JPS6325162A - Pressure regulator - Google Patents

Abstract

(57) [Abstract] 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 pressure regulator, in particular, comprising a housing having a regulating piston between a pressure fluid inlet and a pressure fluid outlet, and a pressure fluid supplying a pressure fluid to the regulating piston. Pressure regulators, in particular for pressure fluid-operated braking systems of motor vehicles, in which the applied II-III force is proportional to the load between two members capable of being transferred to each other, in particular between the axle and the cushion-protected mold body Regarding regulators.

[Prior Art] The above type of pressure regulator is described in, for example, the literature (A.
LFRED TEVES GMBHBRAKE
HANDBOOK, 8th edition, 1984, 8 arts
ch-Verlag Publishing, 0ttO-[3run,
p., 240, ``5.5. Load Sensing Brake Force Regulator'').The brake force regulator described in said document transfers a control force proportional to the wheel load to the axle. It is operated by a mechanical device which transmits the relative movement between the brake force regulator and the mold body to the regulating piston of the brake force regulator, thereby varying the switching pressure depending on the load.

- Although various intermediate and transfer member manufacturing tolerances are considered, this type of equipment requires a variety of processes to be applied to the vehicle, such that the actual equipment and adjustment price is typically twice the price of the regulator. The disadvantage is that it has to be adapted. However, adjustments in automobiles only compensate for dimensional changes because the chassis springs have a so-called "setting" of the chassis springs due to very large length tolerances as well as increased operating life.

There is also the disadvantage of displacement of the mechanical drive caused by wear during operation.

Problem to be Solved by the Invention It is therefore an object of the invention to provide a pressure regulator of the aforementioned type which does not require adjustment in a motor vehicle so as to ensure correct operation regardless of tolerances and wear of the chassis. Offer to,
At the same time, it should be easy and inexpensive to manufacture and install.

[Means for solving the problem] This problem is solved by the present invention, which includes a housing in which a regulating piston is provided between a pressure fluid inlet and a pressure fluid outlet, and the control force supplied to the regulating piston is moved relative to each other. The generation of control forces in pressure regulators that are proportional to the load between two possible parts, in particular an axle and a cushion-protected mold body, in particular pressure regulators for pressurized hydraulically operable braking systems of motor vehicles. characterized in that the displacement is caused by a control pressure fluid, for which the load, in particular the wheel load, is supplied to a load transfer element capable of varying its capacity, communicating with a pressure fluid line which transfers the control force from the transfer element to the regulating piston. This is solved by a pressure regulator.

According to a particularly advantageous embodiment of the invention, the transfer element is a tubular structure, the load is supplied to it through the molded part, in particular through the chassis spring, and the connection socket to the control pressure fluid carrying conduit is in the tube. is provided, thereby realizing a particularly simple form of embodiment of the load transfer element. According to a preferred form of an embodiment of the invention, the control pressure fluid is specifically sealed by a diaphragm, thereby preventing displacement of the load sensing drive throughout its operational life.

The socket that connects the load transfer element to the control fluid conveyance pipe is a load transfer member! In general, the open elastic part and the mounting are made of a member, one of which is movable relative to the other.
In particular, it is provided connected to the car body or axle protected by a cushion.

Due to the fact that the capacity of the control pressure fluid of the load transfer element is very large compared to the capacity formed by the product of the diameter of the differential piston and the displacement of the differential piston, the load-sensing drive of the regulator is essentially Moreover, the load transfer elements, which do not affect the chassis structure and do not fatigue elastically during loading, are only changed at inappropriate times.

In order to prevent the mold member tilting of the load type transfer element during the vibration of the car and the correction of the angle between the axle and the car spring, the load transfer element is attached to the load transfer element through means such as a ball joint joint in an angular movement method. Particularly preferred is the arrangement of the receivers.

A similar advantage is that the differential piston is of two-piece construction so that the ball acts as a valve closing member provided for forced contact and sealing with the integrated valve seat. The fact that the differential piston together with the sealant is introduced into the housing in the form of a completely installed regulator cartridge, such that it is substantially fixed during screwing in the closing member, is particularly advantageous for the device in terms of cost.

It is particularly advantageous that the load transfer element for determining the axle load is arranged between the wheel suspension and the chassis spring or between the vehicle body and the chassis spring.

[Embodiments] In the following description, corresponding devices are designated by the same reference numerals in the drawings.

The pressure regulating device shown in FIG. 1 comprises a multi-stage axially extending main bore for the differential piston 2 and a connecting bore for the pressure fluid port 10 and the pressure fluid outlet 11. A housing 1 is provided. The regulating piston 2 consists of a valve carrier part 6 and a transfer piston 5 for the control force.

A transfer piston 5 of substantially cylindrical configuration projects into a large diameter stepped sleeve-shaped valve carrier part 6 in caulking relation and is screwed into the housing in a gas-tight manner so as to seal as a bearing. protruding into the closure member 16. The recess 8 of the valve carrier part 6 is provided with a spherical valve closing member 7 which is forced into contact with the inner end of the axial boat 19 of the valve carrier part 6. The valve seat and valve spring 18 are arranged adjacent to each other. Valve spring 18 @!
The end is supported by the transfer piston 5 and guided by a step 17 of the transfer piston 5 provided at the corresponding end.

The valve operation bin 20 is introduced into the boat 19 with enough time. The boat 19 has a transverse hole 2 communicating with it.
1 is provided vertically. Another Yokote boat 22
and via the main hole the recess 8 communicates with a connection boat 10 for the pressure fluid inlet. The valve carrier part 6 is removably arranged in the ring 23 and sealed to the housing 1 by a groove ring 24.

The groove ring 24 is locked via an annular disc 25 to which pressure is supplied via a spring 26, the other end of which is Il! It is supported by a ring 27 that is in contact with the F1wA member 1 and others.

The ring 27 has an inner diameter smaller than the outer diameter of the valve carrier part 6 and limits the return stroke of the adjusting piston 2 and acts as a stop for the front face 29 of the valve carrier part 6.

A ring-shaped sealant 28 that effectively seals between the transfer piston 5 and the closure member 16 is locked by the ring 27.

The valve operating pin 20 has a cup-shaped enlarged cross section at the end facing the valve closing member 7 and is coaxially locked by a correspondingly shaped recess in the valve carrier part 6 . The end of the graduated sleeve-type spring cup 30 on the opposite front surface of the connecting nipple 31 to the body canal 40 is in caulking relationship with the closure member 16. The outer bulge of membrane 34 forms a curved fold and circumferential pea 32.
and the front side of the closing member 16 are sealed and clamped.

The closing part 1 is closed by a radially enlarged piston @35.
The end of the transfer piston 5 protruding from 6 is fastened in cross section to the membrane center, which is reinforced and provided with a stepped hole opening towards the housing 1 . In order to support the membrane 34, an annular disc 36 is provided on the side of ll34 facing the closure member 16, which by means of its inner diameter is at the step of the transfer piston 5 with an outer edge slightly inclined towards 1I34. Supported. On the opposite side, pressure is supplied to the membrane 34 by a helical spring 37 whose other end is supported on the front side of the spring cup 30. Via a stepped structure in the center of the membrane and a flange 38 provided at the end of the connecting nipple 31 to connect to the inside of the front side of the spring cup 30, the helical spring 37 is guided centrally.

[The space between I34 and the closure member 16 is impervious to pressure fluid. Protected against the surroundings by an elastic ring,
A leakage boat 33 provided between the O-ring 28 and the membrane 34 of the closure part 16 monitors the density of the membrane 34 and sealant.

The control fluid conduit 40 is, according to FIG. 1, a flexible hose-type structure 45 and connected to a connecting part 42 of a load transfer element 50 provided between a receiving part 48 rigidly connected to the shaft and the molded part. Ru. The annular molded part 44 having a conical cross section has recesses each having a rectangular cross section on the upper and lower sides thereof, and these recesses are provided to fit the chassis spring 46 and the flexible hose 45 .

The recess operative to accommodate the hose is provided in its central part with an annular projection 47 of square cross-section which creates a pressure supply to the flexible hose 45 with a cross-sectional surface. According to FIG. 2, the load transfer member 50f consists of a flexible portion 52 and a base portion 53. A sleeve-shaped, ring-shaped flexible part 52 with two outer bulges is fixed to the platform element 53 by pressing. The side portion 55 of the base member 53 having a U-shaped cross section is connected to the chassis spring 4.
6 and operates to guide the flexible portion 52 longitudinally. The flexible portion 52 is the chassis spring 42
is deflected by the intermediate plate 54 with an annular receptacle to accommodate the chassis spring 46. At the same time, the receiving part forms a defined pressure supply surface for the flexible part 52. The axially curved outer edge of the intermediate plate 54 surrounds the outer side 55 of the platform portion 53. The platform portion 53 is rigidly connected to the shaft and the receiver is connected to the portion 48. Attached to the end facing the transfer member 50 is a connecting member 42 provided with a flange.
are guided through a common coaxial boat.

The embodiment of the load transfer element 50 according to FIG. 3 is suitable for mounting on the spring stem of a car spring. To this end, the receiver member 48 has an annular structure and is welded to the spring stem 60. The carrier portion 63 is axially folded back at its inner flange to surround the spring stem 60 and the receiver is attached to the member 48.
The axially folded outer flanks are operative to guide the flexible portion 52 . It is introduced into the carrier part 63 and is attached in the form of a sleeve by the ring 61.
The flexible portion 52 curved through is maintained with two attachment bulges. The force of chassis spring 46 passing through intermediate plate 54 and spring guide ring 64 is guided by flexible portion 52 .

Intermediate plate 54 comprises a portion of circumferential rectangular cross section forming a pressure supply surface for flexible portion 52 . A ball-shaped spring guiding the ring 64 contacts the intermediate plate 54 and is movably guided along the inner side of the carrier part 63 through the guide cap 65 .

To enhance the axial sliding movement of the guide cap 65 of the carrier part 63, the sliding surface is provided with an annular circumferential groove.

A peripheral groove cut into the front face of the transfer cap accommodates a spring guide ring 64 that partially surrounds the lower end of the chassis spring by its radiused outer portion.

According to an advantageous form of embodiment of the invention, the load transfer member 5
0 are respectively provided on the two spring stems of the rear axle of the motor vehicle, and the load transfer elements 50 are connected via one control fluid line 40 in such a way that they are one regulator. At the beginning of the braking operation, the valve closing member 7 is opened through the valve operating pin 20, and at this time joins with the housing 1;
This ensures that the pressure fluid initially flows from the pressure fluid inlet 10 to the pressure fluid outlet 11 without obstruction. Based on the difference in the pressure supply surface of the regulating piston 2, the valve operating pin 20
With increasing input pressure against the force of the helical spring 37, the regulating piston 2 Moving.

In the next control phase, the initial pressure is reduced at the regulating piston 2 opposite the inlet pressure associated with the pressure supply surface.

Depending on the load on each axis, the pressure of the control pressure fluid from the control fluid pipe 40 is added to the force of the helical spring 37 and supplied to the adjusting piston 2 . This pressure of the control pressure fluid causes the change point of the pressure regulator to vary with load. Additional pressure while the vehicle is under load is applied via the force of chassis springs 46 to flexible hose 45 and flexible portion 5.
It is generated by compression of the capacity of 2. Connection member 42 and v
Said pressure through the 1wJ fluid line 40 is sent to g34, the number regulating piston 2, thereby raising the change point of the pressure regulating device.

[Brief explanation of the drawing]

FIG. 1 shows a pressure regulating device according to the invention, and FIGS. 2 and 3 show another type of embodiment of the load transfer element and its fixing to the chassis. 2... Adjustment piston, 34... Membrane, 40... Pressure fluid pipe, 42... Connection portion, 44... Mold member, 45... Flexible hose, 46... Chassis spring, 50 ... Transfer element, 52 ... Elastic part, 53
...Installation is partial.

Claims (5)

[Claims] (1) A housing provided with a regulating piston between a pressure fluid inlet and a pressure fluid outlet, the control force supplied to said regulating piston being protected between two mutually movable members, in particular an axle and a cushion. In a pressure regulating device which is proportional to the load between the vehicle bodies, the generation and transfer of the control force is caused by a control pressure fluid, so that the load, in particular the wheel load, is supplied to a load transfer element which can vary in capacity. , a pressure regulating device, characterized in that it communicates with a pressure fluid conduit that allows the control force to be transferred from the transfer element to the regulating piston. (2) characterized in that the load transfer element is in the form of a flexible hose, the load is supplied to said hose through a molded part, in particular a chassis spring, and a connection part for the control fluid pipe is provided on the flexible hose; A pressure regulating device according to claim 1. (3) Pressure regulating device according to claim 1 or 2, characterized in that the control pressure fluid is preferably sealed by a membrane. (4) that the load transfer member, consisting of an open elastic part and a mounting part, communicates in a gas-tight manner with one of the transferable parts relative to each other, in particular with a cushion-protected body or with an axle; A pressure regulating device according to any one of claims 1 to 3. (5) The capacity of the load transfer element is very large compared to the capacity formed by the product of the diameter of the adjusting piston and the displacement of the adjusting piston. The pressure regulating device according to any one of the items.