JPH0457902B2 - - Google Patents

Description

DETAILED DESCRIPTION OF THE INVENTION [Technical Field of the Invention] The present invention relates to a brake device, and particularly to a disc brake device with a hydraulically controlled brake release device.

[Prior art]

Conventionally, multi-disc brakes have been known in which braking is performed mechanically by the action of a return spring and the braking is released by pressurized fluid. a second chamber containing a spring necessary for mechanical braking and communicating with the atmosphere; having a pressure greater than said first chamber, separated by a brake piston, and providing hydraulic brake release during operation; It has a third chamber that allows

The chamber containing the brake disc is separate from the chamber that carries out the piston operation, and this presents considerable drawbacks: the diameter of the brake release piston is relatively small, so that the brake cannot be released at a given pressure. In order to be able to
It is necessary to provide an initial brake control spring with a relatively small return force. However, unless the diameter of the brake release piston, and therefore the space occupied by the brake, is increased, the desired brake may be insufficient. Increasing the pressure itself is not an easy task. This is because it is necessary to increase the dimensions of various parts.

[Object of the present invention]

An object of the present invention is to provide a brake device that eliminates the problems of known brakes and has a simplified structure.

[Configuration of the present invention]

In order to achieve the above object, a brake device based on the present invention includes: a frame; a rotating member such as a shaft extending in the axial direction of the frame and rotating relative to the frame around its own axis; a housing fluid-tightly coupled to the frame; a cover fluid-tightly mounted to the housing and forming a closed chamber with the housing, at least a portion (e.g. a boss) being movable in the axial direction of the frame; at least one plate disposed within the closure chamber transverse to the axis of the rotating member and mounted on one of the rotating member and the frame, movable axially but immovable circumferentially; a brake disk of said cover, disposed in said closed chamber parallel to said brake disk and on the other of said rotating member and said frame, movable axially but immovable circumferentially; at least one brake lining adapted to engage said brake disc for braking or move away from said brake disc for braking as said portion is moved axially; said cover; a resilient biasing element disposed between the portion of the cover and one of the rotating member and the frame to bias the portion of the cover in a direction to engage the brake lining with the brake disc; a compression spring; a pressurized fluid is introduced into the housing facing the cover in a direction opposite to the biasing direction of the resilient biasing element to move the portion of the housing in a direction opposite to the biasing force; a brake release chamber provided in such a manner; and a pressurized fluid source for brake release to which the brake release chamber is connected; a sealing member is provided between the rotating member and the frame and housing combination, and at least a portion of the cover is configured to be a piston of the decontrol chamber.

[Specific description of the invention]

Hereinafter, the present invention will be explained based on specific examples thereof with reference to the drawings.

The brake device shown in FIGS. 1 to 6 has a structure in which a shaft 1 provided to a frame 2 so as to rotate around a rotation shaft 3 performs braking. In these examples, the frame 2 is the body of a hydraulic motor, and the shaft 1 is an extension of the shaft of this hydraulic motor.

The housing 4 of the brake device has a flat surface 5 which adjoins a flat surface 6 at one end of the frame 2 . The housing 4 is fixed to the frame 2 with screws 7. A seal 8 is provided in a groove in the frame 2 and is retained against the flat surface 5 of the housing 2 to provide a composite contact surface 9 between the housing 4 and the frame 2.
is fluid-tight.

In the six examples used to explain the invention:
The housing 4 is hollow and is closed by a housing cover (hereinafter simply referred to as cover) 10 as shown in FIGS. As shown, it is closed by both the cover 10 and elastic washers 46, 47. Thus, a closed chamber 11 is formed in the housing 4, in which a brake disc 12 rotating with the shaft 1 is located.
It is provided on the inner wall of the housing 4 together with a lining 13 formed so as not to rotate in the circumferential direction. The brake discs 12 are arranged one after the other in the axial direction, as is known in the art.
Each lining 13 is interposed between two adjacent brake discs 12, and each lining 13 is interposed between two adjacent brake discs 12.
The set of disk 12 and lining 13 starts and ends with the lining.

The boss 14 on the crown-shaped cover 10 faces and is supported by the lining 13 at one end of the brake disc and lining pair. As shown in Figures 1, 2, 4 and 6, 1
Reference numeral 6 denotes a hole 16 formed in the end of the housing 4 opposite to the plane 5, the central axis of which is the shaft 3.
The cover 10 is installed inside the hole 16 by sliding its outer peripheral edge 15 against the inner wall of the hole 16 in the axial direction. Inner wall of hole 16 and outer peripheral edge 1 of cover 10
5, a sealing member 17 is provided between them to provide a fluid-tight seal.

In the embodiment of FIGS. 1 and 2, a compression spring 18 consisting of a dish-shaped washer is secured to the outer surface of the cover 10 by means of a retaining piece 20 inserted and fixed in a groove 21 formed in the free end of the housing 4. It is in contact with 19. The effect of the spring 18 is to eliminate the play between the brake disc 12 and the brake lining 13 and to hold the shaft 1 relative to the housing 4 (and therefore relative to the frame 2) against each other. The goal is to not move in any direction.

In the embodiments of FIGS. 1 and 6, shaft 1
is the central opening 22 in which the cover 10 is provided.
penetrates through. An annular seal member 23 is provided between the shaft 1 and the cover 10 to provide a fluid-tight seal between them.

In the embodiment of FIG. 4, the shaft 1 is connected to the cover 1
0, which has a gap 38 so large that no sealing member can be provided between it and the shaft 1. A ring member 39 is mounted coaxially to the shaft 1 by a piece 40 inserted into a groove 41 in the shaft 1 . For example, a dish-shaped elastic washer 46 is attached to the cover 10 by means of a piece 42 inserted into a groove 43 in the shaft 1.
Further, annular seals 44, 45 are provided between the ring member 39 and the shaft 1 and between the resilient washer 46 and the cover 10, respectively, for engaging the cover 10 with the brake lining 13. It's getting old.

In the embodiment of FIGS. 2, 3 and 5, the cover 10 is without a hole and the shaft 1 does not pass through it. In the embodiment shown in FIGS. 2 and 3, the cover 10 completely closes the opening in the housing 4 (the central opening). On the other hand, in FIG. 5, the cover 10 is (center)
It occupies only the central part of the opening, the other part being closed off by an elastic washer 47 holding the cover 10 in engagement with the brake lining 13. For this purpose, the elastic washer 47 is held by a piece 48 inserted into a groove 49 in an opening in the housing 4 . Two seal members 50 and 51 are interposed between the washer 47 and the cover 10 and between the washer 47 and the cover 10, respectively, for liquid-tight sealing.

In the embodiment of FIG. 6, the shaft 1 is connected to the cover 10.
and is made fluid-tight by a sealing member 23. The elastic washer 18 is supported by a piece 52 inserted into a groove 53 in the shaft 1, and the cover 10
is biased into engagement with the brake lining 13, eliminating the need for any fluid-tight seal between the washer 18 and other parts.

In each embodiment, the shaft 1 passes through the frame 2, with a (annular) sealing member 24 in between. The closure chamber 11 is therefore completely isolated from the outside.

In the embodiment of FIGS. 1, 2, 3 and 5, the union 25 is connected to the peripheral chamber 2 in the housing 4.
6 and selectively connects the occlusion chamber 11 to a pump 27 . Here, the peripheral chamber 26 and the closed chamber 11 are always in communication and constitute two parts of one and the same chamber.

The suction duct 35 of the pump 27 is connected to a reservoir 28 for pressure-free fluid;
The discharge duct 29 of 7 is a fluid distributor (distribution valve) 3
Connected to 0. A duct 31 connects the distributor 30 to the reservoir 28 and another duct 32 connects the discharge duct 29 to the reservoir 28 and to a constant pressure discharge valve (relief valve) 33 located in the duct 32. A duct 34 connects the distributor 30 to the union 25.

The distributor 30 has three positions as follows. The first position connects the ducts 29 and 34 and cools the duct 31; the second position connects the ducts 29 and 34 to cool the duct 31;
The third position is the one that allows the ducts 29, 31 and 34 to communicate with each other and closes the duct 34.

The pressurized fluid supply device includes a pump 27 and a reservoir 2.
8 and a distributor 30, which are also used in the embodiments of FIGS. 4 and 6, but are not shown in FIGS. 4 and 6 because they are similar to those of FIG. 1.
However, there is a slight difference in that the duct 34 is
It is connected to a duct 54 which extends directly into the chamber 11 formed therein (in FIG. 4, in the area of the cavity 38 of this chamber 11).

In the embodiment of FIGS. 1, 2, 4, 5 and 6, the cover 10 is highly rigid and substantially undeformable, and the boss 14 is formed by elastic washers 18, 4.
6, 47 engages only one of the brake linings 13.

In the embodiment of FIG. 3, the cover 10 is elastic in the axial direction, so that the boss 1 of the cover 10
4 becomes a compensating spring that biases and engages one of the brake linings 13. Therefore, the separate spring 18
There is no need to provide Of course, it is still necessary to provide elements that exhibit an elastic function, that is, elements that hold the outer peripheral edge of the cover 10 on the housing 4, that is, the holding pieces 20 and the grooves 21. A hole is formed in the free end of the housing 4 and a cover 10 is placed.
It is preferable to attach the outer peripheral edge of the housing 4 to the housing 4 without sliding it any further. Further, a fluid-tight (incompressible) sealing member 36 is interposed between the housing 4 and the outer peripheral edge of the cover 10.

As shown in both embodiments, the housing 4 is separate from the frame 2, and these are assembled via the seal member 8.
Equivalents to these assemblies can be manufactured in which the housing is integral with the frame.

[Advantages of the present invention]

Below, the advantages of the brake device based on the present invention will be described.

First, because chambers 11 and 26 are in constant communication, that is, because they are combined into one chamber, distributor 30
The brake release fluid coming from the pump 27 when the pump assumes the first position acts on the entire cross-sectional area of the cover 10 in the cases of FIGS. 1, 2, 3 and 6, and in the cases of FIGS. Section of elastic washers 46, 47
acts on the section of the cover 10 compensated by, i.e. the sum of both parts,
These total cross-sectional areas and the sum of both parts are clearly larger than the pressure-receiving area of the brake release piston of prior art brake systems.

Therefore, in the present invention, not only can brake release be performed using fluid pressure at the same time as in a known brake device, but also a fluid pressure lower than this fluid pressure can be used. When using a fluid pressure similar to that of the known brake system, the spring 18 has a greater return force than the spring used in the known brake system;
46 and 47 can be used, the brake release force is larger than that of the conventional one. Also, in this case, the braking force is increased (compared to the conventional one). On the other hand, maintaining the same braking force and therefore the same brake release force as in the conventional one, it is also possible to employ a lower brake release pressure than in the conventional one.

As shown in Figures 1, 4 and 6, shaft 1 is connected to cover 1.
If it passes through 0, the above advantages are recognized. As shown in Figures 2, 3 and 5, shaft 1 is connected to cover 1.
This advantage is even more pronounced if it does not penetrate 0 and therefore the entire area acts as a brake release piston.

As in the present invention, the cover member is directly biased against the brake lining to perform braking, and the brake is released by applying fluid pressure to the cover member. , the axial volume of the braking device is reduced,
The configuration is simple and lightweight.

The seal member 24 also makes it possible to isolate the chamber 11 from the mechanisms within the frame 2. Accordingly, in the present invention, a mechanism contained (or protected) in the frame 2 is contained in the chamber 11 and in which particulate abrasive coming from the brake lining or the brake disc or both is suspended. There is no risk of contamination from the fluid (oil) being used. This means that the frame
This is particularly important in the case of hydraulic motor frames that cannot withstand contamination during operation. Furthermore, since the braking oil and the motor oil are isolated from each other, these oils can be used in accordance with their respective uses and functions.

The embodiment of FIG. 3, in which the cover 10 also performs an elastic compensating action, has the advantage of simplicity.

Since the outer surface 19 of the cover 10 is in free communication with the atmosphere, the cover 10 can be displaced during debraking without being subjected to counter pressure.

In operation, the volume of the chamber 11 is equal to the volume of oil that the brake piston displaces during operation, thus reducing the response time of the brake system during braking and release.

Moreover, the operation of the brake is completely independent of the operation of other structures on which it is installed.

[Brief explanation of the drawing]

FIG. 1 is a vertical cross-sectional view of the main part of one embodiment of the brake device according to the present invention, together with its hydraulic control circuit, and FIGS. 2 to 6 are views of other embodiments of the present invention. FIG. 3 is a vertical sectional view of the main part. 1...Axis, 2...Frame, 3...Rotation axis, 4
...housing, 5, 6...plane, 7...screw,
8... Seal member, 9... Composite contact surface, 10...
(Housing/) Cover, 11... (Closing) Chamber, 12... (Brake) Disc, 13...
...(brake) lining, 14...boss, 1
5... Outer periphery, 16... Hole, 17... Seal member, 18... (compression) spring, 19... Outer surface, 2
0... Holding piece, 21... Groove, 22... Central opening, 23, 24... Annular seal member, 25... Union, 26... Peripheral chamber, 27... Pump, 28... Reservoir, 29... ...Discharge duct, 3
0...Fluid distributor, 31, 32...Duct, 33
...Low pressure discharge valve, 34, 35...Duct, 36...
... Seal member, 37 ... Center opening, 38 ... Gap, 39 ... Ring member, 40 ... Piece, 41 ...
... Groove, 42... Piece, 43... Groove, 44, 45...
Annular seal member, 46, 47... elastic washer,
48... piece, 49... groove, 50, 51... seal member, 52... piece, 53... groove, 54... duct.

Claims (1)

[Scope of Claims] 1. A rotating member 1 that rotates about its own axis 3 relative to a frame 2; and a housing 4 that is integral with the frame 2 and is in fluid tight condition with the frame. a cover 10 , which is fluid-tightly attached to this housing, forms a closed chamber 11 with the housing, and is axially movable with respect to said frame 2;
10-46, 10-47, and at least one member arranged across the axis of the rotating member 1 and rotating integrally with the rotating member 1.
at least one brake lining 13 arranged alternately opposite the at least one brake disc 12 in the closed chamber 11 and making it possible to brake a rotary member; integral with the cover; a contact portion 14 of the cover that is formed to engage the brake lining 13 as the cover moves; and a contact portion 1 of the cover that extends in the direction of engaging the brake lining 13 with the brake disc 12.
4, elastic biasing elements 18, 46, 47 provided between the cover and one of the rotary member and the frame; and in the housing opposite to the biasing direction of the elastic biasing elements. a brake provided to introduce pressurized fluid in a direction facing the cover and move the abutment portion 14 of the cover in a direction opposite to the biasing force against the biasing force of the elastic biasing element; Liberation chamber 26
and a pressurized fluid source for brake release selectively connected to the brake release chamber, (a) constantly communicating the brake release chamber 26 and the closed chamber 11, (b) A sealing member 2 is provided between the rotating member 1 and the combination of the frame 2 and the housing 4.
4, and (c) a piston of the brake release chamber is formed by at least a portion of the cover 10. 2. The brake device according to claim 1, wherein a hole 16 is formed at one end of the housing 4 for fluid-tightly sealing the outer peripheral edge 15 of the cover 10. 3. The brake device according to claim 2, wherein the cover is rigid and the elastic biasing elements 18, 46, 47 are separate from the cover. 4 The rotating member 1 passes through the cover, the elastic biasing elements 46 and 18 are provided between the rotating member 1 and the cover 10, and the hole 16
Claim 3, characterized in that an annular seal member 17 is provided between and the cover 10.
Brake device as described in Section. 5 A passage 3 between the rotating member 1 and the cover 10
8 is formed, and the elastic biasing element is at least one annular elastic washer 46 provided with sealing members 44, 45 between it and the rotary member 1 and between it and the cover 10. A brake device according to claim 4. 6. The brake device according to claim 4, wherein a seal member 23 is provided between the rotating member 1 and the cover 10. 7. The brake device according to claim 3, wherein the elastic biasing elements 18, 47 are provided between the housing 4 and the cover 10. 8. The brake device according to claim 7, wherein the cover 10 is not perforated. 9. The cover 10 has an outer surface at a central portion, and the elastic biasing element is an elastic washer having seal members 51, 50 between the central portion and the housing. A brake device according to claim 7. 10 The rotating member 1 passes through the cover 10, and an annular seal member 2 is provided between the rotating member 1 and the cover 10.
Claim 7 characterized in that it has 3.
Brake device as described in Section. 11 The cover 10 has a holding member 20 whose outer peripheral portion engages with a groove 21 formed in the housing 4.
2. The brake device according to claim 1, wherein the brake device is an axially elastic element which is held and fixed to the housing 4 by a central portion and whose central portion is movable relative to the outer peripheral portion. 12. Claim 11, wherein the elastic biasing element is constituted by the cover 10.
Brake device as described in Section.