JPS60176859A - Hydraulic booster - Google Patents

Abstract

PURPOSE:To improve actuation efficiency, by forming a movable valve body of a valve gear for feeding or discharging a pressure fluid, into being columniform while fitting the tip end in a convavity formed in a power piston via a sealing member. CONSTITUTION:A stepped hole 94 is formed in the rear of a first piston 19 in an axial direction, while a movable valve body 97 is slidably inserted in position over a medium diametral hole part 95 and a large diametral hole part 96 of the stepped hole 95. The movable valve body 97 is formed into being columniform, and its front end is fitted in the medium diametral hole part 95 via a seal ring 99. With the movable valve body 97 formed into being columniform, an area of the front end of the movable valve body 97 is able to be almost equal to a seating area on an inner flange part 104a of a sleeve 104 at an annular projection part 97a of the valve body 97. Accordingly, such force that the annular projection part 97a presses the inner flange part 104 becomes smaller so that force to open a feed valve is constituted to be small, thus braking operation comes speedy.

Description

DETAILED DESCRIPTION OF THE INVENTION The present invention relates to a hydraulic booster that fully assists the operation of a brake or clutch mask cylinder of a vehicle or the like.

Conventionally, this kind of device has a main body with a cylinder hole formed entirely, a piston slidably inserted into the cylinder hole, and a pressure source formed on the side of the piston and connected to a pressure source for supplying pressurized liquid. an input chamber, a pressure chamber formed at the rear of the piston, a recess connected to the input chamber and the pressure chamber and provided at the rear side of the piston, a valve device provided in the recess, and the valve. It is equipped with an input shaft on which the device is arranged so that it can be operated,
The valve device includes a movable valve body slidably inserted into the recess, a valve seat formed on the rear side wall of the recess opposite to the movable valve body, and the movable valve seat so as to be seated on the valve seat. It is known that the movable valve body has a valve spring that biases the entire body rearward, and that the front side of the valve seat is connected to the input chamber and the rear side is connected to the pressure chamber, and further, the movable valve body is made of steel. It is known as a ball.

However, in such conventional valves, the movable valve body receives all the pressure in the input chamber over a large area, which increases the operating force required to open the valve at the start of operation, increases the operating resistance, and reduces the speed of operation. has the problem of reduced efficiency.

The present invention has been made in view of the above problems, and an object of the present invention is to provide a hydraulic booster with improved operating efficiency. According to the present invention, this object is achieved by moving the movable valve body in the above configuration to
This is achieved by a hydraulic booster having a columnar shape, the front end of which is fitted into the recess through a sealing member.

DESCRIPTION OF THE PREFERRED EMBODIMENTS Hereinafter, a mask cylinder with a brake hydraulic booster according to an embodiment of the present invention will be described with reference to all the drawings.

In the figure, the master cylinder with a hydraulic booster of this embodiment is shown as a whole by (1), and its cylinder body (2
) A mask cylinder section (3) is provided on the left side, and a booster section (4) is provided on the right side. Cylinder body (
A stepped hole (5) is formed in 2), the front end is a closed end, and the rear end opening is closed by a lid (6). The lid body (6) is fixed to the cylinder body (2) by a plurality of bolts (4) with the entirety of the sea (3) and cylinder (7) interposed therebetween, and this hydraulic booster is attached to the toe board (not shown) by the same bolts (to). The entire master cylinder with device (1) is fixed.

A shaft-shaped input member (9) with a cup seal 0η attached to the rear end is slidably fitted into the center through hole (8) of the lid body (6), and the input member (9) is inserted into the central through hole (8) by the spring 00. is energized by

(In this specification, the front means the left side in the figure,
Rear shall mean to the right. ) Furthermore, the tip of the rond part 0 of the connecting member (2) connected to the brake pedal (not shown) is received in the recess (a) formed at the rear end of the input member (9), and the rubber The material (15a) prevents the material from being removed. A boot α→ is fixed between the rod part α and the lid (6) to prevent dust.

The stepped hole (5) of the cylinder body (2) is made up of a large diameter hole section α and a small diameter hole section. A second piston (E) is slidably fitted into the small diameter hole (C). The first piston α has a first large diameter part (211) and a second large diameter part (211) at the rear end, middle part and (4) front end, respectively.
21 (having the same diameter as the first large diameter part + 213) and a small diameter part (C), and is equipped with a cup seal (241 (25 + 261). Thus, the second large diameter part (221) and the small diameter part (
An auxiliary pressure chamber (2 forces) is formed between the second large diameter section (22) and the first large diameter section (21+), and an accumulator royal chamber (28) is formed between the second large diameter section (22) and the first large diameter section (21+). First large diameter section CD
A boosting pressure chamber (c) is formed between and the lid (6). Of these auxiliary pressure chambers (271, accumulator pressure chamber and booster pressure chamber (2ω), only auxiliary pressure chamber (2) belongs to the mask cylinder part (3), and this pressure chamber (29) The front half of the first piston 09 belongs to the mask cylinder section (3), and the details of this mask cylinder section (3) will be explained below.

A bolt (311) is screwed onto the front end of the first piston α, and a ring-shaped spring plate (311) is engaged with the head of this bolt 6υ, and a ring-shaped spring plate is engaged on the shaft. Receiving (32
1 is fitted, and a spring member is stretched between these spring receivers (32 (331) in a compressed state, and the spring receivers (all three The small diameter part (23) as a head formed at the front end of the first piston 4 is in contact with the above-mentioned cup seal (2), and the other A cup seal is also installed on the large diameter part (to) of the rear end of the second piston, so that the first piston 4 and the second piston (e)
A first hydraulic pressure generating chamber (41) is formed between the two.

In addition, a through hole is formed in the small diameter part (c) located behind the cup seal (to) and near the first piston α, so that the hydraulic pressure in the auxiliary pressure chamber (8) is transferred to the first hydraulic pressure generation chamber (c). When the hydraulic pressure is higher than the hydraulic pressure in the first hydraulic pressure generating chamber (41), the lip portion of the cup seal (26) is fully opened through the 20th through hole (301″fc) and the hydraulic fluid flows into the first hydraulic pressure generating chamber (41). has been done.1st
The hydraulic fluid does not flow from the liquid king generation chamber (41) into the auxiliary pressure chamber (27) through the through hole (301-). That is,
A check valve is constituted by the lip portion of the cup seal (to) and the portion where the through hole (to) of the small diameter portion (c) of the first piston α is formed.

A cup seal clη is also attached to the large diameter portion 51 at the front end of the second piston (corporate), which creates a pressureless chamber between the large diameter portion at the front end (c) and the large diameter portion at the rear end ((4). (31 is formed, and a second hydraulic pressure generating chamber (4υ) is formed between this piston (A) and the bottom wall of the cylinder body (2). The second piston (1) is located at its front end. The return spring (4) stretched between the fitting spring rest (4) and the bottom wall of the cylinder body (2)
It is biased to the right by four. Although not shown, an output port is formed in the cylinder body (2) so as to communicate with each of the first hydraulic pressure generating chamber (41) and the second hydraulic pressure generating chamber (41), and each of these is connected to a pipe line ( 44) (431, later-described first solenoid valves (110) (112), second solenoid* (11
1) (1, 13) Full valves are connected to the wheel cylinder (46a) of the rear wheel (46) and the wheel cylinder (45a) of the front wheel (4 (g)).
Although only one of each of 46) is shown, it is assumed that the other front wheel and rear wheel have a similar configuration.

A check valve similar to that described above is also provided between the second hydraulic pressure generating chamber (41) and the no-pressure chamber (31). A through hole (4) is formed in the front large diameter part +39 of the piston (7), and if the liquid pressure of the pressureless chamber (3 liters) is higher than the second hydraulic pressure generating chamber (the current liquid pressure, The liquid passes through this hole (43') and the cup seal c3
The lip part of η is fully opened so that the liquid flows into the second pressure generation chamber (4υ).
From 4υ to (7) Through holes (the working fluid does not flow into the no-pressure chamber opening through the four holes. In other words, the through hole of the cup seal (lip part of 261 and large front part a5 of second piston α0) (The portion where 43 is formed constitutes a check valve.

A boss portion 61 is attached to the earth wall at the front end of the cylinder body (2).
) is formed, and the liquid restricting hole 621 communicates with the second hydraulic pressure generation chamber (4υ through the return hole (501') when the brake shown in the figure is not in operation, and the liquid through the supply hole (4υ). It is in constant communication with the liquid flow restrictor (53).
The cylindrical part (551) of the reservoir joint (Incorporated) is press-fitted through the grommet seal (53)'i, and the fixing member (
581 and the grommet seal (581), and the screws (5 (5)
By fixing the reservoir joint (54) with
is fixed to the cylinder body (2).

A rubber tube is connected to the rubber tube connection portion (G) of the reservoir joint 64J as shown by the dotted line, and communicates with the reservoir shown by the dot (57).

A boss part (67J) higher than the above-mentioned boss part 51) is formed on the earthen wall in the middle part of the cylinder body (2), and the lower part of the liquid (8) connecting hole is shown in detail in Fig. 2. A double-valve device (
64) is provided, and the lower bottom hole (651 is in communication with the first hydraulic pressure generation chamber (4G) via the return hole (61J), and is always in communication with the auxiliary pressure chamber (4G) via the supply hole (601). It's communicating.

In addition, a grommet seal (
661 to the reservoir joint (6η cylindrical part (the decoy is press-fitted), and the above-mentioned fixing member marked 5 and the grommet seal (6
6) ,! : The 2 langes s are interposed between them, and the fixing member 6 is fixed to the downward protrusion (58a) and the lateral protrusion (51a) of the boss part (52) with screws (5 (support)). yp reservoir joint (6η is the cylinder body (2
) is adhered to. That is, the fixing member is a common fixing means for both reservoir joints (54) (6η).A rubber tube is connected to the rubber tube connection part of the reservoir joint (6η) as shown by the dotted line, It communicates with the reservoir indicated by the inner hole (7
α is shown, but the other reservoir joint (541) has a similar shape and has a similar upper end of the inner hole. ) a plurality of protrusions (71) as shown in FIG.
are formed, and by engaging with the plurality of recesses of the fixing member portion, both reservoir joints t541 (6η) are firmly fixed to the cylinder body (2).

Next, the multiple valve device (6) located at the bottom of the boss (6)
The details of 4) will be explained with reference to FIG.

This valve device (6th part consists of a first valve part (731) and a second valve part (731), these valve parts (73) are common to the valve body (7). The spring catcher (candle is fitted on the outer edge), the spring catcher (stop ring (8) that engages with the layer, and the lower tapered part (64a) of the valve body (T4J)
The valve device (64
The whole of 1 is fixed to the liquid throttle hole (6 The ball valve σe is seated on the valve seat (74C) formed in the valve body σ.The ball valve ffe is seated on the valve seat (74C) formed in the valve body σ. The valve seat (74c) is biased by a leaf spring ση stretched over the valve body (74c).A first through hole (74a) is formed in the center of the valve body (74a). is the bottom hole portion (as the second valve chamber) formed below the valve body (7IO).
65, and in the normal state shown, the ball valve (7
6) The communication with the first valve chamber (79) is cut off by the heart.

A plurality of second passage holes (74b) are further formed around the first passage hole (74a) in the valve body σa, and these communicate with the first valve chamber σ, and usually the valve body σ Communication with the bottom hole (65) serving as the second valve chamber is blocked by a rubber valve member (65) fixed to the lower end of the valve chamber. As described above, the first valve part σ water is a ball valve (7υ1 valve body Cl4), a valve seat (
740), a leaf spring (77), and a second
The valve part σ is composed of a valve body (?→) and a rubber valve member @D.

The first valve chamber opens with a spring receiver (center opening (78a) of 78).
The bottom hole (65) serving as the second valve chamber is connected to the cylinder body (2) through the return hole (60) and the supply hole (60) as described above. It communicates with the inside of the cylinder hole.A throttle groove (74d) is formed in the lower end peripheral edge of the valve body (74), and
The bottom hole (65) serving as the second valve chamber is the throttle groove (74d).
) and the second through hole (74b) '! There is constant communication through the.

When the pressure in the bottom hole portion (as the second valve chamber) becomes higher than the pressure in the first valve chamber (79) by a predetermined value or more, the first valve portion (721) opens and the bottom hole portion (as the second valve chamber) ( 6 and the first valve chamber (flying). This valve opening pressure is determined by the strength of the plate spring (7η) and the seating area of the ball valve (76) relative to the valve seat (7→). In addition, the opening pressure of the second valve part (73) is sufficiently small, and the pressure of the bottom hole part (65) as the second valve chamber is higher than a predetermined value than the pressure of the first valve chamber (73) communicating with the reservoir. The valve is configured to open when it becomes smaller, that is, when the bottom hole (651) serving as the second valve chamber becomes negative pressure.

Next, details of the booster section (4) will be explained with reference to FIG. 1 again.

The first piston Ql is also one of the main components of the booster section (4), and is located above the above-mentioned accumulator royal example formed on the rear and side circumferences of the first piston Ql, and is attached to the cylinder body (2). is formed with a boss end, and a connecting member (goods) is attached to this.
is screwed on. There is a ball valve (c) and a valve flap (8) inside the boss section.
A reversal valve consisting of 6) is disposed, and the direction from the upper side to the lower side is all forward direction, and the η side of the conduit connected to the connecting member S4) through the through holes (83a) and 83f is an example of an accumulator pressure chamber. It is possible to communicate with. An accumulator (881) is connected to the conduit η, and the conduit (89) and check ff (9
0)? A discharge port of a hydraulic pump (91) is connected through r. The check valve (90) has a forward direction from the discharge port side of the hydraulic pump (91J to the pipe @η side.The hydraulic pump (9υ) is driven by a motor (9υ),
Its inlet is connected to a reservoir (57), shown as a dot, via a conduit (93) k, shown in dotted lines. That is, the reservoir 6η functions as a common reservoir of hydraulic fluid for the above-mentioned mask cylinder section (3) and booster section (4). Furthermore, as will be described later, the anti-skid arrangement W m (
130).

A stepped hole (84) is formed in the axial direction at the rear of the first piston, and a movable valve body (97) is slidably inserted into this medium diameter hole (9!9) and large diameter hole (961). The front end is fitted into the medium diameter hole (()) through the seal ring (99, 1').The small diameter hole (121) at the front end of the stepped hole (94) is It communicates with the auxiliary pressure chamber □□□ via the axial passage hole (122).
) and the step between the small diameter hole (121) and the medium diameter hole (E) of the stepped hole (94).
), and the movable valve body (97) is formed with a through hole (97c) that is aligned and communicates with the small diameter hole (121) of the stepped hole (94) in the axial direction. A spring receiving ring (96) is disposed in contact with the stepped part between the medium diameter hole ((g)) and the large diameter hole (96) of the stepped hole (H), A valve spring (2) is stretched between the annular protrusion (gya) formed on the outer periphery of the movable valve body (971') and urges the movable valve body (971' rearward).

A sleeve (104) is attached to a seal ring (103)' and fitted into the rear end opening of the stepped hole ((b) of the first piston α. The rear end of the movable valve body (part) fits into the inner hole of the sleeve (104) and is slidable.
(106) '(rThe attached rear end surface is an annular projection (107) formed on the front end surface of the input member (9).
and are opposed to each other at a predetermined distance when the illustrated device is not in operation. That is, the movable valve body (97) has its annular protrusion (97a) in contact with the inner flange (104a) formed at the front end of the sleeve (104), thereby increasing its relative position with respect to the first piston α1. The rear position is regulated.

In the large diameter hole (961) of the stepped hole (94), an input chamber a is formed around the middle part of the movable valve body (9D), which is connected to the through hole (1) formed in the first piston (1). 101) All valves are in constant communication with the accumulator chamber. Also, a communication gb is formed around the rear end of the movable valve body (9η) within the sleeve (104), which is connected to the movable valve body (97).
A groove (97b) on the outer periphery of the rear end and a groove (109) on the outer periphery of the front end of the input member (9).
1 is in constant communication. The annular projection (97a) of the movable valve body (97) and the inner flange (1) of the sleeve (104)
04a) constitutes a supply valve, which is closed in the illustrated state, but when opened, the input chamber a and the communication chamber b1, that is, the boosting pressure chamber wall are communicated with each other. In addition, a movable valve body (9D
A discharge valve is constituted by the rubber sheet (106) on the rear end surface and the annular projection (107) on the front end of the input member (9), and in the illustrated state, it is open and the axial hole (
97c) and the small diameter hole (121) of the stepped hole (94) of the first piston α, the radial through hole (122) and the auxiliary pressure chamber c'ni to the reservoir side and the boosting pressure chamber (2 ) side, but when this is closed, the communication between them is cut off.The input member (9) is connected to the spring O as described above.
Although the sleeve (104
) is regulated from its rear position by a stopper (108) fixed to the rear end opening.

Next, the anti-skid piping section (130) connected by piping between the master cylinder with hydraulic booster (1) configured as above and the front wheels (four, rear wheels (46)) will be explained. .

The second hydraulic pressure generation chamber (4D1 first
Fluid pressure generation chamber (40 is each pipe line + 43) t44)
All valves are connected to first solenoid valves (110) (112). This first solenoid valve (110) (112) and the front wheel (451
, wheel cylinders (45a) (46a) of the rear wheels (46)
) A second solenoid valve (111) (113) is connected between the two solenoid valves (111) and (113). In addition, a check valve (118) is installed in the conduit connecting the first solenoid valve (110
) (119) A third electric throttle valve (117) is connected via pipes (123) and (124). The inlet of the third electromagnetic valve (117) is connected to the pressure chamber (29) of the booster section (4) via a conduit (120)'. In addition, the second solenoid valve (11
1) (113) are respectively connected to the fourth solenoid valve (114).
X115), reservoir (57) via conduit (116)
connected to.

First, second, third and fourth solenoid valves (110) (112)
, (111) (113), (117), (114) (1
15) is a 2-position solenoid valve with each solenoid (110
a) (112a), (111aX113a), (117
a), (114, a) and (115a) are excited, but depending on whether they are excited or not, two purple states can be taken.

Even if not shown, each output terminal of the amplifier skid control circuit is connected to a solenoid (110a) (112a) (111a) (11
3a) (117a) (114a) (]15a), each solenoid is energized by the output '1#,
Each solenoid is not energized with an output of 0''.The anti-skid control circuit determines the skid status of the wheels based on the wheel speed detection signal of the wheel speed sensor attached to the front wheels (451 and rear wheels (46)). and determines whether the brake should be applied, released, or held constant. Depending on this decision, a 1" or 0# lick output is selectively generated at each output terminal.

The first solenoid 9F (110) (112) and the fourth solenoid valve (,
115) is a so-called "on-off" type valve, and when the solenoids (110a, 112a, and 115a) are not energized, it assumes the A state shown in the figure, and the inlet and outlet are in communication. .

Further, when the solenoid (noaXu2a) (nsa) is energized, it enters the B state 9, and the inlet and outlet are out of communication.

Second solenoid valve (111X113) and third solenoid valve (117
) is a so-called "3-boat valve", which has both a passenger exit and a Japanese exit, with respective solenoids (111a) (113a),
When (117a) is not excited, the states shown in C and E are taken. That is, in the second solenoid valve (111X113), the first solenoid valve (110) (112) side and the front and rear wheels (4!i
The wheel cylinders (45a) (46a) of F46) are placed in communication, and in the third solenoid valve (117), the check valve (118) (119) side and the reservoir θη side are placed in communication. is the inlet and outlet, that is, the tube wI (12
0) side and the check valve (118x119) side are in a non-communicating state. Solenoid (lla) (113a
) is excited, the second solenoid valves (111) (113)
In this case, the inlet and outlet are blocked, but the outlet and outlet are in communication. In other words, the wheel cylinders (45a, 46a) of the front and rear wheels (461) communicate with the fourth solenoid valves (114, 115).Also, when the solenoid (117a) is energized, Third solenoid valve (
117) changes the state of F and puts the inlet and outlet in communication.

In other words, the check valve (118 x 119) side and the pipe line (120
) side are communicated. In addition, the check valve (118) (1
19) is the entire forward direction from the third solenoid valve (118X119) side to the pipeline side between the eleventh and second solenoid valves (110), (112), and (111X113).

The tandem master cylinder with a hydraulic booster according to the embodiment of the present invention is constructed as described above.
Explain the effects etc.

When the brake is not activated, each part is in the state shown.

When the driver depresses a brake pedal (not shown) in this state, the connecting member (2) moves forward and pushes the input member (9). An annular projection (107) at the tip of the input member (9) is seated on a rubber sheet (106) at the tip of the movable valve body. That is, the discharge valve is closed and the pressure chamber (21) and the reservoir side are in a state of no communication. When the input member (9) moves further forward, the movable valve body (97) releases the valve spring and the rubber ring (
102) relative to the first piston (6), and its annular protrusion (97a) is separated from the inner flange (104a) of the sleeve (104). . That is, the supply valve opens, and the pressure liquid flows from the input chamber a through the groove (97b) on the outer periphery of the communication chamber b1, the movable valve body (97), and the groove (109) on the outer periphery of the input member (9), and flows into the pressure chamber (
2. Flowing into Kuuchi. As a result, the first piston a9 receives hydraulic pressure at the right end surface of its first large diameter portion QD, and a leftward movement force is generated. It is assumed that when the vehicle starts running or when the brakes start operating, the motors (9 motors) are driven and the hydraulic pump (91)' is operated. This is the accumulator royal (28) through the sphere ff (851)
Supplied within. Input chamber a has a through hole (101)'
Pressure from the accumulator royal family (to) is constantly applied via Ik.

As the first piston Ql moves forward, the input member (9) also moves forward, and the discharge valve remains closed. Cup seal CI attached to the small diameter part of the first piston 4! 61 is the return hole (
When all 61 passes, the first hydraulic pressure is generated, W (4G is sealed against the reservoir side, but in order to compensate for the fluid loss on the wheel cylinder side, the first hydraulic pressure is generated (the pressure of 4G is At the beginning, there is almost no increase.

On the other hand, the pressure in the auxiliary pressure chamber (2) increases as the first piston 01 moves forward, and the pressure in the auxiliary pressure chamber (2) and the first hydraulic pressure generation chamber (
Due to the pressure difference between the first piston 4 (231 flows into.

This rapidly compensates for the fluid loss on the wheel cylinder side connected to the output port of the first fluid pressure generating chamber (4G).

When the pressure inside the auxiliary pressure chamber (side) reaches the opening pressure of the first valve part (7), the hydraulic fluid in the auxiliary pressure chamber (towards the second valve) is
Bottom hole part as valve chamber, through hole (74a), ball valve (7G
It is guided to the reservoir side through the gap between the valve seat (74C) and the first valve chamber CI mark. When the first piston α field further advances, the fluid loss on the wheel cylinder side has already been compensated for, so the pressure on the first fluid pressure generation chamber (411, that is, the wheel cylinder side connected to this) increases rapidly. (E) also moves forward together with the first piston 4, but after the first piston 4 moves forward slightly, the first hydraulic pressure generating chamber t4 (I
As the pressure inside starts to rise rapidly, the pressure difference between the front and rear of the second piston head is also added, and the first piston moves forward rapidly as the first piston tilts, compensating for the fluid loss on the wheel cylinder side and increasing the pressure in the first fluid pressure generating chamber (41 Almost simultaneously, the pressure in the second hydraulic pressure generation chamber (41) began to rise rapidly, and the pressure in the first and second hydraulic pressure generation chambers (4QC
The hydraulic pressure of 41) increases equally. In this way, the desired brake can be applied to the vehicle.

When the desired brake is applied, the input member (9
) through the connecting member 0■ and the force exerted on the input member (9) by the hydraulic pressure Pa introduced into the pressure chamber (2α) match approximately 9, and the resulting hydraulic pressure Pa becomes 1 piston (1
00 Force exerted on the right end face and generated hydraulic pressure P in the first hydraulic pressure generating chamber
The force that i exerts on the left end surface of the first piston α is balanced, the first piston a9 stops, and the supply valve also closes. That is, the annular protrusion (97) of the movable valve body (97)
a) is the inner two flange portions (104a) of the sleeve (104).
), the above-mentioned constant hydraulic pressure Pa is introduced into the pressure chamber (291).

That is, in the above balanced state, the following equation holds true.

F = Pa (S, -8,) ・・・・・・・・・
・・・・・・・・・・・・・・・(υPm X 8m=
Th X 83 ・・・・・・・・・・・・・・・・・・
・・・・・・・・・(2) Here, 8a is the cross-sectional area of the large diameter portion (9a) at the rear end of the input member (9), and S is the annular area ( 107) Gomshi) (106)
The seating area, Sm, is the small diameter part of the first piston α (2
3) and Sa are (the cross-sectional area S-8 of the large-diameter hole αη into which the first large-diameter portion (2]l of the first piston α9 fits);
)'(r shall be represented respectively.

From equations (1) and (2) above, Therefore, the following equation holds.

PmS S g Pm' 84-8m It is clear from the figure that 8)S, so it can be seen that the power has been doubled.

When the driver returns the brake pedal to the 7th position to release the brake, the input member (9) moves back to the right under the full force of the liquid m in the pressure chamber (2 (g)) and the spring force of the splash (10). This causes the annular projection (107) at the tip to separate from the rubber seal (106) of the movable valve body (97).In other words, the combined valve opens.The pressure fluid in the pressure chamber (29) is transferred to the tip of the input member (9). groove (109) on the outer periphery of the
7c) and the radial through hole (122) to flow into the auxiliary pressure chamber (2'D).

As the pressure in the pressure chamber Cj decreases, the pressure in the first hydraulic pressure generation chamber (4Q
The first piston 1.1 and the second piston (E) begin to move back to the right under the hydraulic pressure of 1.1 and the spring force of the return spring (47). The pressure in the auxiliary pressure chamber 07) tends to become negative due to the backward movement of the first piston α, but this is compensated by the pressure droplet and the inflow of hydraulic fluid from the reservoir (57). On the other hand, the first hydraulic pressure generating chamber (41) also tries to become negative pressure, but the hydraulic fluid that has flowed into the auxiliary pressure chamber (2η) partially flows through the through hole of the small diameter part (c) of the first piston 4.
□h11 The outer edge of the cup seal Q section is bent and flows into the first hydraulic pressure generation chamber (41. Therefore, the negative pressure is fully compensated. The second hydraulic pressure generation chamber (4υ also tries to become negative pressure, but This room (
There is a supply hole (49) in the 4υ, a through hole (351) in the large diameter part of the second piston (421k way, cup seal cl
By bending the outer edge of D, hydraulic fluid flows in from the reservoir side. Therefore, the negative pressure is fully compensated. After the pressure in the pressure chamber t29) becomes zero and the second valve part (7 east) closes, the throttle groove (74
d) The working fluid gradually flows into the auxiliary pressure chamber (2) through the entire passage, thus causing the auxiliary pressure secondary first hydraulic pressure generation chamber (41 and the second
The pressure in the hydraulic pressure generation chamber (4υ is zero, and each part reaches the state shown in the figure. Note that the throttle groove (74d) is connected to the first valve part (721) and the second valve part (731 are closed). Sometimes an auxiliary pressure chamber (
2) The working fluid inside also functions to fully compensate for changes in volume due to temperature changes.

The above example assumes that the vehicle is driving on a road with a normal coefficient of friction and the brake pedal is depressed appropriately, but if the vehicle is driving on a road with a low coefficient of friction, such as an icy slope, the brakes are applied suddenly and the wheels are pressed down. In this embodiment, if there is a possibility that the vehicle may become locked, all anti-skid control is performed.

That is, by depressing the brake pedal 1, the hydraulic pressure generation chamber (4
1 (before the fluid pressure of 4υ reaches a certain value according to the input F,
Loosening the brake, holding the foot down, and applying the brake are repeated over and over again.

When the anti-skid control circuit (not shown) determines that the brake is applied too much, the first solenoid valve (110) (112)
and the solenoid (1) of the second solenoid valve (111) (113)
10a) to (113a) are excited. It should be noted that anti-skid control may be performed on each of the four wheels individually, but for the sake of clarity, it is assumed that all wheels (45) and t46) are in the same skid state and are subjected to anti-skid control in the same way.

The first solenoid valve (110) (112) and the second solenoid valve (11
1X113) now assumes states B and D. Solenoids (114) of other solenoid valves (114) (115) (117)
a) (115a) and (117a) are not excited, so they remain in the states of A and E shown in the figure.

Wheel cylinder (45a) of wheel (451 (46)) (
46a) is communicated with the reservoir 57) side, but is not communicated with the hydraulic pressure generation chamber (41 (4υ) side of the mask cylinder part (3).The pressure liquid of the wheel cylinder (45aX46a) is communicated with the reservoir (57) side. This releases the brake.

When it is determined that the over-applied brake has been released, the solenoids (114a) (1) of the fourth solenoid valves (114) (115)
15a) is excited. Take state money from A to B. First,
The second solenoid valves (110) to (113) remain energized.

As a result, the current hydraulic pressure is contained within the shift wheel cylinder (45aX46a). In other words, the braking force is held constant.

When it is determined that the wheel speed has sufficiently recovered, the third solenoid valve (
117) solenoid (117) is energized, E to F
state? Take. The solenoid (110a) (112) of the first solenoid valve (noXn2) remains energized, but the solenoid (lla) (112) of the second solenoid valve (1n) [3]
13a) and the solenoids (114a) (115a) of the fourth solenoid valve (114X115) are demagnetized. Accordingly, the wheel cylinder (45aX46a) is connected to the reservoir (5
Liquid pressure generation chamber (4t1) on the η side and mask cylinder part (3)
(Although it is not in communication with the 1 side, the third solenoid valve (117), check valve (118X119), and second solenoid valve (111X11
3) It is in communication with the pressure chamber (c) of the booster section (4) via k. As a result, pressure fluid flows into the wheel cylinders (45a) (46a) from the pressure chamber 0ω, and the braking force increases again.

When the anti-skid control circuit determines that the brake is applied too much, the solenoid (11) of the third solenoid valve (117)
7) is demagnetized, and the solenoid (lla) (113a) of the second solenoid valve (111) (113) is energized. 1st
Solenoid (110a) of solenoid valve (110X112) (
112a) remains energized. Wheel cylinder (45aX46a) l'1 4th solenoid valve (114) (1
15) Fully open the valves to communicate with the reservoir 57), and pressurized fluid is discharged from the wheel cylinders (45a) and (46a) to the reservoir 67). This releases the brakes.

When it is determined that the over-stressing of the brakes has been released, the fourth
Solenoid (114a) of solenoid valve (114X115) (
115a) is excited, and the wheel cylinder (45a) (
46a) is also cut off from the reservoir 67) side, and the braking force is kept constant.

When it is determined that the wheel speed has sufficiently recovered, the third solenoid valve (
The solenoid (117a) of the brake booster (4) is energized, pressure fluid is supplied from the pressure chamber (21) of the booster unit (4) to the wheel cylinders (45a) and (46a), and the braking force increases again.

In this way, the brake force is repeatedly lowered, held and raised several times in a short period of time to prevent the wheels from locking up, but once the vehicle reaches the desired speed. , or when the vehicle stops, the pedal force applied to the brake pedal is released, and the anti-skid control circuit also cuts off the current to the solenoid of the electromagnetic valve that was energized at that time. That is, each of the electromagnetic valves (110) to (115) and (117) is in the illustrated state.

The pressure fluid in the wheel cylinder (45a
12) The entire fluid pressure generation chamber (3) of the mask cylinder part (3)
41 (reflux to 4υ, excess pressure liquid is returned through the return hole (50)
It passes through f6υ and returns to the reservoir (57). On the other hand,
Pressure chamber CI of booster section (4)! 91 is discharged to the reservoir (57) side through the entire through hole (970) of the movable valve element (material), as in the case where the above-mentioned anti-skid control is not performed at all.Thus, the braking force becomes zero.

As mentioned above, when performing anti-skid control, pressure fluid is partially discharged from the wheel cylinders (45a) (46a) to the reservoir 67) many times, but the brake force does not increase again. This is done by supplying pressure liquid from the pressure l mark of the booster part (4), and the liquid pressure is generated in the mask cylinder part (3) because it is not supplied from the liquid discharge generation chamber ( The piston α1 (E) will not be overstroked due to insufficient hydraulic fluid in the 4/4υ.

A hydraulic pump (
Since pressurized liquid is supplied from 9υ or the achievator (c) through all the open supply valves, the liquid pressure will not drop.

That is, when the annular protrusion (97b) of the movable valve body (97) is in contact with the inner two flange portions (104a) of the sleeve (104) during brake operation, pressure fluid flows from the pressure chamber (c) to the wheel. By discharging the liquid to the cylinders (45a) and (46a), the hydraulic pressure in the pressure chamber decreases, but the first piston α moves to the right and the movable valve body (9
The annular projection (97b) of 7) is separated from the inner flange (104a) of the sleeve (104), and the input chamber a
Pressure liquid flows into the pressure chamber (21) and is replenished. That is, the sum of the input F to the input member (9), the moving force of the booster unit (4) against the first piston α, and the mask cylinder A state of balance between the current hydraulic pressure of the hydraulic pressure generating chamber (41 (41) of section (3) and the reaction force exerted on the first piston α force is maintained).

Although the embodiment of the present invention performs all of the above-mentioned functions,
Furthermore, the movable valve body (97) of the opening (1) has a columnar shape, and its front end is connected to the first piston (1) through the seal ring (99). The medium diameter hole part (951K fits) of the stepped hole (94).
ing. Therefore, the force exerted by the hydraulic pressure in the input chamber a against the annular protrusion (97a) of the movable valve body (97) and the inner flange (104a) of the entire sleeve (104) can be minimized. In other words, the cross-sectional area of the movable valve body 0'0 on the end side '? i-8,, movable valve body (9η annular protrusion (97
The inner flange portion (104a) of the sleeve (104) in a)
) on the seating area 'kS4, the hydraulic pressure in the input chamber a kPiv, the sum of the spring force of the valve spring 0 (1) and the elastic force of the rubber ring (102), then the movable valve body (the annular projection of 9η ( 97a
) is the inner two flange portions (104a) of the sleeve (104).
k press force''/'le force is (Sm-81) X Pi +f
It can be made as small as possible by publishing it in Tonashi, S., and S.S. Therefore, the force for opening the supply valve by the supply valve input member (9) configured in this manner can be minimized, and the operation can be speeded up.

Conventionally, a steel ball is used in place of η of a columnar movable valve body, and the force required to open the valve is equal to the seating area of the steel ball XPi and the spring force of the valve spring, and the force required to open the valve is input g
Full aO fluid pressure was being received. Therefore, the force required to open the valve is large, making it difficult to operate quickly. However, according to this embodiment, the force required to open the valve can be made almost equal to the sum of the spring force of the valve spring and the elastic force of the rubber ring (102), so that the speed is completely increased. It can be greatly improved.

In addition, when performing anti-skid control as in this embodiment, pressure fluid flows from the pressure chamber (29) to the wheel cylinder (4).
5aX46a) Even if K is supplied, since the opening pressure of the supply valve is small, pressure fluid can be immediately replenished from the input chamber a side. This makes it possible to cope with a decrease in braking force within a short period of time, and a rise during repeated repetitions of foot hold and rise.

(2) Annular protrusion (97a) of movable valve body (97)? The spring force that resists opening the supply valve when the sleeve (104) is unseated from the inner flange (104) is caused by the valve spring (coil spring) and the rubber ring (10
2), the viscosity coefficient or damping coefficient of the coil spring is small, but that of the rubber ring (102) is large. If the spring force that resists valve opening is obtained only by the coil spring, if the input member (9) suddenly pushes the movable valve body (θη), the coil spring and the movable valve body (
97] may move forward more than necessary, causing notching and unstable control. However, in this embodiment, since the spring force of the rubber link (102) is also resisted, it is possible to suppress the above-mentioned forward movement more than necessary, and prevent the occurrence of sudden force applied to the input member (9). Stable control can be performed even in difficult situations.

Furthermore, since the groove (97b) functions as a restricting groove, sudden inflow of hydraulic fluid from the input chamber a is prevented, and hunting prevention 1 can also be achieved by this.

(3) When the discharge valve is opened, that is, the input member (9)
The annular projection (107) at the tip of the movable valve is a rubber seal for corporal punishment.
) (106), the pressure fluid in the pressure chamber Q9 flows through the movable valve body (97c), the small diameter hole (121) of the first piston (l″a), and the auxiliary hydraulic pressure chamber ( 271 all passes through and is refluxed to the reservoir 6η.The cylinder body (2)
No special drain structure is provided. Therefore, the entire configuration for this purpose is simplified.

(4) The first solenoid valve (110) (112) and the second solenoid valve (
111) (113) and the booster section (4)
Is there a third solenoid valve (1t7) between the pressure display and the ? , so that during amplifier skid control, there is no need to supply pressure fluid only from the fluid pressure generation chamber (41 (41) of the mask cylinder part (3) to raise the brake force of the wheel cylinder again. , the hydraulic pressure generation chamber (41 (4υ) can prevent a shortage of liquid volume.

The embodiments of the present invention have been described above, but of course the present invention is not limited thereto, and various modifications can be made based on the technical idea of the present invention.

For example, in the above embodiment, the anti-skid piping section (13
0)? Although the brake system is provided to enable anti-skid control, it may be omitted and used as a normal brake system.

Furthermore, in the above embodiments, the entire hydraulic booster for assisting the operation of the mask cylinder for the brake has been described, but the present invention is not limited to this and may be used for, for example, a clutch.

In addition, in the above embodiments, the sleeve (1) is used as the valve seat of the supply valve.
The inner flange part (104a) of 04) was used, but
A step is formed in the inner hole of the first piston a, and this? It can also be used as a valve seat. Alternatively, the shape of the inner hole of the first piston may be completely changed and omitted as a sleeve (104)'.

In addition, in the above embodiment, the cross-sectional area S of the front end side of the movable valve body (971) and the seating area of the discharge valve are the seating area S of the supply valve.
, smaller and movable valve body so that these are equal! D and input member (9) 1- may be configured. In this case, the force required to open the supply 9F is equivalent to the spring force of the valve spring υ, making it possible to achieve extremely quick operability.

As described above, according to the hydraulic booster of the present invention, the cylinder-shaped movable valve body is entirely fitted into the recess of the piston via the sealing member, so that the operating force required to open the valve is reduced. It can be made as small as possible, thereby speeding up the operation and improving overall efficiency.

[Brief explanation of drawings]

FIG. 1 is a side sectional view showing a mask cylinder with a brake hydraulic booster according to an embodiment of the present invention together with an anti-skid piping section, and FIG. 2 is an enlarged side sectional view showing details of the multiple valve device in FIG. 1. It is a diagram. In the figure, (11......Mask cylinder with hydraulic booster for brake (4)...・・・・・・Boosting device part (9)・・・・・・・・・・・・・・・・Input axis αO・・・・・・・・・・・・・・・・・・First piston (29)・・・・・・・・・・・・・・・・・・
Boosting pressure chamber (94)・・・・・・・・・・・・・・・
・・・Stepped hole (97)・・・・・・・・・・・・・・・
・・・・・・Movable valve body (97a)・・・・・・Annular protrusion (99)・・・・・・・・・・・・・・・・・・
Seal ring (104a)... Inner flange of sleeve (104) Attorney Yasuo Iisaka (Adjoining Proceeding Amendment May 2, 1980, Mr. Kazuo Wakasugi, Commissioner of the Japan Patent Office, 1) Indication: 1982 Patent Application No. 33041 2, Title of invention: Hydraulic booster 3, Relationship with the person making the amendment: Patent applicant: 4, Attorney: 5, Date of amendment order: 6, Invention increased by amendment Number 07, drawing 8 subject to correction, and supplementary drawing of Shoji Toshi in the attached sheet of contents of correction.

Claims (1)

[Claims] A main body having a cylinder hole formed therein, a piston slidably inserted into the cylinder hole, an input chamber formed on the side of the piston and connected to a pressure source for supplying pressurized liquid, and a rear side of the piston. a pressure chamber formed in the input chamber and the pressure chamber, and a recess provided on the rear side of the piston in communication with the input chamber and the pressure chamber;
The valve device includes a valve device provided in the recess, an input shaft disposed to allow full operation of the valve device, and a movable valve body movably inserted into the recess, and a movable valve body opposed to the valve device. a valve seat formed on the rear side wall of the recess, and a valve spring that biases the movable valve body fully rearward so as to seat on the valve seat; In a hydraulic booster whose rear sides are connected to the pressure chambers, the movable valve body has a columnar shape, and the front end of the movable valve body is fitted into the recess through a sealing member. Pressure type booster.