, so that when the brake is applied with the device in good condition, the pressure fluid in the two working chambers 26, 27 is Not only is it pressed by the cylinder piston 40.41 and supplied to the brake line 28.29, but also the supply chamber 22
Pressure fluid within is also supplied. Therefore, the pedal travel l is reduced by the amount of fluid supplied from the supply chamber to the brake line. At the same time, the booster chamber 7 is connected to the housing port 7
8, a connecting pipe 115, and a check valve 117 to the pressure chamber 21 of the rapid supply cylinder 18.

If the pressure in the booster chamber 7 drops to a predetermined level due to a failure of the pressure fluid source 13, the stepped piston will not move from its initial position on the right, and the pressure fluid in the supply chamber 22 will have no braking effect. .

The amount of liquid in the supply chamber 22 pressed by the stepped piston 20 is configured to be transmitted and changed by the rapid supply cylinder 18, and when the booster device is not malfunctioning, the master cylinder 3 has a large effective piston diameter ( For example 2
4 mm) and acts like a master cylinder with a relatively small diameter piston (for example 20 mm piston diameter) when the booster device fails and therefore the rapid feed cylinder 18 is not activated.

The above transmission change is such that the vehicle can be decelerated even after a booster failure (pedal travel distance increases).

In order to ensure safety in the event that the booster 5 breaks down during braking operation, the booster chamber 7 and A check valve 117 is disposed in a connecting pipe line that connects the pressure chamber 21 of the rapid supply cylinder 18, and includes a connecting pipe line 116, a housing groove 121, a valve hole 120, a valve chamber 114, an axial inner hole 52, and a radius. The connection connected to the booster 7 via the directional bore 54 is closed by the control slide 51 which is moved to the left by a pair of levers 59,62. That is, the valve ball member 11
1 closes the axial bore 52 and the control slide 51 closes the housing groove 112, so that the return line 109 is likewise closed.
is separated from the valve chamber 114.

[Brief explanation of the drawing]

FIG. 1 is a cross-sectional diagram showing a master cylinder and a braking force booster of a brake device according to one embodiment of the present invention, and FIG.
FIG. 3 is a diagram of a further embodiment of a braking system particularly suitable for use with slip control electronics; FIG. It is a diagram. 1... Housing, 2... Cylinder inner hole, 3, 30
... Master cylinder, 4,91 ... Booster piston, 5.31 ... Braking force booster, 6 ... Brake valve, 7.35 ... Booster chamber, 8 ... Piston rond, 9. ...Sliding member, 10...Sleeve, 13.
...Auxiliary pressure source, -14,15,16,17...Wheel brake, 18...Rapid supply valve, 19...Stepped inner hole, 20...Stepped piston, 21...Pressure Chamber, 22... Supply chamber, 23... Elastic member, 24.32
, 115, 116... Combined pipe line, 25.33, 85,
87,102゜105...Pressure pipe, 26.27.3
4... Working chamber, 28.29, 36.37... Brake pipe line, 40° 41.92... Master cylinder piston, 51... Control sliding member, 64.90... Tappet , 81°86.102...Shutoff valve, 95.96
...Step part, 101... Sensing member, 110... Valve body, 114... Valve chamber, 118... Valve groove, 120...
...Valve hole.

Claims (1)

[Claims] (1) A booster chamber (7, 35) that is coupled to the master cylinder (3, 30) and forms an auxiliary pressure proportional to the booster piston (4, 91) and the pedal depression force (F); a braking pressure booster (5, 31) having an auxiliary pressure supply mechanism (13);
) and a wheel brake (14, 15, 16, 17) coupled to a master cylinder (3, 30), the hydraulic brake device comprising a rapid supply cylinder (18), the rapid supply cylinder A stepped piston (20) having two lands is slidably supported, and a pressure chamber (21) is disposed on the side of a large-diameter land (96) and a small-diameter land (95). A supply chamber (22) disposed on the side and the stepped piston (22)
0) in the direction of the pressure chamber (21)
and a stepped inner hole (19) having said pressure chamber (
21) communicates with the booster chamber (7, 35) via the coupling line (24, 80, 32), and the supply chamber (22) communicates with the master cylinder (3, 3) via the pressure line (25, 33). 30
) and one of the working chambers (26, 34) and the brake pipe (28
, 29, 36, 37). (2) A stepped piston having the two land portions (2)
0) is held and guided in the housing of the quick-feeding cylinder (18) and cooperates with a sensing member (101) forming part of the electrical switch (82). Hydraulic brake equipment. (3) The two land portions of the stepped piston (20) (
An annular chamber (84) formed by a stepped inner hole (19) and a stepped inner hole (19) communicates with the booster chamber (35) via a pressure line (85, 87); , 87) is provided with a multi-way control valve (88) acting as an inlet valve, the second switching position of which connects said annular chamber (84) to the supply reservoir (97). A hydraulic brake device according to claim 1. (4) The two land portions of the stepped piston (20) (
An annular chamber (84) formed by the stepped inner bore (19) of the rapid feed cylinder (18) is connected to the brake line (36) via the pressure line (85, 33, 102).
, 37), and the hydraulic brake device according to any one of claims 1 to 3, which communicates with the cutoff valve (86, 103) inserted in the pressure pipe (33, 102). . (5) An elastic member (23) is disposed, which is formed by a small-diameter land portion (95) and a stepped inner hole (19) of the rapid supply cylinder (18), and acts on the stepped piston (20). Claim 1, wherein the supply chamber (22) is connected to one brake line (37) via a pressure line (33).
The hydraulic brake device according to any one of items 4 to 4. (6) Multi-directional control valves (99, 100) are disposed in the brake pipes (36, 37), and the multi-directional control valves (99, 100) are arranged in the brake pipes (36, 37).
9, 100) is the master cylinder (30) in the first switching position.
communicates pressurized fluid from the working chamber (27, 34) to the wheel cylinder of the wheel brake, and in a second switching position blocks the communication of pressurized fluid between the working chamber (27, 34) and the wheel brake, and A hydraulic brake device according to any one of claims 1 to 5, wherein fluid from the wheel brake can be communicated and returned to the working chamber (27, 34). (7) The multi-directional control valves (88, 99, 100) are switched by an electronic mechanism that monitors slip;
For this purpose, the hydraulic brake device according to any one of claims 1 to 6, wherein the directional control valve is formed as an electrically operated valve. (8) The two land portions of the stepped piston (20) (
95, 96) and the stepped inner bore (19) of the rapid feed cylinder (18).
Hydraulic brake device according to any one of claims 1 to 7, which is connected to the supply reservoir (55) via a supply reservoir (55). (9) Pedal actuation that is connected to the master cylinder (3) and consists of a booster piston (4) and a booster chamber (7) that forms an auxiliary pressure proportional to the pedal depression force (F) via the brake valve (6). a braking force booster (5), a pressure fluid source (13) and wheel brakes (14, 15, 16, 17) connected to the master cylinder (3) and a stepped piston (20) provided with two lands. ) and a pressure chamber (21) and a small-diameter land (95) disposed on the side of the large-diameter land (96) of the piston.
A stepped inner hole (with a supply chamber (22) arranged on the side)
19), the supply chamber (22) being connected to one working chamber (26 or 27) of the master cylinder (3) and the brake line (28, 29).
A hydraulic brake device coupled to one or both of the booster chamber (7) and the pressure chamber (21) of the rapid supply cylinder (18).
A check valve (117) is inserted into the brake valve (6).
Hydraulic brake device, characterized in that the control sliding member (51) of ) cooperates with a valve body (110) which communicates with the pressure chamber (21) via this brake valve (6). (10) The rapid supply cylinder (18) has a valve chamber (114).
), a mechanically actuated multi-directional control valve is inserted in the pressure fluid line connecting the brake valve (6), and the actuating member of this valve is combined with the control sliding member (51) of the brake valve (6). Hydraulic brake device according to scope item 9. (11) From the booster chamber (7) to the rapid supply cylinder (
The valve body (110) that controls the flow of pressurized fluid to the pressure chamber (21) of 18) moves a valve member such as a valve pole member (111) at an end proximate to the control sliding member (51). However, this valve ball member opens or closes the axial inner hole (52) of the control sliding member (51) and can slide within the inner hole (50) of the housing (1) depending on its position. A hydraulic brake device according to claim 9. (12) A valve body (11) that controls the flow of the pressure fluid
0) is provided with a valve hole (120) that communicates with a coupling line (116) connected to the rapid supply cylinder (18), and this valve hole communicates with the valve body (110) via a valve groove (118). A valve chamber (114) formed between the control slide (51) and the inner bore (50) communicates with the supply reservoir (106) through a groove (112) in the housing. A hydraulic brake device according to claim 9 or 11. (13) Valve ball member (11) of the valve body (110)
1) is an axial bore (52) of a control sliding member (51) longitudinally slidably supported within the housing (1);
a valve groove (118) held concentrically to and connecting the valve chamber (114) to the valve bore (120) of the valve body (110);
is the valve chamber (114) outside the area of the valve ball member (111).
) Claims 9, 11 and 1 ending in
The hydraulic brake device according to any one of Item 2. (14) Valve hole (120) of the control sliding member (51)
a recess (119) formed within the housing of the booster (5) and a valve body (110) having a valve member (110) and a valve groove (118); is held within the recess (119) and the inner hole (50)
at least one valve hole (120
), and communicates with the valve groove (118), and communicates with the valve hole (
81) is a hydraulic brake according to any one of claims 9 to 13, which communicates with the housing groove (121) connected to the pressure chamber (21) via the connection pipe (116). Device.