JPH0248287Y2 - - Google Patents

Description

[Detailed Description of the Invention] (Field of Application of the Invention) The present invention relates to an improvement of a pressure fluid restricting device that supplies pressure fluid to a hydraulic pressure adjustment device for an anti-lock brake used in automobiles and the like.

(Background of the invention) In the fluid circuit that drives the power steering device installed in automobiles, etc., a regulator piston is provided between the discharge side of the pump and the power steering device to control the flow of fluid. A device in which fluid is supplied to a hydraulic pressure regulating device for an anti-lock brake connected upstream of the brake is already known.

However, in the conventional type described above, the regulator piston is always driven in conjunction with the brake operation by the hydraulic pressure of the brake system, so a loss in the amount of fluid discharged from the brake master cylinder is unavoidable. At the same time, there was a problem in that the number of seals in the brake system increased due to the regulator piston.

(Purpose of the invention) The purpose of the invention is to provide a pressure fluid throttling device that can solve the above-mentioned problems, eliminate the loss of fluid volume discharged from the brake master cylinder, and reduce the number of sealing points in the brake system. The goal is to provide the following.

(Characteristics of the invention) In order to achieve the above object, the invention includes two pressure chambers connected to the high pressure chamber side and the low pressure chamber side of the brake servo motor, and partitioning both the pressure chambers, and a reciprocating body that is driven by the pressure difference between the high pressure chamber side and the low pressure chamber side when the brake servo motor operates, and a throttle valve that is operated by the reciprocating body and controls passage of fluid. Accordingly, the brake servo motor is configured to operate according to the difference in air pressure between the brake servo motors.

(Embodiment of the invention) The drawing is a sectional view showing an embodiment of the invention.

The suction side of the pump 1, which is driven by an engine (not shown), is connected to a reservoir 4 by conduits 2,3. The discharge side of the pump 1 is connected to conduits 5, 6, 7.
It is connected to an inlet port 10 provided in the case 9 of the pressure fluid restricting device 8 through the. 11 is a check valve. Conduits 12 and 13 branched from the aforementioned conduits 5, 6, and 7 are connected to a front wheel antilock brake hydraulic pressure adjusting device 14 and a rear wheel antilock brake hydraulic pressure adjusting device 15, respectively.

Inside the case 9, a cylinder portion 16, a small diameter chamber 17, a large diameter chamber 18, and an opening 19 are formed.
The small diameter chamber 17 is connected to the reservoir 4 via an outlet port 20, a conduit 21, a power steering device 22 and a conduit 23, and the large diameter chamber 18 communicates with the aforementioned inlet port 10.

The left side of the case 9 is covered by a lid member 24, and a solenoid coil 25 and a guide 2 are installed inside.
6 is accommodated, and a chamber 27 is formed. A valve plunger 28 that is slidably loaded into the cylinder portion 16 of the case 9 projects into the chamber 27 , and the valve plunger 28 is inserted into the chamber 27 through a clip 29 .
It is biased to the right by a spring 30.

The valve plunger 28 includes passages 31 and 32 that communicate the chamber 27 and the large diameter chamber 18, and a throttle hole 3.
3 and a collar portion 34 are formed. The flange 34 comes into contact with the step 35 when the solenoid coil 25 is energized and the valve plunger 28 is driven leftward.

An inner shell 36 is attached to the right side of the case 9 and is secured together with a nut 37 that closes the opening 19. A valve rod 38 is inserted into the nut 37. A valve head 39 for opening and closing the passage 32 of the valve plunger 28 is formed at the inner end of the valve rod 38, and a plate 40 and a diaphragm 41 are attached to the outer end by a clip 42. The outer periphery of the diaphragm 41 is sandwiched between the inner shell 36 and the outer shell 43, and the inner space of both shells 36, 43 is larger than the diaphragm 41.
The chamber is divided into a low pressure chamber 44 and a high pressure chamber 45. 46 is a seal, 47 is a relief valve for oversupplying the pump 1, and 48 is a spring that biases the relief valve 47.

The aforementioned low pressure chamber 44 and high pressure chamber 45 are connected to connection hoses 49, 5, respectively, indicated by broken lines.
0, it is connected to the low pressure chamber 52 and high pressure chamber 53 of the brake servo motor 51. In the servo motor 51, when a pedal force is applied to the brake pedal 54, a pressure difference is generated between the low pressure chamber 52 and the high pressure chamber 53, and the servo piston 55 is pushed to the left by the pressure difference. brake pedal 54
This will help improve your pedaling power.

One brake pipe 57 of the tandem master cylinder 56, which is attached so as to be pushable by the output of the servo motor 51, is connected to the hydraulic pressure adjustment device 14 for antilock brakes on the front and rear wheels via brake pipes 58 and 59. , 15, and further connected to a front right brake device 62 and a rear left brake device 63 through brake pipes 60 and 61 connected to the output side.

The other brake pipe 64 of the tandem master cylinder 56 is connected via brake pipes 65 and 66 to the input sides of the front and rear antilock brake hydraulic pressure regulators 14 and 15, respectively, and is further connected to the output side Brake pipes 67, 68 connected to
Thus, it is connected to the front left brake device 69 and the rear right brake device 70.

The above connection simultaneously configures a two-system brake system using cross piping and an anti-lock brake system that operates independently in the front and rear.

Next, the anti-lock brake hydraulic pressure adjustment device 15
I will explain about it. The two anti-lock brake hydraulic pressure adjusting devices 14 and 15 each have a similar structure.

The anti-lock brake hydraulic pressure adjustment device 15 includes a pressure difference responsive member 72 integrally formed with a hydraulic pressure adjustment piston 71 so as to be movable up and down. Note that the hydraulic pressure adjustment piston 71 is formed separately.
and a pressure differential responsive member 72 may be incorporated.
A lid member 73 is fixed above the pressure difference responsive member 72, and compressed air is sealed in a pressure chamber 74 formed inside. 75 is a spring retainer, 7
6 is a compression spring. Pressure differential responsive member 72
is pressed downward by the compressed air and the compression spring 76.

A recess 79 that engages with the inner end of the valve plunger 78 is formed around the side surface of the pressure differential responsive member 72 .

Spool valves 80 and 81 are formed around the side surfaces of the valve plunger 78, and a passage 8 is formed inside.
2,83 are provided. Valve plunger 78
When the solenoid coil 84 is energized and excited,
Once removed from the recess 79 and driven to the right and demagnetized, the spring 105 returns it to the illustrated position. The spool valve 80 operates to open and close the supply passage 85, and the spool valve 81 operates to open and close the discharge passage 86. When the valve plunger 78 is in the position shown, a chamber 87 formed below the pressure differential responsive member 72 includes a discharge passage 86, passages 83, 8
2. A chamber 88 formed by the recess 79 and a passage 89 communicate with the reservoir 4, which is connected by a conduit 90 and is open to atmospheric pressure.

A cylinder 91 extending below the hydraulic pressure adjusting piston 71 accommodates a floating piston 92 that adjusts the hydraulic pressure of the two-system brake so as to be vertically slidable.

The valve chamber 93 of the floating piston 92 accommodates an on-off valve 94, and the brake pipe 66 on the input side and the chamber 9
5. Passage 96, output side brake pipe 68, chamber 97
Communication with is controlled intermittently.

In the valve chamber 98 below the floating piston 92,
An on-off valve 99 similar to the on-off valve 94 is housed, and includes a brake pipe 59 on the input side, a brake pipe 61 on the output side,
Communication with the chamber 100 is controlled intermittently. The on-off valves 94 and 99 are opened by pushing down pins 101 and 102, respectively, and springs 103 and 1
04 in the valve closing direction.

In addition, the solenoid coil 2 of the pressure fluid restricting device 8
5 is a hydraulic pressure adjustment device 1 for anti-lock brakes.
4, 15, the supply fluid from pump 1 is insufficient or each brake device 62, 63, 69, 7
0, when a sudden pressure reduction is requested, a controller (not shown) energizes the solenoid coils 84 of the anti-lock brake hydraulic pressure regulators 14 and 15 (anti-lock brake hydraulic pressure regulators). 14 (not shown) are also energized by the controller during braking, just before locking.

Next, the operation of the illustrated embodiment will be explained.

When the pump 1 is driven by the engine, the fluid in the reservoir 4 flows through conduits 5, 6.7 and 12.
13, the fluid is fed under pressure to a pressure fluid restricting device 8 and anti-lock brake hydraulic pressure adjusting devices 14 and 15.

The fluid to be fed to the pressure fluid restriction device 8 is introduced into the large diameter chamber 18 through the inlet port 10.

When no input is applied to the servo motor 51, no pressure difference occurs between the low pressure chamber 52 and the high pressure chamber 53 of the servo motor 51. Therefore, connection hose 4
Pressure fluid restriction device 8 connected by 9,50
Both the low pressure chamber 44 and the high pressure chamber 45 are maintained at equivalent vacuum pressure. In this state, the valve rod 38 is pushed to the right by the fluid pressure within the large diameter chamber 18, and the valve head 39 is placed in a position away from the valve plunger 28, ie, in the state shown.

The fluid introduced into the large diameter chamber 18 passes through the passage 32 of the valve plunger 28 on the one hand, and the outer circumferential side of the flange 34 of the valve plunger 28 on the other hand, and is merged in the small diameter chamber 17. The said merging includes the outlet port 20, the conduit 21, the power steering device 22 and the conduit 23.
and is returned to reservoir 4.

When the brake pedal 54 is depressed, the servo motor 5
When an input is given to 1, atmospheric pressure is introduced into the high pressure chamber 53, and a pressure difference is generated between the high pressure chamber 53 and the low pressure chamber 52. The atmospheric pressure in the high pressure chamber 53 is also introduced into the high pressure chamber 45 of the pressure fluid throttle device 8 through the connection hose 50, and a pressure difference corresponding to the pressure difference of the servo motor 51 is generated between the high pressure chamber 45 and the low pressure chamber 44.

Due to the pressure difference between the high and low pressure chambers 44 and 45,
The valve rod 38 is pushed to the left via the diaphragm 41 and the plate 40, and the valve head 3
9 comes into contact with the right end of the valve plunger 28 , the passage 32 is closed, and only the fluid passing through the outer circumferential side of the flange 34 is restricted from the large-diameter chamber 18 to the small-diameter chamber 17 .

Due to the above throttling operation, from pump 1 to large diameter chamber 1
The fluid circuits up to 8 are maintained at a higher pressure than when the brake system is not activated. In this state, when the solenoid coil 84 is energized by the command current for anti-lock operation,
The valve plunger 78 is disengaged from the recess 79 of the pressure differential responsive member 72 and is driven to the right. Next, when the spool valve 81 closes the discharge passage 86 and the spool valve 80 opens the supply passage 85, the pressure fluid is supplied to the chamber 87 below the pressure differential response member 72 via the supply passage 85, chamber 88, and passage 89. , the pressure difference responsive member 72 is connected to the pressure of the atmospheric pressure chamber 74 and the spring 76.
move upward against the pressure of

Due to the above movement, the on-off valves 94 and 99 disposed above and below the floating piston 92 are closed, and the chambers 97 and 99 are closed.
Since the internal volume of chamber 100 is expanded, chambers 97 and 10
Rear wheel left and right brake devices 63, 70 connected to
The hydraulic pressure is reduced and anti-lock operation is performed.

If faster anti-lock operation is required depending on the driving condition of the vehicle, the solenoid coil 25
The power is turned on. By energizing the solenoid coil 25, the valve plunger 28 is moved away from the valve head 39 and driven to the left until the collar 34 abuts the step 35. With this operation, the flow path from the large diameter chamber 18 to the small diameter chamber 17 is closed on the outer peripheral side of the collar 34, and the flow path from the large diameter chamber 18 to the small diameter chamber 17 is closed.
narrowed down to only

Due to the above throttling operation, from pump 1 to large diameter chamber 1
The fluid circuits up to 8 are raised and maintained at a higher pressure than when only the valve head 39 is operated, and the anti-lock brake hydraulic pressure regulator 1
Since the fluid pressure is quickly supplied to 4 and 15, the anti-lock operation can be performed more quickly.

When the solenoid coil 84 is de-energized to release the anti-lock operation, the valve plunger 78 is pushed back to the left by the spring 105, the discharge passage 86 is opened, and the supply passage 8
5 is closed. Therefore, when the fluid in the chamber 87 passes through the passage 89, the chamber 88, and the passages 82, 83 and is released to the atmosphere through the conduit 90 into the reservoir 4, the pressure differential responsive member 72 and the hydraulic pressure adjusting piston 71 are moved back into the atmospheric pressure chamber 7.
4 and the compression spring 76 to apply pressure to the left and right brake devices 63 and 70 of the rear wheels.

(Correspondence between the invention and the embodiment) The diaphragm 41 and plate 40 in the illustrated embodiment correspond to the reciprocating body of the invention, and the valve head 39 corresponds to the throttle valve of the invention.

(Modification) In the illustrated embodiment, a vacuum type servo motor 51 is used, but a servo motor other than a vacuum type can be used. Further, the anti-lock brake hydraulic pressure adjusting devices 14 and 15 are not limited to those of this embodiment. The present invention can also be used in a fluid circuit that does not include a power steering device 22.

(Effect of the invention) As explained above, according to the invention, two pressure chambers are respectively connected to the high pressure chamber side and the low pressure chamber side of the brake servo motor, and the two pressure chambers are partitioned, and a reciprocating body that is driven by the pressure difference between the high pressure chamber side and the low pressure chamber side when the brake servo motor operates, and a throttle valve that is operated by the reciprocating body and controls passage of fluid. Since the brake servo motor is constructed in this manner and operates according to the pressure difference between the brake servo motors, it is possible to eliminate loss of the amount of fluid discharged from the brake master cylinder and to reduce the number of sealing points in the brake system.

[Brief explanation of the drawing]

The drawing is a sectional view showing an embodiment of the present invention. 1... Pump, 4... Reservoir, 8... Pressure fluid restrictor, 14, 15... Hydraulic pressure adjustment device for anti-lock brake, 17... Small diameter chamber, 18... Large diameter chamber, 25... Solenoid coil , 28... valve plunger, 33... throttle hole, 34... flange,
35...Step part, 38...Valve rod, 39...
Valve head, 40...Plate, 41...Diaphragm, 44, 52...Low pressure chamber, 45, 53
... Hyperbaric chamber, 49, 50 ... Connection hose, 51
... Servo motor, 56 ... Tandem master cylinder, 62, 63, 69, 70 ... Brake device.

Claims (1)

[Scope of utility model registration request] In a pressure fluid throttling device that is installed to divide the fluid to the antilock brake hydraulic pressure adjustment device by throttling the fluid flowing in from the pump, a pressure fluid restriction device is installed on the high pressure chamber side and the low pressure chamber side of the brake servo motor, respectively. Two connected pressure chambers,
A reciprocating body that partitions both the pressure chambers and is driven by the pressure difference between the high pressure chamber side and the low pressure chamber side when the brake servo motor operates; A pressure fluid throttling device characterized by comprising a throttling valve for controlling passage.