JPS61286616A - Clutch disc - Google Patents

Abstract

PURPOSE:To reduce vibration by providing a spring made of an elastic body set in such a manner as to have multistage property between a disc plate and a hub to hold down an angle of displacement for torque fluctuation. CONSTITUTION:In case of transmitting torque from a disc plate 2 to an intermediate plate 6, as the first spring 11 is previously set in the compression state, a spring constant characteristic is kept from the point of time a rubber 20 is displaced by a gap delta to the pre-load point. The spring constant characteristic of the second spring 13 is a linear characteristic passing the origin 0. Accordingly, the final spring constant characteristic extending from the disc plate 2 to the hub 3 have a reverse spring characteristic so as to reduce rotational vibration generated in a driving system.

Description

DETAILED DESCRIPTION OF THE INVENTION Field of Industrial Application The present invention is configured such that input torque is outputted through an elastic body, and the spring constant of the elastic body is changed according to multistage characteristics 1 to 4. Regarding the clutch disc that has become more common.

Clutch discs based on conventional technology, for example,
There is one shown in 33828. That is, this clutch disc has a disc plate that can input torque,
An elastic body is provided between the hub that outputs torque, and the spring constant of this elastic body changes in multiple stages as the displacement angle between the disc plate and the hub increases, as shown in Figure 13. It is now possible to do so.

Problems to be Solved by the Invention However, the problem with such conventional clutch discs is that
The change in the spring constant of an elastic body is that the spring constant (inclination) increases stepwise as the displacement angle increases (in the direction away from the origin 0).In other words, as the displacement angle increases, the stiffness changes from small to large. It was set up to be changed step by step. Therefore, if a torque fluctuation occurs between the spring constants that are changed in this step, the displacement angle will change significantly, and if such a clutch disc is installed in the engine output section of the vehicle, this will occur when the accelerator is turned OFF. The torque fluctuation causes the drive system from the transmission to the drive wheels to twist and shake, inducing so-called jerky vibrations in which the vehicle swings back and forth.

That is, this is due to the fact that the spring constant increases as the displacement angle increases, resulting in an increase in vibration energy. For example, when considering the change in the spring constant, assume a vibration model of a one-degree-of-freedom system shown in FIG. 12, and use this model l to consider the change in the spring constant. That is, in this model, a mass body M is supported by a spring K having a spring constant characteristic A that can be felt in multiple steps as shown by the solid line in FIG.
When the vibration is applied, the generated vibration is centered at the value l of the excitation force Fo. The photographing energy at this time is the potential energy of the spring K of one photographing width, and is determined by the area U1 indicated by diagonal lines in FIG. On the other hand, according to the law of conservation of energy, the potential energy U2 above the characteristic connection point Fo is equal to the aforementioned Ul, so the maximum excitation force Fmax and the maximum displacement δmax can be determined from the value of U1 and the spring characteristics. Therefore,
As the spring K has a characteristic that the spring constant changes from low to high as the amount of deflection increases, the vibration energy indicated by the area U2 increases. Therefore, with the conventional clutch disc having the spring characteristics shown in Fig. WJ13, there is a problem in that large torque fluctuations occur as the kinetic energy increases, causing the jerky vibration of the vehicle as described above. Ta.

Therefore, the present invention reverses the height relationship of the multi-stage spring constant of the elastic body, thereby reducing the potential energy in the portion where the displacement angle is small, and thereby the maximum excitation force determined by this pre-adjustment energy. The purpose of the present invention is to provide a clutch disc that is made smaller.

Means for Solving the Problems In order to achieve these objectives, the present invention provides a disc grate to which torque is input, a torque input to this disc plate is transmitted via an elastic body, and this torque is transmitted outward. In the clutch disc, the spring constant of the elastic body is changed in multiple stages when torque is transmitted from one disc plate to the knob A, and the spring constant of the elastic body is changed in multiple stages. In the spring constant characteristics, the relationship between at least one set of consecutive spring constant characteristics is set such that the spring constant increases and then decreases as the displacement angle between the disk plate and the hub increases. It is composed by

Due to the above-described structure, the clutch disc of the present invention has a low spring constant in the portion where the displacement angle between the disc plate and the hub is small. Because the constant is high, the potential energy of the elastic body for a given excitation force, that is, a constant input torque, is small, and the maximum excitation force and maximum displacement determined by the part where the spring constant of the next stage is lower are set to be small. be done. Therefore, the drive system noise is reduced by the characteristic of a low spring constant at small displacement angles, and the torque fluctuates between the characteristic with a high spring constant at the next stage and the characteristic with a low spring constant at large displacement angles. In this case, the change in displacement angle for a predetermined amount of torque fluctuation is suppressed to a small value, and the vibrations generated at that time are significantly reduced.

Example Hereinafter, embodiments of the present invention will be described in detail based on the drawings.

That is, FIG. 1 and FIG. 2 show an example of a clutch disk 1 according to the present invention, which is used between an engine and a transmission mounted on a vehicle. The clutch disc 1 includes a disc plate 2 to which torque from an engine is input, and a hub 3 to output the input torque to a transmission. The hub 3 projects like a brim from the outer periphery of a boss portion 4 having serrations 4a formed on its inner periphery, and the center hole 2a of the disk plate 2 is rotatably fitted into the boss portion 4. A facing material 5 is fixed to the outer peripheral edge of the disc plate 2, and engine torque is transmitted by pressing the facing material 5 against a flywheel (not shown). Also, disk plate 2
An intermediate plate 6 is provided between the hub 3 and the hub 3, and a center hole 6a of the intermediate plate 6 is rotatably fitted into the boss portion 4. In addition, 7 is the hub 3
The center hole 7a of this support plate 7 is also rotatably fitted into the boss portion 4, and its outer peripheral edge is connected to the hub 3. A rivet 8 is fixed to the disk plate 2 with a constant width at a portion with a larger diameter than the intermediate plate 6.

Here, in this embodiment, the disk plate 2 and the intermediate plate 6 have first window portions 10 and 1 facing the boss portion 4.
01L 1, and this first window portion 10°10
& is a first spring stored in the circumferential direction spanning both the disk plate 2 and the intermediate plate 6.

Of this first window section 10, 10 & intermediate play) 6
The length of the window 10& of 141 in the direction of the disc plate 2
It is formed longer than the side window portion 10, and a gap δ is provided between both ends of the first spring 11, and a rubber pad with a low spring constant is arranged in this gap δ.

On the other hand, the hub 3 and the intermediate plate 6 are marked with a tx1 window 10.
, 10 a, and are formed by penetrating through second window portions 12 , 12 a that similarly face the border of the boss portion 4 . A second spring 13 is housed in the circumferential direction across the plate 6. At this time, the second springs 13 come into contact with both sides of the Wc2 windows 12, 12& in the circumferential direction in their natural state, but the first springs 11 contact the first windows 10 in their compressed state.
, 10a in the circumferential direction. And the above @1. The second springs 11 and 13 constitute an elastic body.

With the above configuration, in the clutch disc 1 of this embodiment, the engine torque input to the disc plate 2 is transmitted to the intermediate plate 6 via the first spring 11, and furthermore, from the intermediate plate 6 to the second The transmission is transmitted to the hub 3 via the spring 13, and the transmission is driven via a shaft (not shown) fitted into the boss portion 4 through serrations. By the way, when the torque is transmitted from the first disc plate 2 to the intermediate plate 6, the first spring 11 is set in a compressed state in advance, so the return torque-displacement angle characteristic, that is, the spring constant characteristic at that time, is shown in Fig. 3. As shown in FIG.
The spring constant characteristics are as shown in Figure @4, with the origin 0'1
It is a linear characteristic that passes through . The final spring constant characteristic from the disc plate 2 to the hub 3 is the spring constant characteristic shown in FIG. 5, which is a combination of the above-mentioned FIG. 12 and FIG. By forming the bending characteristic, the amount of displacement angle with respect to the fluctuation of the simulated torque is reduced, the rotational vibration or judder generated in the drive system is significantly suppressed, and the jerky vibration of the vehicle body is reduced. That is, if we explain using the characteristic B shown by the two-dot chain line in FIG. 11, which is the effect of the reverse bending characteristic, the step input F
When o is added, characteristic B is higher than characteristic A in the second stage (
Since the rigidity of the portion (where the amount of deflection is small) is high, a small amount of vibrational energy is generated, which is represented by the area u1 shown in the matte finish.

Furthermore, by making the rigidity of the third stage lower than that of the first stage, the area U! The potential energy expressed by
The maximum excitation force F'max can be brought closer to Fo.

In this embodiment, the first spring 11 is set in a compressed state and the wIJ2 spring 131 is set in a natural state, but this is the opposite; the first spring 11 is set in a natural state. Even if the second spring 13 is set in a compressed state, the same reverse bending characteristics as shown in FIG. 5 can be obtained as a result.

FIGS. 6 and 7 show other embodiments, and the same components as those in the previous embodiment are given the same reference numerals and redundant explanation thereof will be omitted.

That is, in this embodiment, the disc plate 2, the hub 3, and the intermediate plate 6 are located concentrically, and the seven acing materials 5 are adhered to the front and back surfaces of the outer periphery of the disc plate 2. The disk plate 2 and the intermediate plate 6 are connected to the first window portion 1
The first spring 21 and the third spring 23 are fully supported in the circumferential direction through the third window portion 25°25&'fl and can rotate on a concentric axis. The first spring 21 is provided on either the disk plate 2 or the intermediate plate 6, and the first window portion 10B on the intermediate plate 6 side is provided with a clearance in the circumferential direction.

The intermediate plate 6 and 3 hubs @ 2 springs 22 are supported in the circumferential direction via the second windows 12 and 12a and can rotate on a concentric axis. The first spring 21 at the circumferential direction,
The other springs are installed at their natural lengths. The support plate 7 is connected to the disk plate 2 via rivets 8 while maintaining a constant width, and the intermediate plate 6
This is to prevent the hub 3 from moving. It is also possible to replace the rivet 8 with a screw and nut.

The rotational torque is transmitted to the facing material 5 and the disc plate 2 which are pressed together by the flywheel, and the rotational torque is transmitted to the intermediate plate 6 via the 8g3 spring 23.
It is transmitted to As the torque increases, the clearance disappears, just like the first spring 21 is loaded in parallel! : The first spring 21 and three springs are parallel springs. Furthermore, the torque is transmitted from the intermediate plate 6 to the hub 3 via the second elastic body n, and then to the transmission. Here, it is assumed that the circumferential rigidity of the elastic body is constant. Since the first spring 21 is compressed and installed and there is a clearance, the imitation characteristics between the intermediate plate 6 and the hub 3 will be linear characteristics as shown in Figure @8, and the smoldering characteristics between the disc plate 2 and the intermediate plate 6 will be Since the elastic body is compressed, the characteristics as shown in FIG. 9 are obtained. Therefore, the torsional characteristic of the entire clutch disc can be considered to be that the rigidity of the @l spring 21 and the second spring n are set in series. Therefore, the characteristics as shown in FIG. 10 can be obtained, and the same functions as those of the embodiment described above can be exhibited.

As described in detail, in the clutch disc of the present invention, the spring constant of the elastic body provided between the disc plate and the hub is the same as that of the disc plate.

As the spring constant is set to have at least one set of characteristics such that the spring constant increases and then decreases as the displacement angle between the hubs increases, the low spring constant of the portion where the displacement angle is small increases the drive speed. Abnormal noise in the system is reduced, and the potential energy of the elastic body is reduced due to the high spring constant of the next stage, and the maximum excitation force and maximum displacement of the part where the spring constant of the next stage is low are set to be small. Therefore, the displacement angle is suppressed to a small extent against torque fluctuations caused by passing points with different spring constants, and the vibrations generated at that time can be significantly reduced, and the engine output of the vehicle with such a clutch disc 2 is suppressed. When provided in the section, it has the excellent effect of reducing drive system noise (transmission rattling noise) and significantly reducing jerky vibrations caused by torque fluctuations when the accelerator is turned on and off.

[Brief explanation of the drawing]

Fig. 1 is a front view of a clutch disc showing an embodiment of the present invention, Fig. 2 is a sectional view taken from the line ■-■ in Fig. 1, and Figs. 3, 4, and 5 are the views shown in Fig. 1. Figure Wc6 is a front view of the clutch disc shown in another embodiment of the present invention, Figure 7 is a cross-sectional view taken from the line ■-■ in Figure 6, Figures 8, 9, and @10 are characteristic diagrams of spring constants for the clutch disc shown in Figure 6, Figure 11 is an explanatory diagram of various spring characteristics based on the vibration waveform of Figure WJ12, and Figure 12 is a diagram of the characteristics of the clutch disc. A vibration model diagram schematically showing the spring action, Figure 13 is a characteristic diagram showing the spring constant of a conventional clutch disc. 1...Clutch disc, 2...Disc plate, 3...Hub, 11...I! 1 spring (elastic body), 13... 2nd spring (elastic body), 21...
1st spring (elastic body), n... 2nd spring (
elastic body), 23... third spring (elastic body). Figure 6 Figure 7 Figure 12 Figure 13

Claims (1)

[Claims] (1) A disk plate to which torque is input, and a hub to which the torque input to the disk plate is transmitted via an elastic body and output this torque to the outside, and the torque is transmitted from the disk plate to the hub. In a clutch disc in which the spring constant of the elastic body is changed in multiple stages when the spring constant is changed in multiple stages, the characteristic of the spring constant of the elastic body that is changed in multiple stages is the characteristic between at least one consecutive set of spring constant characteristics. A clutch disk characterized in that the relationship is set such that as the displacement angle between the disk plate and the hub increases, the spring constant increases and then decreases.