JPS6085055A - Hydraulic booster - Google Patents

Abstract

PURPOSE:To weaken a return spring in its force and quicken the return of a piston instead, by adjoining a rear surface of the piston of a master cylinder to an input hydraulic chamber of a booster, while making a pressure receiving area of the booster piston larger than that of the master cylinder's piston. CONSTITUTION:A booster piston 21 is solidly coupled with a rear piston 72 of a master cylinder M. An input hydraulic chamber 23 and an output hydraulic chamber 24 are formed at both sides of the booster piston 21. It is recommended that a pressure receiving area S2 of the booster piston 21 be set to being larger than that (a pressure receiving area S1) of the rear piston 72. In time of engine driving, if a switch 55 is turned on and a brake pedal 28 is stepped on, a switch 52 closes, making a valve 49 open, whereby hydraulic pressure is led into the input hydraulic chamber 23. After brake operation, the hydraulic pressure continues to be led into hydraulic chamber 23 till the pedal 28 is fully restored to its original position so that the booster piston 21 is quickly returned by means of a pressure receiving area differential. With this constitution, return springs 121 and 122 are able to be relatively set to weakness.

Description

DETAILED DESCRIPTION OF THE INVENTION The present invention relates to a hydraulic booster, particularly a booster sill that is connected to the rear of the ring body of a mask sill; A booster piston is divided into an input hydraulic pressure chamber and a rear output hydraulic chamber having a larger pressure receiving area, and is connected to a Musk Schilling piston; the booster piston is slidably fitted into a valve hole provided in the booster piston, This invention relates to a booster device consisting of a valve piston that is manually operated to move forward and backward so as to communicate and disconnect between the output hydraulic chambers and to disconnect and communicate between the output hydraulic chamber and the oil tank, and its purpose is When the valve piston is retracted to disable the Musk Schilling, the hydraulic pressure in the input hydraulic chamber is used to apply a retracting force to the booster piston, and the cent load of the piston return spring in the Mask Schilling is relatively reduced. It is an object of the present invention to provide a booster capable of quickly retracting a booster piston even if it is set weakly.

To achieve this objective, the present invention makes the rear surface of the piston of the mask ring face the input hydraulic chamber, and makes the pressure receiving area of the booster piston in the input hydraulic chamber larger than the pressure receiving area of the piston of the master ring in the same chamber. It is characterized by the fact that

Embodiments of the present invention will be described below with reference to the drawings. First, starting with the first embodiment shown in FIG. 1, M is a Kundem-type mask cylinder for a two-system hydraulic brake of an automobile, and an oil tank 2 is formed on the upper side of the cylinder body 1.
Inside, the lower half is separated by a partition wall 2a into a front oil sump 2, a rear oil sump 2. These oil sumps are divided into 2. ．． 22 communicate with the cylinder hole 1a of the knolling body 1 via the front relief boat 31, 32 and the rear relief boat z, , 42, respectively. A front piston 71 and a rear piston 72 are slid into the cylinder hole 1a.

In the cylinder hole 1a, a front hydraulic chamber 81 is formed between the front piston 7 and the front end wall of the seven-ring hole 1α, and both pistons 7, . Rear hydraulic chambers 82 are defined between the hydraulic chambers 8.72, respectively. ．． 82 communicates with each of the two brake hydraulic circuits via output boats (not shown). Each piston 7, 17□ has a piston cup 9. at its front end. ,92
and an annular replenishment oil chamber 10. with a small diameter in the middle part and an annular replenishment oil chamber 10. , 102 are formed, respectively, and through holes ii, , i+□ which communicate the oil chambers 101, 10□ with the back of the piston cup 91°9□ are formed in each screw I・N7.
, 72.

A front return spring 12 is provided in the front hydraulic chamber 81 to urge the front piston 71 in the backward direction. is accommodated, and the rear oil chamber 82
A rear return spring 12□ that springs the rear screw 72 in the backward direction and a spacing retaining device 14 that restricts the extension of the spring beyond a certain level are housed in the rear return spring 12□. The spacing device 14 includes a pair of front and rear movable and fixed seats 15 and 16 that receive both ends of the rear return spring 122, and a support shaft 17 that is taken over the rear piston 72 and slidably supports the movable seat 15. The support shaft 17 has an enlarged head 17α that restricts the forward movement of the movable seat 15. Therefore, the support shaft 17 allows the movable seat body 15 to approach the rear piston 12, but prevents the movable seat body 15 and the rear piston 7 from being separated by a certain distance or more from the rear piston 72 by the enlarged portion 170.
The maximum distance between the two is regulated, and this regulation causes the return spring 122 to exceed its extension limit.

The above is a conventional configuration, and the hydraulic booster of the present invention is connected to this mask/ring M. The configuration of the booster B will be explained next.

A booster cylinder 20 having a cylinder hole 20a with a larger diameter than the cylinder hole 1a is integrally connected to the rear of the cylinder body 1 of the mask cylinder 11/, and a booster cylinder 20 having a cylinder hole 20a having a larger diameter than the cylinder hole 1a is connected to the rear of the cylinder body 1 of the mask cylinder 11/. A booster piston 21 is integrally connected. An end plug 22 that restricts the backward limit of the booster piston 21 is screwed onto the rear end of the booster cylinder 20 .

At the injection hole 20ff, the booster piston 21
has an annular input hydraulic chamber 23 with a small diameter in the middle part, and defines an annular input hydraulic chamber 23 on the outer periphery thereof, and also defines an output hydraulic chamber 24 between it and the end plug 22, and the pressure receiving area of the output hydraulic chamber 24 corresponds to the input hydraulic pressure. It is thicker than that of chamber 23. In addition, the cylinder holes 1a and 2
0a, the pressure receiving area S1 of the rear piston 72 in the input hydraulic chamber 23 is larger than that of the booster piston 21.
The pressure receiving area S2 is larger.

A series of valve holes 25 are bored in the rear piston 72 and the booster piston 21 along their axes, starting from the rear end of the booster piston 21 and ending at the middle of the rear piston 7 □. , a valve piston 26 that passes through the end plug 22 is slidably engaged with the valve piston 26 , and a brake pedal 28 is connected to the rear end of the valve piston 26 via a busho schrond 27 .

An annular recess 29 is formed in the rear end surface of the booster piston 21, and a stopper ring 30 is fixed to the opening of the recess 29, and comes into contact with the stopper ring 30 within the recess 29 to restrict the backward limit of the valve piston 26. A stop ring 31 is fixed to the valve piston 26. The latter stopper ring 31 is urged toward the former stopper ring 30 by a return spring 32. The forward limit of the valve piston 26 relative to the booster piston 21 is regulated by the front end of the valve piston 26 coming into contact with the front end wall of the valve hole 25 .

The valve piston 26 is provided with three annular ports (33, 34, 35) arranged at intervals in the axial direction on its outer periphery, and an oil passage 36 that communicates these ports 33, 34, 35 with each other. . Hereinafter, the above Poe) 33, 34.35 will be
The valve piston 26 is called a front port 33, a center port 34, and a rear port 35 from the front end side, and the rear port 35 is always open to the output hydraulic chamber 24.

On the other hand, the booster piston 21 has an inlet boat 3 extending from the input hydraulic chamber 23 to the valve hole 25 corresponding to the central hoard 34.
7, and an outlet port 38 extending from the valve hole 25 to the replenishment oil chamber 102 is bored in the rear piston 72 in correspondence with the front port 33.

Note that the cylinder hole 20α26 is connected to the front end of the valve piston 26.
The through hole 40 of the rear piston 7□ is
It communicates with the replenishment oil chamber 102 via.

The rear piston 72 has a large diameter hole 41 that opens on its front surface.
A small diameter hole 42 (open at both ends) is bored in this large diameter hole 41 and the cylinder body 20a, and in the large diameter hole 41, from the back of the large diameter hole 41, an elastic piston 43 made of a comb or the like, and an elastic piston 43 of the same diameter are formed. Once the pressure receiving piston 44 is slid together, the pressure receiving portion of the pressure receiving piston 44 faces the rear hydraulic chamber 82 . A reaction piston 45 that can come into contact with opposing end surfaces of the valve piston 26 and the elastic piston 43 is slid into the small diameter hole 42 . A reaction mechanism R that transmits the operating reaction force of the rear piston 72 to the valve piston 26 by these pistons 43, 44, 45.
is configured.

The pressure receiving piston 44 is separated from the large diameter hole 41 by a stop ring 46 fixed to the opening of the large diameter hole 41. 17 are integrally provided in a protruding manner.

In this case, since the support shaft 17 and the pressure receiving piston 44 form one part, it is advantageous to reduce the structure to 1'.

The human hydraulic pressure chamber 23 is connected to the oil tank 2 by an oil passage 47, and the oil passage 47 has an input hydraulic pressure chamber 2 containing oil stored in the oil tank 2.
A hydraulic pump 48 capable of supplying pressure to the oil pump 3 and an electromagnetic on-off valve 49 located downstream of the pump 48 are interposed, and a pressure accumulator 50 is connected between the hydraulic pump 48 and the O/on-off valve 49.

The electromagnetic on-off valve 49-1 is a normally closed type that opens when the lunoid is energized, and the electric circuit connecting the lunoid and the power source 51 includes a control switch that closes when the brake pedal 28 is depressed. 52 is inserted. Further, the hydraulic pump 48 is configured to be driven by an electric motor 53, and an electric circuit connecting the motor 53 and the power source 51 is configured to respond to the decrease in the internal pressure of the pressure accumulator 50 below a certain value. A closing pressure switch 54 is inserted. Incidentally, 55 is a main switch that is linked to opening and closing of the ignition/ignition switch of the automobile.

Next, the operation of this embodiment will be explained. First, the main switch 55 is
When closed, the electric motor 53 operates and the °C hydraulic pump 48
The hydraulic pressure can be stored in the pressure accumulator 50 up to a predetermined pressure.

When the brake pedal 28 is in the inoperative state, as shown in the figure,
Since the control switch 52 is open, the electromagnetic on-off valve 4
9 is in a closed state. Further, the valve piston 26 is held at the backward limit by contacting the stopper rings 30 and 310, the front boat 33 occupies a position communicating with the 1'' robot 38, and the central boat 34 is cut off from the inlet port 37. It occupies a position slightly further back. Therefore, the output oil pressure v24 is from the rear port 35, the oil passage 36, and the front boat 33.
, exit boat 38, replenishment oil room 102 and Zaburai port 1
・Since it communicates with the oil tank 2 through 4□ and is at atmospheric pressure, the front and rear pistons 7, . 72 and booster piston 21 each have a return spring 121.

It is held in the retracted position by a force of 122.

Now, when the brake pedal 28 is depressed to brake the automobile, the control switch 52 is closed and the on-off valve 49 is opened. At the same time, from the brake pedal 28 to the bushing rod 2
7, the valve piston 26 is pushed forward, firstly the front boat 33 is isolated from the outlet boat 3B, and then the central boat 34 is moved into a position of communication with the inlet port 37.

As a result, the hydraulic pressure is supplied from the pressure accumulator 50 and the hydraulic pump 48 to the input hydraulic chamber 23, and the hydraulic pressure is applied to the inlet boat 37, the central boat 34, the oil passage 36, and the booster piston no. moves forward, which causes the front and rear pistons 7, . 7. ! and their return springs 12. ．． 122 is moved forward while being compressed. At this time, if both brake hydraulic circuits are normal, each piston cut 91°9□ is IJ IJ-Fuft 3□
, 32, hydraulic pressure is generated in each hydraulic chamber 81, 82 according to the advance of each piston 70, 7□, and both brake hydraulic circuits can be operated simultaneously.

During this braking process, the central boat 34
1, the valve piston 26 abuts the elastic piston 43 via the reaction piston 45. Then, as the rear piston 72 moves forward, the hydraulic pressure in the rear hydraulic chamber 8□ rises, and the pressure receiving piston 44 receives the hydraulic pressure as an operation reaction force of the rear piston noah 2, and the elastic piston 4
Compress 3 → −7, ] − to F ino 1: tuyere 2k //'
l I-i:#;:sl//'1-stand II -A: I
It is fed to the valve piston 26 via the G-claw l + bibton 45, and then to the brake pedal 28 via the Zonschlotz 27, which allows the driver to sense the strength of the braking force. 71!i, the pressure receiving piston 44 directly senses the oil pressure in the hydraulic chamber 82 of the Mask Schilling M, so the magnitude of the output of the Mask Schilling M can be accurately sensed from the initial stage of operation.

During this braking, if there is an oil leakage failure only in the brake hydraulic circuit on the front hydraulic chamber 8□ side, no oil pressure will naturally be generated in the front hydraulic chamber 81 even though the front piston 71 moves forward.
The forward stroke of the booster piston 21 until the front piston 7□ comes into contact with the front end wall of the sill hole 1a becomes an invalid stroke, but the subsequent forward movement of the booster piston 21 generates hydraulic pressure in the rear hydraulic chamber 8□. I can do it.

On the other hand, if there is an oil leakage failure only in the brake hydraulic circuit on the rear hydraulic chamber 82 side, no oil pressure will naturally be generated in the rear hydraulic chamber 82 even though the rear piston 72 moves forward.
The forward stroke of the booster piston 21 until the support 11Q1117 of the first device 14 comes into contact with the rear end of the front histone 11 becomes an invalid stroke. The front piston 71 is moved forward, and hydraulic pressure can be generated in the front hydraulic chamber 8□. At this time, the actuation reaction force of the front piston 7 is transmitted to the pressure receiving piston 44 via the support shaft 17, so this force can be fed back to the brake pedal 28 in the same manner as described above.

Next, when the brake pedal 28 is released to release the brake, the valve piston 26 is moved back by the force of the return spring 32, and the central boat 34 is placed in the position where it is cut off from the inlet port 37, as in the non-operating state described above. In addition, since the front boat 33 is returned to the position where it communicates with the outlet boat 38, the output hydraulic chamber 24
The hydraulic pressure is released to the oil tank 2. On the other hand, while the on-off valve 49 is open, oil pressure continues to be introduced into the input oil pressure chamber 23, so this oil pressure is applied to the pressure receiving area difference (S2S+
) to apply a retreating force to the booster pist 721. As a result, the booster piston 21 follows the backward motion of the brake pedal 28, and in conjunction with this, the front and rear pistons 71.7□ move backward by the force of the return springs 12, i22. When the booster piston 21 reaches its backward limit and the brake pedal 28 returns to its original non-operating position, the control switch 52 is opened, and the on-off valve 49 closes to cut off the oil passage 47.

During this time, both pistons 7, . Hydraulic room 8 due to employee 72 leaving work.
．． ．． If pressure reduction occurs in 82, piston camp 92, 9□
The outer periphery of the oil sump 2. bends forward due to the pressure difference between the front and rear, creating a 7-ring hole b. ．． Hydraulic oil in 22 is supplied to the supply boat 4. ．． 42. Supply oil room 10. , 102 and through hole 11. ．． Hydraulic chamber 8 through 11□. ．． 8. .

G3. , 3□ and returned to the oil tank 2.

Next, to explain the second embodiment of the present invention shown in FIG. 2, in addition to the inlet port 27, the booster piston 21 has a communication boat 60 that connects the valve hole 25 to the output hydraulic chamber 24 at the rear thereof. At the rear, from the output hydraulic chamber 24 to the valve hole 25
The valve piston 726 has an annular communication groove 61 that communicates and blocks communication between the inlet port 37 and the communication boat 60 as the piston 26 advances and retreats, and An annular rear boat 35 that is shut off and communicated with outlet water 1 and 38 according to advance and retreat, and this rear port 35 is connected to the replenishment oil chamber 1 through the front oil chamber 39 of the valve hole 25
02 and an oil passage 36 which is in continuous communication with the oil passage 36 is bored. The support shaft 17 of the spacing device 14 is screwed onto the rear end of the front piston nore 1, and the front and rear pistons 7, . When the interval 72 narrows to a certain value, the piston nozzle 5 connects to the pressure receiving piston nozzle 44 that slides on the rear piston nozzle 2. This support shaft 17 is equipped with an enlarged head i7a at the rear end, and is adapted to restrict the backward movement of the movable seat 15, and a rear return spring 122 is installed between the movable seat 15 and the front piston noah 1. It will be reduced. Note that the valve piston 26 is divided into two parts, front and rear, for manufacturing reasons, but it is not necessary to do so. does not have the same sign as that.

Thus, when the valve biston 26 is in the retracted position, it shuts off the inlet boat 37 and connects the rear port 3 to the outlet boat 38.
5, so the connection between the person and the output hydraulic chambers 23 and 24 is cut off, and the output hydraulic chamber 24 is connected to the outlet water 1 and 38,
Rear port 35, oil passage 36.9, front oil chamber 39, through hole 40
and communicates with the oil tank 2 via the replenishment oil chamber 102. Furthermore, when the valve piston 726 is moved to the forward position, the communication between the outlet boat 38 and the rear boat 35 is cut off, and then the communication groove 61 connects the inlet boat 37 and the communication boat 60, so that the output hydraulic chamber 24 and the communication boat 60 are communicated with each other. The space between the oil tanks 2 and 2 is blocked, and the space between the output hydraulic chambers 23 and 24 is inlet port 37,
They are communicated via a communication groove 61 and communication bows 1 and 60.

As described above, according to the present invention, in the hydraulic booster, the rear surface of the piston of the master ring faces the input hydraulic pressure chamber, and the pressure receiving area of the booster piston in the manual hydraulic chamber is equal to that of the piston of the mask ring in the same chamber. Since the area is larger than the pressure receiving area, by retracting the valve piston, the input and output hydraulic chambers are cut off and the hydraulic pressure in the output hydraulic chamber is transferred to the oil tank.
When M is released, the hydraulic pressure in the input hydraulic chamber can be used to apply a retraction force to the booster piston. Therefore, even if the force of the return spring of the piston in Musk Schilling is set relatively weak, the booster piston can be moved quickly. The valve piston can be moved backward, and the input force on the valve piston can be reduced to the extent that the cent load of the return spring is weakened, thereby improving its operability.

[Brief explanation of drawings]

FIG. 1 is a longitudinal sectional side view of an assembly of a mask shilling and a booster according to a first embodiment of the present invention, and FIG. 2 is a similar longitudinal sectional side view illustrating a second embodiment. A (master/linda, B... booster, R... reaction mechanism, Sl - pressure receiving area of the rear piston 7□ in the input hydraulic chamber 23, S2... pressure receiving area of the booster piston 21 in the input hydraulic chamber, 1 Silling body, 2...Oil tank, 71.7□・Front. Rear piston, 80,8□・Front, rear hydraulic chamber, 20 Booster cylinder, 21・Booster piston, 23 Human power hydraulic chamber, 24-・Output hydraulic chamber, 25. Valve hole, 26.
- Valve piston, 28... Brake peg nope 33... Front boat, 34. Center boat, 35... Rear port, 3
6...Oil route, 37 Population boat 1., 38 Departure boat,
48 Hydraulic pump as a hydraulic source, 50 Pressure accumulator as a hydraulic source Patent applicant Nissin Kogyo Co., Ltd. Procedural amendment (Engraving 1. Display of the case 1982 Patent Application No. 194713 2, Name of invention Hydraulic booster Device 3, relationship with the case of the person making the amendment Patent applicant name: Nissin Kogyo Co., Ltd. 4, Korito Dai 105 JJ- Address: 4-4-5 Shinbashi, Minato-ku, Tokyo No. 2/Mura Building Telephone Tokyo 434- 4151 5 Daily publication of the order for amendment J. 11, 1980 (Date of dispatch: January 31, 1982) Annex No. 1 (No change in content)

Claims (1)

[Claims] A booster sill that is connected to the rear of the ring body of the master ring; an input hydraulic chamber at the front that is slid into this booster sill and whose inside is connected to the hydraulic pressure source, and an output hydraulic pressure chamber at the rear that has a larger pressure receiving area. a booster piston partitioned into a chamber and connected to the piston of the Musk Schilling; and a booster piston that is slidably engaged with a valve hole provided in the booster piston to establish communication and isolation between the output hydraulic chamber and the output hydraulic chamber. A booster comprising: a valve piston that is artificially moved forward and backward to shut off and communicate between oil tanks; A hydraulic booster characterized in that the pressure receiving area of the piston is larger than that of the piston of the mask cylinder in the same chamber.