JPS59231219A - Hydraulic clutch - Google Patents

Abstract

PURPOSE:To obtain a high load from the early stage of the slide stroke of a piston by superposing at least two pieces of belleville springs for compressing a friction disc, in the counter posture, and fitting a guide member for applying a preload, onto the belleville springs. CONSTITUTION:A belleville spring 13 is arranged between a piston 3 and a friction disc 8 on the input side continuous to the piston 3, and said belleville spring 13 is arranged in the counter posture where each outer peripheral edge part of two pieces of annular belleville springs 13 and 13 is attached. The inner peripheral edge part of the belleville spring 3 is fitted onto a cylindrical guide member 14. Said guide member 14 is integrally equipped with the annular stopper parts 15 and 15 for holding the belleville springs 13 and 13 in a prescribed compression state, and therefore the belleville springs 13 and 13 are kept in the state where a preload is applied.

Description

DETAILED DESCRIPTION OF THE INVENTION The present invention relates to all hydraulic clutches employed in automobiles, industrial machinery, construction machinery, agricultural machinery, ships, and the like.

As shown in Fig. 1, the conventional hydraulic clutch has cylinder 1.
By introducing hydraulic oil into the hydraulic chamber 102 in the 01, the hydraulic piston 108 is slid to the right in the figure, and the disc spring 104
The clutch is connected by pressing the friction plates 105 and 106 on the input side and the output side against each other via the clutch.

In this configuration, since the disc spring 104 is in a free state in the clutch disengaged state (the state shown in FIG. 1), the relationship between the sliding stroke S of the hydraulic piston 108 and the load W generated between the friction plates 105 and 106 is similar to that of the disc spring. Due to its unique properties, it becomes as shown in Figure 2.

However, with the above conventional configuration, only a hydraulic clutch having the characteristics shown in Fig. 2 can be obtained, and modern automobiles,
It is not possible to adequately meet the needs for hydraulic clutch characteristics such as shock prevention during clutch engagement due to the diversification of industrial machinery. In particular, if characteristics such as a relatively high load W are required from the initial stage (near O) of the sliding stroke S of the piston 108, it is impossible to meet the requirements with the above-mentioned conventional configuration.

In view of the above-mentioned problems, the present invention has a simple structure that allows a relatively high load to be applied from the beginning of the piston's sliding stroke, thereby meeting various demands such as shock prevention when connecting a clutch. DESCRIPTION OF THE PREFERRED EMBODIMENTS For the purpose of providing a hydraulic clutch having various characteristics, the present invention will now be described based on the drawings.

In FIG. 8, a cylinder 1 is integrally provided on the outer peripheral side of a clutch input shaft 2, and an annular piston 8 is slidable in a cylindrical space formed in the cylinder 1 in the direction of the center line O-O. is fitted. 4.5 is a seal ring or a seal ring.

The outer cylindrical part of the cylinder 1 is cylindrically extended to the right in the figure, and the extended part 6 is provided with a slit 7 parallel to the center line ○-○. The outer peripheral protrusion of No. 8 (Dofip plate) is slidably fitted.

A stopper 9 for preventing the friction plate 8 from sliding is attached to the inner surface of the tip of the extension 6. An annular friction plate 10 (driven plate) having facings on both sides is arranged between each two adjacent friction plates 8.8.
A protrusion provided on the inner periphery of the cylindrical output shaft 11 is slidably fitted into a slit 12 formed in the cylindrical output shaft 11 and parallel to the center line o-O.

A disc spring 3 as shown in FIG. 4 is disposed between the piston 3 and a friction plate 8 on the input side adjacent to the piston 3. As shown in FIG. 4, two annular disk springs 18, 18 are arranged in opposite positions with their outer peripheral edges abutting each other, and their inner peripheral edges spaced apart fit into the cylindrical guide member 14. are doing. The guide member 14 has an integral annular stopper portion 15.15 that holds the disc spring 18.18 in a predetermined compressed state, so that the disc spring 18.13 is in a preloaded state. Retained. The guide member 14 is the third
As shown in the figure, the piston 8 is rotatably and slidably fitted to the output shaft 11, and the piston 8 and the friction plate 8 on the piston 8 side each have an inner peripheral portion on which the piston 8 slides toward the friction plate 8 side. An annular notch 16. is provided so that the guide member 14 does not become an obstacle when
17 is formed.

Next, the operation will be explained. When the clutch connection operation is performed, hydraulic pressure is introduced from an oil passage (not shown) formed in the input shaft 2, and the hydraulic chamber 20 is pressurized.Receiving the hydraulic pressure in the chamber 20, the piston 3 moves the disc spring 18 to the right in the figure. , and presses the friction plate 8 via the disc spring 18. As a result, the friction plates 8.10 begin to press against each other and the clutch begins to engage. As the piston 8 slides further to the right, the disk spring 13,18 begins to be compressed. When the disc springs 13, 13 are fully compressed (flat plate state), the clutch connection is completed. At this time, since a preload has been applied to the disc springs 18 and 13 in advance, the relationship between the piston 30 stroke S and the load W is as shown by the solid line A in Fig. 5. Load characteristics having a relatively higher load W can be obtained.

When the clutch disengagement operation is performed to release the hydraulic pressure in the hydraulic chamber 20, the piston 3 is pushed back to the left in the figure by the repulsive force of the disc spring 13, returning to the state shown in FIG. 8, and becoming the clutch disengaged state (2).

Note that when the disc springs 13 and 18 are compressed between the piston 3 and the friction plate 8, the disc springs 1
The inner peripheral end of 3.13 slides and is compressed into a flat plate shape, and the guide member 14 is inserted into the piston 8 and the notch 1 provided in the friction plate 8.
6.17. On the other hand, when the piston 8 is pushed back by the repulsive force of the disc springs 13.13, the guide member 1 moves in the direction in which the inner peripheral parts of the disc springs 13.18 separate from each other.
4 and is held in a predetermined compressed state by abutting a stopper part 15.15 (FIG. 4).

As explained above, according to the present invention, the friction plate 8 on the input side
In this hydraulic clutch, the friction plates 8 and 10 on the output side are overlapped and a piston 8 is provided which presses the two friction plates 8 and 10 via a disk spring 13 so as to press them against each other.
Since the guide member 14 that applies a preload is fitted onto the disc spring 18 and the guide member 14 is stacked in opposite directions to each other, it is possible to obtain a characteristic that a relatively high load is applied at the beginning of the sliding stroke of the piston 8. This has the advantage that it is possible to obtain a hydraulic clutch that can meet various demands such as shock prevention during clutch engagement, which is accompanied by the development of machines that employ hydraulic clutches. Moreover, since it has a simple configuration in which a conventional disc spring 1B is fitted into the guide member 14, it is easy to adopt and has high practicality.

In carrying out the present invention, the following configuration may also be adopted.

(a) As shown in FIG. 6, a disc spring 18 may be further interposed between the disc spring 18 and the piston 3 (which may be on the friction plate 8 side). In this case, since no preload is applied to the disc spring 18, a gentle rising characteristic is obtained as shown by the chain line B in FIG.

Of course, two or more plate springs 18 may be fitted to the guide member 14.

(g) The disc springs 13, 13 may be arranged so that their inner circumferential sides abut each other and their outer circumferential sides are spaced apart, and the guide member 14 may be fitted on the outer circumferential sides. In this case piston 3
and a notch 16.1 on the outer circumferential side of the friction plate 8 on the piston 3 side.
It is necessary to provide 7.

(C) FIGS. 7 and 8 show different embodiments. In this case, the input shaft 2 is provided with an annular step 19, and the guide member 14 is slidably fitted into the step 19, so that the relative position between the piston 8, friction plate 8, and disc spring 18 (18) is There is an advantage that rotation does not occur and the durability of the disc spring 18 (18) is improved.

[Brief explanation of the drawing]

FIG. 1 is a partial longitudinal side view of a conventional hydraulic clutch. FIG. 2 is a graph showing the characteristics of a conventional hydraulic clutch. FIG. 8 is a partial vertical side view of a hydraulic clutch according to the present invention. FIG. 5 is a graph showing the characteristics of the hydraulic clutch according to the present invention, and FIGS. 6, 7, and 8 are partial longitudinal side views showing different embodiments. 8...
Piston, 8.10... Friction plate, 18... Belleville spring,
14... Guide member patent applicant Daikin Seisakusho Co., Ltd. 9

Claims (1)

[Claims] In a hydraulic clutch in which a friction plate on the input side and a friction plate on the output side are overlapped and a piston is provided that presses the two friction plates via a disc spring so as to press the two friction plates against each other, two or more of the above-mentioned device springs are arranged in opposite directions. A hydraulic clutch characterized in that a guide member that overlaps in position and applies a preload is fitted to a disc spring.