JPS5977134A - Brake gear - Google Patents

Abstract

(57) [Summary] This bulletin contains application data before electronic filing, so abstract data is not recorded.

Description

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

[Prior art]

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

The chamber containing the brake disc is separate from the chamber carrying out the piston operation, and this presents considerable disadvantages. That is, the diameter U of the brake release piston
11. Since it is relatively small, it is necessary to provide an initial braking control spring with a relatively small return force in order to be able to release the brake at a predetermined pressure. 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 a trivial task. This is because it is necessary to increase the dimensions of various parts.

[Object of the present invention]

An object of the 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, the brake device based on the present invention includes a frame; and a rotating part such as a shaft that extends in the axial direction of the frame and rotates relative to the frame around its own axis. a housing fluid-tightly coupled to the frame; a housing fluid-tightly disposed on the housing and forming a closed chamber with the housing;
a cover disposed within the closure chamber transverse to the axis of the rotating member and movable axially towards one of the rotating member and the frame; at least one brake disc disposed circumferentially immovable within said cold chamber and axially movable in parallel to said brake disc and relative to the other of said rotating member and said frame; the cover is fixed in the circumferential direction and engages the brake disc for braking or moves away from the brake disc for braking release as the portion of the cover is moved axially; at least one brake lining configured to engage the brake lining with the brake disc between the portion of the cover and one of the rotating member and the frame; a resilient biasing element, i.e. a compression spring, provided to bias the portion; a pressurized fluid introduced into the housing facing the cover in a direction opposite to the biasing direction of the resilient biasing element; a brake release chamber configured to move the portion of the housing in a direction opposite to the biasing force; and a control release pressurized fluid source connected to the brake release chamber. (b) Further, the brake release chamber and the closure chamber are always communicated, and a sealing member is provided between the rotating member and the combination of the frame and the housing, and at least a portion of the cover (n1) is released from the control. The chamber is configured to be a piston.

[Detailed description of the invention]

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

The brake device shown in FIGS. M1 through FIG. 6 has a structure in which it is provided to rotate with respect to the frame 2 in rotations 11113 and performs braking.

In these examples, the frame 2 is the frame 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;
This is in contact with a plane 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 the housing 2
is held in a plane 5 to make the composite contact surface 9 of the housing 4 and frame 2 fluid-tight.

In the six embodiments used to explain the invention, the housing cover 4 is hollow, and as shown in FIGS. 1 to 3 and FIG. ) is closed by 10, Figures 4 and 5.
It is closed by both the cover 10 and elastic washers 46,47 as shown. Therefore, the occlusion chamber 1
1 is formed in the housing 4, in which chamber 11 a brake disc 12 rotating with the shaft 1 is provided with a lining 13 formed on the inner wall of the housing 4 so as not to rotate in the circumferential direction. There is. The brake discs 12 are arranged side by side sequentially in the axial direction as in the known art, and each lining 13 is interposed between two adjacent brake discs 12, and the linings 13 are interposed between two adjacent brake discs 12. The 130 pairs of linings start and end with lining.

The crown 214 on the crown-shaped cover 1θ faces and is supported by the lining 13 at one end of the brake disc and lining pair. Section 1.2.4
As shown in FIGS. and 6, 16 is a hole 16 formed in the end of the housing 4 opposite to the plane 5, and its central axis is the axis 3. The cover 10 is installed in the hole 16 by sliding its outer peripheral edge 16 against the inner wall of the hole 16 in the axial direction. A sealing member 17 is provided between the inner wall of the hole 16 and the outer peripheral edge 15 of the cover 10 to fluid-tightly seal the space between them.

In the embodiment according to FIGS. 1 and 2, a compression spring 18 consisting of a disk washer is secured to the outer surface 19 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. are in contact. The effect of spring I8 is
Brake disc 12 and brake lining 4713
This is to prevent the shaft 1 from moving in the axial direction relative to the housing 4 (and therefore relative to the frame 2) while eliminating play between the shaft 1 and the housing 4 and holding each other together.

In the embodiment of FIGS. 2 and 6, the shaft 1 passes through a central opening 22 in which the cover 10 is provided.

An annular seal member 23 is provided between the shaft 1 and the cover 10,
A fluid-tight seal is established between these parts.

In the embodiment of figure M4, the shaft 1 passes through a central opening 37 in the cover 10, which is so large that it is not possible to provide a seal between it and the shaft 1. It has a cavity 38. A ring member 39 is provided coaxially with the shaft 1 by a piece 4o inserted into a groove 4 in the shaft 1. For example, Ml, I type elastic washer 4
6 is inserted into the groove 43 in the shaft and held on the cover 10 by the cutting piece 42tlC, and an annular seal 44 is provided between the ring member 39 and the shaft 1 and between the elastic washer 46 and the cover 10, respectively. 46 is provided for engaging the cover 10 with the brake lining 13.

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 of FIGS. 2 and 3,
The cover 10 has an opening in the housing 4 (center opening)
is completely occluded. On the other hand, in FIG. 5 the cover 10 only occupies the central part of the (center) opening, the other part holding the cover 10 engaging the brake lining 13. It is closed by an elastic washer 47. For this purpose, the elastic washer 47 is inserted into the piece 4 pushed into the groove 49 in the opening in the housing 4.
8. For liquid-tight sealing, two seal members 50, 51 are interposed between the washer 47 and the cover 10, and between the washer 47 and the cover 10, respectively.

In the embodiment of FIG. 6, the shaft 1 passes through 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, urging the cover 10 into engagement with the brake lining 13 and creating no fluid tight seal between the washer 18 and other parts. This eliminates the need for a seal on the side for stopping.

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

@V, In the embodiments of Figures 2.3 and 5, union 2
5 extends into a peripheral chamber 26 within the housing 4 and selectively connects the occlusion chamber 11 to a pump 27. Here, the peripheral chamber 26 and the closed chamber 11 are in constant communication and constitute two parts of one and the same chamber.

The suction duct 35 of the pump 27 is connected to a pressureless fluid reservoir 28 , and the discharge duct 29 of the pump 27 is connected to a fluid distributor 30 .

A duct 31 connects the distributor 30 to the laser nozzles 28, and another duct 32 connects the discharge duct 29 to the laser 28 and to a constant pressure discharge valve (relief valve) 33 located in the duct 32. duct) 34 tit, divider 30 into union 2
Connect to 5.

The distributor 30 has three positions as follows.

The first position II1 connects the ducts 29.34 and closes the duct 3; the second position connects the ducts 29.31 and closes the duct 34; the third position
．． 31 and 34 are connected to each other.

It consists of a pressurized fluid supply device IL, a pump 27, a laser pump 28, and a distributor 30, and is also used in the embodiments shown in FIGS. 4 and 6, but since it uses the same equipment as that in FIG. is not shown. However, there is a slight difference that the duct 34 is formed within the shaft 1 and the chamber 11 (fourth
In the figure, the area of the cavity 38 of this chamber 11)
It is connected to a duct 54 which extends directly into the interior.

In the embodiments shown in FIGS. 1.2, 4.5 and 6, the cover 10 is highly rigid and does not substantially deform, and its zest 14 absorbs the elastic force of the elastic washer (18° 4e, 4v). It engages only one of the brake linings 13 by means of the brake lining 13.

In the embodiment of FIG. 3, the cover 10 is elastic in the axial direction, so that the cover 10 can be braked.
It becomes a compensating spring that biases and engages one of the linings 13. Therefore, there is no need to provide a separate spring 18. Of course,
An element that exhibits an elastic function, that is, an element that holds the outer peripheral edge of the cover 10 on the housing 4, that is, a holding piece 2
It is still necessary to provide 0 and 21. It is preferable to form a hole in the free end of the housing 4 so that the outer peripheral edge of the cover 10 can be attached to the housing 4 without any further sliding. Further, a fluid-tight (incompressible) seal member 36 is interposed between the haw and kung 4 and the outer peripheral edge of the cover 10.

As shown in both embodiments, the housing 4
are separate from the frame 2, and are assembled via the seal member 8. Equivalents to these assemblies can be manufactured in which the mounting 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, chambers 71 and 26 must be in constant communication;
That is, because these channels are combined into one chamber, the brake release fluid coming from the pump 27 when the distributor 30 assumes the first position is transferred to the first, second, and second positions.
In the case of Figures 3 and 6, it acts on the entire cross-sectional area of the cover 10,
In the case of Fig. 4.5, the elastic washer 46.47 part (
section), i.e., the sum of both sections, but these whole sections and the sum of both sections are obviously the same as the brake release piston of the prior art brake device. It is larger than the pressure receiving area of .

Therefore, in the present invention, not only can brake release be performed using the same fluid pressure as used in known brake devices, but also a fluid pressure lower than this fluid pressure can be used. When using fluid pressure of the same pressure as the known brake system, the spring used in the known brake system has a larger role (F+j
Since springs 18, 46, 47 with force can be used, the brake release force is greater than in the prior art. Also, on this occasion,
The braking force is increased (compared to the conventional one). On the other hand, by maintaining the same braking force and therefore the same brake release force as in the conventional system, it is also possible to use a brake release pressure that is υ lower than in the conventional system.

The above advantages are realized if the shaft 1 passes through the forceps 10, as shown in FIG. 1.4.6. Second.
This advantage is even more pronounced if, as in Fig. 3.5, the cover 10 does not penetrate the cover 10 and the entire area therefore acts as a brake release piston.

The sealing member 24 also makes it possible to isolate the chamber 1 from the mechanisms within the frame 2. Therefore, in the present invention, the mechanism contained in (or protected by) the frame 2 is free from freezing and braking in the chamber 11.
There is no risk that the particulate abrasive coming out of the lining or the brake disc or both will be contaminated by suspended fluid (oil). This means that the frame
This is particularly important when the frame of a hydraulic motor is strong and resistant to contamination during operation. Furthermore, since braking oil and motor oil are isolated from each other, these oils
It can be made according to each purpose and function.

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

Since the outer surface 19 of the cover 10 is in free communication with the atmosphere, the brake release opening force bar 10 is exposed to counter pressure.
r 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 drawings]

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...times 11ii [
, 4... Housing, 5, 6... Plane, 7... Screw, 8... Seal member, 9... Composite contact surface, 10...
... (Housing) Cover, 1 No. (Occluded) Chamber, 12... (Brake) Disc, 13...
(Brake) Lining, 14...Zess, 15...
・Outer peripheral edge, 16... Hole, 17... Seal member, 18
... (compression) spring, 19 ... outer surface, 20 ... holding piece, 21 ... groove, 22 ... center opening, 23.2
4... Annular seal member, 25... Union, 26...
... Peripheral chamber, 27... Pump, 28... Reservoir, 29... Discharge duct, 30... Fluid distributor 1
．． ? 7, j 2...Duct, 33...Low pressure discharge valve1. ? 4, J5...duct, 36...
Seal side 1. ? 7... Central opening, 38... Gap, 39... Ring portion, 40... Piece, 41...
Groove, 42... Piece, 43... Groove, 44.45... Annular seal member, 46.47... Elastic washer, 48...
... Piece, 49... Raku, 50.51... Seal member,
52...piece, 53 groove, 54...duct. Applicant's agent Patent attorney Takehiko Suzue One-page engraving (with no changes to the content) Figure 2 Figure 3 Figure 4 Figure 5 Figure 6 FA Procedural amendment (Honoki Showa q. 11° 6) Yasuo Wakasugi, Commissioner of the Japan Patent Office 1. 11 Indication Special Patent No. 1 Sho 58-125627 2, Name of the Invention Brake Device 3, Relationship with the Amendment Person Case Patent Applicant Declan Idrolic 4, Agent (2) Isai of the drawing (no history in the self-answer)

Claims (12)

[Claims] (1) A frame, a rotating member extending in the axial direction of the frame and rotating relative to the frame about its own axis, a housing fluid-tightly coupled to the frame, and a rotating member extending in the axial direction of the frame, a cover disposed in close contact with the housing to form a closed chamber and at least partially movable in the axial direction of the frame; at least one brake disc fixedly disposed in the circumferential direction on one of the brake discs;
a brake disc disposed in the closed chamber parallel to the brake disc and circumferentially immovable on the other of the rotary member and the frame for braking in response to axial movement of the portion of the cover; at least one brake lining that engages the brake disk or moves away from the brake disk for brake release, and between the portion of the cover and one of the rotating part and the frame; a resilient biasing element configured to bias the portion of the cover in a direction to engage the brake lining with the brake disc; and a resilient biasing element within the nozzing. a brake that faces the cover in a direction opposite to that and is provided with a pressurized fluid introduced therein to move the portion of the nozzling in a direction opposite to the biasing force against the biasing force of the elastic element; It comprises a release chamber/J and a pressurized fluid source for brake release to which the brake release chamber is connected, the brake release chamber and the closing chamber are always communicated, and the rotation member, the frame, and the housing are connected to each other. A brake device characterized in that a seal portion side is provided between the combinations, and at least a portion of the cover serves as a piston of the brake release chamber. (2) The brake device according to claim 1, wherein a hole is formed at one end of the housing to slidably attach the outer peripheral edge of the cover in a fluid-tight manner. (3) The brake device according to claim 2, wherein the cover is rigid, and the elastic biasing element is separate from the cover. (4) The rotating member extends through the cover, the elastic biasing element is provided between the rotating member and the force/gut, and the elastic biasing element is provided between the inner wall of the hole and the cover. 4. The brake device according to claim 3, further comprising a sealing member. (5) The brake device according to claim 4, wherein a sealing member is provided between the rotating member and the cover. (6) The pressurized fluid source is connected to the cooling channels through a path J1 formed within the rotating member and between the rotating member and the cover, and the elastic biasing element is connected to the rotating body. 5. The brake device according to claim 4, wherein the brake device is at least one annular elastic washer provided with a seal member between the brake device and the cover. (7) The brake device according to claim 3, wherein the elastic biasing element is provided between the housing and the cover. (8) The brake device according to claim 7, wherein the cover has no holes. (9) The cover has an outer surface at a central portion, and the elastic biasing element is an annular elastic washer provided between the cover and the housing. Brake device according to scope 7 or 8. (10) The brake device according to claim 7, wherein the rotating member passes through the cover, and has a sealing member between the rotating member and the cover. (11) A patent claim characterized in that the cover is an axially elastic element whose outer peripheral part is held and fixed to the housing by a holding means and whose central part is movable with respect to the outer peripheral part. The brake device according to item 1 of the scope. (12) The brake device according to claim 11, wherein the elastic biasing element is constituted by the force.