JPS61112834A - Braking unit - 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 (Field of Industrial Application) The present invention relates to a braking unit, and more specifically to a brake unit that has a center hole and is attached to the circumferential surface of the center hole to rotate with respect to an object. The present invention relates to an improvement of a brake unit having a retaining surface for holding two parts and a plurality of grooves formed in the circular ff6 planes on both sides of the brake disc.

(Prior art) A brake unit as described above is disclosed in German Patent No. 230.
The one disclosed in No. 8256 is known. )-■ of this braking unit are structurally shallow and run in the form of mutually eccentric rings. This known type is for both φ1 use, and the groove must exclude water during IJf.

Further, German Patent No. 1202153 discloses a braking unit with transparent grooves, which extend from one friction surface to the other and divide the brake disc into several parts. . But with this one, aSI! Since the strength is greatly reduced by I, there is a drawback that the number of transparent channels is reduced by fjl. As a result of providing the through groove, the bearing capacity with respect to rotational speed and braking moment is reduced.

Furthermore, U.S. Patent Nos. 3171527 and 349308
No. 7 and German Patent No. 674,759, etc., introduce the so-called split-type braking block in order to obtain higher braking output and reduce the deformation of the brake disc due to temperature rise while braking is still in progress. has been done.

However, this type has the disadvantage of relatively high manufacturing costs.

(Objective of the Invention) The present invention aims to improve the load bearing capacity of the braking unit and to improve operational reliability.

The simple structure of the braking unit is required to minimize deformation due to temperature rise that occurs during braking operation. This deformation is particularly likely to occur in so-called full-length braking units because the braking layer extends over the entire circumference of the circular friction surface.

In addition, such deformation also leads to the fact that in the case of a worn brake mechanism, the brake layer is constantly in contact with the brake disc. If the deformation becomes severe, a significant pressing force will be generated in some parts, leading to local temperature rise and destruction of the brake disc, so the present invention aims to eliminate such inconveniences.

(Basic Structure of the Invention) In the present invention, one circular friction surface is divided into a plurality of segments in the circumferential direction by each extending from the inside in the radial direction to the outside of the circular friction surface.

(Embodiment) In Fig. 1.2, the braking unit l of the present invention has a center hole 2, and the circumferential surface of the center hole 2 is used to lock the braking unit in rotation with respect to the object to be mounted. A tooth-shaped engagement surface 3 is formed. The braking unit 11 has circular friction surfaces 7, 9 on both sides thereof, and grooves 11 formed in these surfaces
．． 13 each run from the radially inside to the outside of the circular friction surface 79. These grooves 11.13 are
It deviates from the same radial direction, and moreover, within each circle 19, it is inclined #J in the same circumferential direction.

That is, one circular Pi! The grooves 11 in the friction surface 7 are oriented in the opposite direction to the grooves 13 in the other circular friction surface 9, and the two intersect in pairs.
No. 1 of the groove 11.13 of the friction surface 7.9 (the remaining disk 1'X21 between the surfaces 23.25 is at most 70% of the axial disk thickness 27 measured at the circular friction surface 7, 9F or less) Yes. 1 again
The width of 11 yen 11.13 is preferably 1 to 5 mm.

The (circular) IiF friction surfaces 7, 9 face the braking layer 35 distributed along the circumferential surface of the pressing plate 37 in a known manner.

Although the brake unit of the present invention has been described above only when used for braking, the application of the present invention is not limited to this, and can be applied to, for example, a clutch. Furthermore, since the braking unit of the present invention has a large load capacity and high transmission reliability, it can be particularly advantageously applied to very heavy vehicles such as war cars.

(Effects of the Invention) Since the grooves are relatively deep, uneven expansion of the brake disc due to high surface temperature is avoided, and deformation of the brake disc is thereby reduced. At the same time, the rigidity of the brake plate #J is significantly reduced, so even if the brake plate is used in a full-strength type braking unit, all the braking layers are uniformly suppressed over the entire circumference of the brake plate.
Therefore, the temperature of the brake disc increases reliably and uniformly. Due to this elasticity of the brake disc, even if it is deformed along the groove due to the application of braking pressure for a short time, the brake disc returns to its flat shape. Therefore, the number of grooves can be made relatively large, and iδ can also be made sufficiently deep. It is also possible to increase the thickness of the brake disc in its axial direction without substantially reducing its rigidity.

This increase in the thickness and weight of the brake disc allows it to take on a large amount of thermal energy and braking action ('I) without causing unacceptably high temperatures. The grooves also increase the cooling effect because cooling air or cold oil flows through the grooves.

Also, by deviating the groove from the radial direction.

Backlash during braking is reduced, and at the same time the braking moment is transmitted reliably.

As is clear from the figure, since the 1A11.13 intersect in pairs in the point-like small cross-sectional area 33, the mechanical strength of the braking unit is not significantly reduced by the presence of the grooves 11.13. In order to make it easier to understand, 1.1111.13 are both slightly exaggerated and wide in the figure, but in reality, a width of 0.5 mm is sufficient.

The grooves 11.13 are preferably straight. This makes manufacturing simple, and also makes it easy to drain cooling air or cooling liquid.

[Brief explanation of the drawing]

FIG. 1 is an end view showing an example of the braking unit of the present invention. FIG. 2 is a section taken along line I-1 in FIG. 1.
It is t4.

Claims (1)

[Scope of Claims] [1] A plurality of circular friction surfaces adjacent to each other in the circumferential direction are provided within the circular friction surfaces on both sides of the brake disc, each extending from the inner side in the radial direction toward the outer peripheral surface of the circular friction surface. A type having a plurality of grooves divided into segments and running offset from the radial direction of the brake disk on at least one side, the groove (11) in one circular friction surface (7) A braking unit characterized in that it is provided oriented in the opposite direction to the groove (13) in the other circular friction surface (9). [2] The brake unit according to claim [1], wherein the grooves (11, 13) on both sides form a pair and intersect with each other when viewed through in the axial direction. [3] The intersecting grooves (11) of both circular friction surfaces (7, 9)
, 13) is 70% or less of the axial disk thickness (27) measured on the circular friction surface. unit. [4] The braking unit according to claim [1] or [2], wherein the width of the grooves (11, 13) is 1 to 5 mm. [5] The braking unit according to any one of claims [1] to [3], wherein the grooves (11, 13) are linear.