阅读说明：本技术 离合器 (Clutch device ) 是由 范意中 于 2019-01-07 设计创作，主要内容包括：本发明涉及一种离合器,其包括：膜片弹簧,所述膜片弹簧大体呈环形并具有多个分离指；定位销,所述定位销用于将所述膜片弹簧固定到所述离合器的盖板；以及平衡弹簧,所述平衡弹簧支撑于所述膜片弹簧和所述定位销之间并且/或者所述平衡弹簧支撑于所述膜片弹簧和所述盖板之间,与不设置所述平衡弹簧相比,所述平衡弹簧使所述离合器的分离力增加。(The invention relates to a clutch, comprising: a diaphragm spring generally ring-shaped and having a plurality of separating fingers; a positioning pin for fixing the diaphragm spring to a cover plate of the clutch; and a balance spring supported between the diaphragm spring and the positioning pin and/or between the diaphragm spring and the cover plate, the balance spring increasing a separating force of the clutch as compared to when the balance spring is not provided.)

1. A clutch, characterized in that the clutch comprises:

-a diaphragm spring (1), said diaphragm spring (1) being substantially annular and having a plurality of separate fingers;

-a positioning pin (4), said positioning pin (4) being used to fix the diaphragm spring (1) to the cover plate (2) of the clutch; and

-a balancing spring (5), the balancing spring (5) being supported between the diaphragm spring (1) and the positioning pin (4) and/or the balancing spring (5) being supported between the diaphragm spring (1) and the cover plate (2), the balancing spring (5) increasing the clutch release force compared to if the balancing spring (5) were not provided.

2. Clutch according to claim 1, wherein the balancing spring (5) increases the minimum value of the disengagement force by an amount greater than the maximum value of the disengagement force.

3. Clutch according to claim 1, wherein the radially inner end of the balancing spring (5) is pressed against the diaphragm spring (1) and the radially outer end of the balancing spring (5) is pressed against the positioning pin (4), the pressure of the balancing spring (5) acting on the diaphragm spring (1) increasing monotonically with the increase in the stroke of the release finger during clutch disengagement.

4. Clutch according to claim 1, further comprising a support ring supporting the diaphragm spring (1), the balance spring (5) being arranged radially outside the support ring and supported between the diaphragm spring (1) and the cover plate (2).

5. Clutch according to any of claims 1 to 4, wherein the balancing spring (5) is a disc spring.

6. Clutch according to any of claims 1 to 4, wherein the body of the balancing spring (5) is substantially shaped as a ring.

7. Clutch according to any of claims 1 to 4, wherein the radially inner and outer ends of the body of the balancing spring (5) form arc fingers, respectively.

8. The clutch of claim 7, wherein the arcuate fingers of the radially inner end and the radially outer end are curved in opposite directions to one another.

9. Clutch according to any of claims 1 to 4, wherein the balancing spring (5) is made of steel.

10. Clutch according to any of claims 1 to 3, wherein the balance spring (5) is located radially inside the dowel pin (4) as a whole.

Technical Field

The present invention relates to a clutch.

Background

A known clutch construction is shown (partially) in fig. 1, with a generally annular diaphragm spring 1 acting on a pressure plate 6, and two support rings 3 supporting the diaphragm spring 1 from both sides in the axial direction a. The diaphragm spring 1 and the support ring 3 are fixed to the cover plate 2 by means of a plurality of positioning pins 4 (only 2 are shown in the figure) distributed in the circumferential direction.

When the clutch pedal is depressed, and the clutch is thus disengaged, the diaphragm spring pivots like a lever about the support ring. Fig. 2 shows the characteristic curve of the change in the separating force (vertical axis) in the process with respect to the stroke of the separating finger (horizontal axis, unit mm), which is the curve when the engine is at rest. As can be seen from the figure, the curve rises monotonously first, descends after reaching the highest point (about 4mm of the stroke of the separating finger), and rises again after reaching the lowest point (about 9mm of the stroke of the separating finger).

For manual gearboxes, the minimum value of the disengagement force (i.e. the value at about 9mm of disengagement finger travel in the figure) is usually limited by the disengagement parameters of the disengagement systems of different manufacturers, which means that the minimum disengagement force must be designed at a lower force level. However, such a low minimum separation force may cause pedal problems in view of the centrifugal load due to the separation fingers of the diaphragm spring. Fig. 3 shows the characteristic curves of the separating force versus the stroke of the separating fingers when the engine is operated at different speeds (0 rpm, 3000rpm, 5000rpm and 6000rpm in sequence from top to bottom). As can be seen, in the region where the stroke of the separation finger is short, the difference caused by the engine speed is not large, and as the stroke of the separation finger is longer, the separation force is more and more affected by the speed, and therefore, it is more significant at high speeds.

Disclosure of Invention

The present invention has been made in view of the above-mentioned known drawbacks, and a primary object of the present invention is to provide a clutch that makes it possible to easily adjust the characteristic curve of the separating force.

The clutch according to the present invention comprises:

-a diaphragm spring generally annular in shape and having a plurality of separating fingers;

-a positioning pin for fixing the diaphragm spring to a cover plate of the clutch;

and

-a balancing spring supported between the diaphragm spring and the dowel pin and

or the balance spring is supported between the diaphragm spring and the cover plate, and the balance spring is not arranged

The counterbalance spring increases the separating force of the clutch compared with the counterbalance spring.

In particular, the balancing spring increases the minimum value of the separating force by an amount greater than the maximum value of the separating force.

In particular, the radial inner end of the balance spring is pressed against the diaphragm spring, the radial outer end of the balance spring is pressed against the positioning pin, and the pressure applied to the diaphragm spring by the balance spring is monotonically increased along with the increase of the stroke of the release finger in the clutch release process.

In particular, the clutch further comprises a support ring supporting the diaphragm spring, the balance spring being arranged radially outside the support ring and supported between the diaphragm spring and the cover plate.

In particular, the balancing spring is a disc spring.

In particular, the body of the balancing spring is substantially formed in a ring shape.

In particular, the radially inner end and the radially outer end of the body of the balancing spring form an arc finger, respectively.

In particular, the bending directions of the arcs of the arc fingers of the radially inner end and the arc fingers of the radially outer end are opposite to each other.

In particular, the balancing spring is made of steel.

In particular, the balancing spring is located entirely radially inside the positioning pin.

The clutch according to the invention allows the characteristic curve of the separating force to be easily adjusted.

The clutch according to the invention improves the behavior of the separating force taking into account the centrifugal force, and the characteristic curve of the separating force can be freely adjusted by setting the parameters of the compensating spring. The influence of the balancing spring on the separating force is small at the maximum value of the separating force and large at the minimum value of the separating force, in particular the centrifugal force at high engine speed is balanced.

Drawings

Fig. 1 shows a partial cross-sectional view of a prior art clutch.

Fig. 2 shows a characteristic curve of the separating force at rest of the engine as a function of the stroke of the separating finger.

Fig. 3 shows a characteristic curve of the separating force versus the stroke change of the separating fingers when the engine is operated at different speeds.

FIG. 4 shows a partial cross-sectional view of a clutch according to one embodiment of the present invention with a counterbalance spring disposed therein.

Fig. 5 shows a perspective view of the balancing spring.

Fig. 6 shows a schematic representation of the change in the characteristic curve of the separating force at rest of the engine with respect to the change in the stroke of the separating finger under the influence of the balancing spring.

Description of the reference numerals

1, a diaphragm spring; 2, covering a plate; 3, supporting the ring; 4, positioning pins; 5 balancing a spring; 6, pressing a disc;

51 a main body; 52 arc fingers;

axial direction A; r is radial.

Detailed Description

Exemplary embodiments of the present invention are described below with reference to the accompanying drawings. It should be understood that the detailed description is intended only to teach one skilled in the art how to practice the invention, and is not intended to be exhaustive or to limit the scope of the invention.

Fig. 4 shows a partial cross-sectional view of a clutch according to an embodiment of the invention, in which, in contrast to the clutch of the prior art shown in fig. 1, a compensating spring 5 is provided, the radially inner end of the compensating spring 5 resting against the diaphragm spring 1 and the radially outer end resting against the positioning pin 4. The balancing spring 5 is seen to be located entirely radially inside R of the positioning pin 4. However, other positional relationships may be provided. The positioning pin 4 in the present invention may be a bolt, a rivet, or the like.

Fig. 5 shows a perspective view of the balancing spring 5. The balancing spring 5 is substantially annular and has a body 51, the body 51 being substantially annular plate-shaped with an axial cross-section as shown in fig. 4, i.e. the balancing spring 5 is a substantially annular disc spring. At the radially inner end and the radially outer end of the main body 51, arc fingers 52 are formed, respectively, whose arc-shaped bending directions are opposite to each other, with intermediate spaces between the main body 51 and the diaphragm spring 1 and the positioning pin 4, respectively, as shown in fig. 4. The material of the balancing spring 5 is, for example, steel. Although not shown in the drawings, the body 51 of the balance spring 5 may have a plurality of holes through which the positioning pins 4 pass in the mounted state.

Fig. 6 shows a schematic representation of the change in the characteristic curve of the separating force at rest of the engine with respect to the change in the stroke of the separating finger under the influence of the balancing spring. In the figure, a characteristic curve in which the stroke of the lowermost separation finger monotonously increases with the stroke of the separation finger is a characteristic curve of the balance spring, a middle solid line is a characteristic curve of the separation force when the balance spring is not present, and an uppermost broken line indicates a characteristic curve of the separation force when the balance spring is present. It is evident from the figure that the influence of the balancing spring on the separating force is smaller at the maximum of the separating force and larger at the minimum of the separating force (the minimum to the right of the maximum). According to actual use requirements, the characteristic curve of the separating force can be adjusted by adjusting the balance spring.

Although fig. 6 shows only the characteristic curve of the separating force with respect to the stroke change of the separating finger when the engine is stationary, the influence of the balancing spring on the separating force when the engine is running is similar to that when the engine is stationary, and therefore the change of the characteristic curve of the separating force is also similar. The characteristic curve of the separating force can be adjusted with the balancing spring according to the invention irrespective of the operating speed of the engine.

It should be understood that the arrangement of the balance spring 5 in the present application is not limited to the above form. In a further alternative embodiment, a further compensating spring may alternatively or additionally be provided, which may be supported between diaphragm spring 1 and cover plate 2. In particular, the further balancing spring may be arranged radially outside the support ring. The further diaphragm spring may have a ring-shaped configuration similar to the diaphragm spring shown in fig. 5. In the case where the further compensating spring is arranged radially outside the support ring, the radially outer end of the further compensating spring exerts a force on the radially outer end of the diaphragm spring 1 toward the pressure plate 6, so that the clutch release force is increased.

The scope of the present invention is not limited to the specific examples described in the above-described embodiments, but falls within the scope of the present invention as long as the combinations of the technical features of the claims of the present invention are satisfied.