JPH0728416Y2 - Clutch disc - Google Patents

Description

DETAILED DESCRIPTION OF THE INVENTION (Industrial field of application) The present invention relates to a clutch disc of a dry single-plate friction clutch.

(Prior Art) Generally, the clutch disc of a dry single-plate friction clutch mounted on a vehicle absorbs engine rotation fluctuations by using hysteresis to suppress abnormal noise in the drive system and muffled noise generated in the passenger compartment. ing. FIGS. 4 and 5 show a conventional clutch disc. The clutch disc 1 includes a clutch plate 2 and a retaining plate 3 (hereinafter simply referred to as a clutch plate 2 or the like) to a hub plate 4 or a hub plate 4 to a clutch. The structure is such that the clutch plate 2 and the like are twisted according to the magnitude of the transmission torque transmitted to the plate 2 and the like, that is, the clutch plate 2 and the hub plate 4 are relatively rotated, and the predetermined twisting characteristics shown in FIG. 6 are set.

Torsional characteristics indicated conventional clutch disc 1 includes a first hysteresis region ranging torsional angle _{θ 3 ~-θ 3 ',} θ 3
It consists of a second hysteresis region ranging through? ₄ and -θ ₃ '~θ _4', the smaller the first hysteresis region transmission torque, only the first coil spring 6 having a small spring constant is compressed , The torque is transmitted according to the compression amount of the coil spring 6, that is, the torsion angle of the clutch disc 1, and the friction plate 5, which has a small friction coefficient,
5 gives a small hysteresis characteristic. In the second hysteresis region where the transmission torque is large, the spring constant is the first
The second coil spring 8 larger than the coil spring 6 is also compressed, torque is transmitted according to the compression amount of the coil springs 6 and 8, and the friction plates 7 and 7 having a large friction coefficient have a large hysteresis characteristic. I'm giving. Then, when the twist angle of the clutch disc 1 reaches θ ₄ or −θ ₄ ′, the connecting pin 9 that connects the clutch plate 2 and the retaining plate 3 is connected to the hub plate 4.
, The clutch plate 1 and the hub plate 4 start rotating integrally while the clutch disc 1 is being twisted at the twist angle. When the transmission torque of the clutch disc increases or decreases, the torsion angle also changes along the hysteresis operation line shown in FIG.

(Problems to be solved by the invention) When setting such a twisting characteristic of the clutch disc 1,
The spring constant of the coil spring and the friction coefficient of the friction plate are set to the optimum values according to the driving pattern of the vehicle, but it is structurally difficult to set the torsional characteristics to suit any driving condition. Met. That is, it is desirable to give a small hysteresis characteristic to a small fluctuating torque and a large hysteresis characteristic to a large fluctuating torque. However, for example, the transmission torque is small during the idle operation of the standard vehicle and the torque fluctuation is large, whereas the transmission torque during the high speed traveling is large, but the torque fluctuation is small. In such cases, generally the first
Also, the second hysteresis region is set in accordance with the main operation region at the time of idling, and the reduction of the idling noise is emphasized, and the measure against the abnormal noise of the drive system at the time of traveling is sacrificed to some extent. However, there is a demand to reduce both the noise during idling and the abnormal noise of the drive system during traveling, which are different in the main operating range.

In addition, the idle operation of a specially equipped vehicle used for a concrete mixer truck, etc., has a large transmission torque and a large torque fluctuation, unlike the idle operation of a standard vehicle. Therefore, the torsional characteristics set for the standard vehicle are directly applied to the specially equipped vehicle. I can't.

However, it is preferable that the clutch disk be applicable to both standard vehicles and specially equipped vehicles because of the demand for production efficiency.

The present invention has been made in order to solve such a problem, and can obtain a suitable twisting characteristic in any operation region having a different main operation region, and can be used in various types of vehicles regardless of whether it is a standard vehicle or a specially equipped vehicle. An object is to provide a clutch disc applicable to a vehicle.

(Means for Solving the Problems) In order to achieve the above object, according to the present invention, in a clutch disc having a rotation direction cushioning mechanism between a hub plate and a torque transmitting member rotatable relative to the hub plate, The direction buffering mechanism frictionally engages between the hub plate and the torque transmitting member, a spring mechanism that transmits torque according to a relative rotation angle between these members, and the hub plate and the torque transmitting member. A first friction engagement member having a first coefficient of friction, and a pin fixed to the hub plate,
A plate member that comes into contact with the pin and integrally rotates when the pin relatively rotates with respect to the pin, and frictionally engages with the plate member and the torque transmission member, and also has the first friction. A second having a second coefficient of friction greater than the coefficient
And a frictional engagement member of the above.

(Operation) Since the hub plate and the plate member are not engaged until the clutch disc is twisted by a predetermined angle or more, the plate member is engaged with the second friction engagement member and integrally rotates with the torque transmission member.

When the clutch disc begins to twist, first the first friction engagement member slides to cause relative rotation of the hub plate and the torque transmission member, and torque according to the relative rotation angle is transmitted via the spring mechanism. At this time, a part of the transmission torque is transmitted via the first friction engagement member according to the first friction coefficient. When the twist angle of the clutch disc increases and reaches a predetermined angle, the hub plate and the plate member engage with each other to start integral rotation, so that the second frictional engagement member begins to slide and a part of the transmitted torque becomes part of the first torque. In addition to one friction engagement member, it is transmitted via the second friction engagement member. Therefore, when an increasing or decreasing torque fluctuation occurs, a part of the transmission torque is always started from the first friction engagement member, and the torque transmission of the second friction engagement member is started after the clutch disc is twisted by a predetermined angle. Be started.

Embodiment An embodiment of the present invention will be described in detail below with reference to the accompanying drawings.

1 and 2 show an embodiment of a clutch disc to which the present invention is applied. The clutch disc 20 includes a clutch plate 21, a retaining plate 22, and a hub plate 2.
3. The clutch plate 21 and the retaining plate 22, which are composed of the spring mechanism 24, the damper mechanism 25 and the like, and are arranged so as to hold the hub plate 23, are connected by the stopper pin 26 and integrally rotate. Also, the stopper pin 26
Is a long hole formed near the outer peripheral edge of the hub plate 23.
It penetrates through 23a. Therefore, the clutch plate 21 and the retaining plate 22 (hereinafter simply referred to as the clutch plate
21)) and the hub plate 23 are relatively rotatable left and right by an angle θ ₂ or θ ₂ ′ from the neutral position of the stopper pin 26 to the position where the stopper pin 26 abuts both ends of the elongated hole 23a (second position).
Figure). In other words, the clutch plate 21
When the rotation torque is transmitted to the 23 (forward transmission), the rotation torque can be relatively rotated by the angle θ ₂ , and when the rotation torque is transmitted from the hub plate 23 to the clutch plate 21 (reverse transmission). , And can be relatively rotated by an angle θ ₂ ′.

The damper mechanism 25 includes a clutch plate 21 and a hub plate 23.
The first hysteresis generating section 27 is arranged between the retaining plate 22 and the hub plate 23, and the first hysteresis generating section 27 is locked to the clutch plate 21. a friction plate 29 that is, interposed between the friction plate 29 and hub plate 23 has a coefficient of friction mu _1, a friction washer 30 that generates a hysteresis H _1, the friction plates 29 and the friction washer 30 and hub plate 23 It is composed of a wave spring 31 that presses against.

The second hysteresis generator 28 has a long hole 32 at a position near the outer peripheral edge.
a has a perforated friction plate 32, a friction coefficient μ ₂ that is interposed between the friction plate 32 and the retaining plate 22 and is larger than the friction coefficient μ ₁ of the friction washer 30 described above, and the hysteresis H ₂ (H ₂ > H ₁ )
And a cone spring 34 for pressing the friction washer 33 against the retaining plate 22. The long hole 32a of the friction plate 32 is penetrated by the pin 35 fixed to the hub plate 23 at one end, so that the friction plate 32 and the hub plate 23 are
From the neutral position to the position where the pin 35 abuts on both side ends of the elongated hole 32a, the pin 35 can be relatively rotated right and left by an angle ε ₁ (forward transmission) or ε ₁ ′ (reverse transmission).

The spring mechanism 24 includes the clutch plate 21 and the hub plate 23.
The first coil spring 36 is interposed between the first coil spring 36 and the second coil spring 37 having a larger spring constant. Both ends of the first coil spring 36 are in contact with the plates 21 to 23 in advance. Further, both ends of the second coil spring 37 are in contact with the clutch plate 21, the retaining plate 22 and the like in advance.
The clutch disc 20 does not come into contact with the clutch 23 unless it is twisted by the angle θ ₁ or θ ₁ ′ (see FIG. 3). For this reason, the first coil spring 36 is compressed even if the clutch disc 20 is twisted even a little, but the second coil spring 37 causes the twist angle of the clutch disc 20 to be the angle θ ₁ (forward transmission) or θ ₁ ′ (forward transmission). It is not compressed until (reverse transmission) is reached.

The angles θ ₁ and θ ₁ ′ are smaller than the angles θ ₂ and θ ₂ ′, respectively, and larger than the angles ε ₁ and ε ₁ ′.

The operation will be described below.

The twist characteristics of the clutch disc 20 are as shown in FIG.
For example, from the state where the rotating torque is not input to the clutch plate 21 and the clutch disc 20 is not twisted (point 0),
Even if a slight rotational torque is input to the clutch plate 21 or the like, the frictional force of the friction washer 30 causes the clutch plate 21 or the like and the hub plate 23 to frictionally engage with each other. H _1/2
Is transmitted to the hub plate 23 via the friction washer 30 (section OF, when the preload is applied to the first coil spring 36, the amount of torque transmission is added accordingly). ). When the rotational torque increases, the friction washer 30 having a small friction coefficient starts to slip and the clutch disc 20 begins to twist and compresses the first coil spring 36. Therefore, the clutch disc 20 rotates according to the amount of compression, that is, the twist angle of the clutch disc 20. Torque is transmitted (section FG). At this time, the friction plate 32 and the retaining plate 22, which are frictionally engaged by the friction washer 33, rotate integrally, and the friction 32 and the hub plate 23 relatively rotate.

When the twist angle of the clutch disc 20 reaches the angle ε ₁ , the pin 35 comes into contact with one end of the long hole 32a of the friction plate 32 of the second hysteresis generating portion 28, so that a part of the rotational torque ( hysteresis H _2/2 torque corresponding to) the said friction washers 33
Is transmitted via (section GH).

When the transmission torque further increases, the friction washer 33
Then, the clutch disc 20 is twisted while the first coil spring 36 is further compressed, and the rotational torque is transmitted according to the twist angle (section HJ). Clutch disc
When the twist angle of 20 reaches the angle θ ₁ , the second coil spring 37 also begins to be compressed, and the rotational torque is transmitted according to the compression amount of each coil spring 36, 37 (section JC). When the clutch disc 20 is further twisted and the twist angle reaches the angle θ ₂ , the stopper pin 26 comes into contact with the hub plate 23, so that the clutch plate 21 and the hub plate 23 rotate integrally, and the clutch disc 20 becomes the angle. The transmission torque input to the clutch plate 21 and the like while being twisted by θ ₂ is transmitted to the hub plate 23 side.

Next, when the transmission torque input to the clutch plate 21 and the like starts to decrease, the clutch disc 20 tries to relatively rotate in the opposite direction to the above-mentioned case, but the variation amount (reduction amount) of this transmission torque is the amount of torque corresponding to the hysteresis of the friction washers 30 and _{33 (H 1/2 + H} 2/2), was added torque amount corresponding to the hysteresis H _1/2 of the friction washers 30 which act in opposite directions in the case of the above value If it is smaller than this, the torsion angle of the clutch disc 20 remains θ ₂ due to the frictional force of the friction washer 30 (section CB).
When the transmission torque further decreases, the friction washer
30 starts to slip and the twist angle of the clutch disc 20 decreases,
The torque according to this twist angle is transmitted (section BK).

When the twist angle of the clutch disc 20 returns to θ ₁ , the second
The coil spring 37 has a free spring length (point K), and only the torque corresponding to the pressing force of the first coil spring 36 is transmitted (section KP). When the clutch discs 20 are relatively rotated by an angle ε _s + ε ₁ 'from point B, the pin 35 abuts the other end of the long hole 32a of the friction plate 32, corresponds to the hysteresis H _2/2 to friction washer 33 begins to slip A decrease in rotational torque occurs (section PQ).

When the transmission torque further decreases (reverse torque is generated), the friction washer 33 also starts to slide due to the pressing force of the first coil spring 36, and the torsion angle of the clutch disc 20 decreases to the negative side. Torque is transmitted, and it operates similarly to section HJ.

Thus, the friction coefficient μ ₁ of the friction washer 30 is smaller than the friction coefficient μ ₂ of the friction washer 33,
In addition, since the friction plate 32 does not engage with the hub plate 23 unless the pin 35 abuts on the friction plate 32, when the rotational torque fluctuates, the first hysteresis generating portion is first irrespective of the twist angle position of the clutch disc 20. When the friction washer 30 of 27 slips and a torque amount (torque amount due to sliding resistance) corresponding to the hysteresis H _1/2 is transmitted through the washer 30 and the pin 35 comes into contact with the friction plate 32, in addition to this friction washer 33 of the second hysteresis generating section 28 is slip, torque amount corresponding to the hysteresis H _2/2 is transmitted through the washer 33 Te. That is, when the fluctuation of the transmission torque in each operating state is small, this torque fluctuates within a small hysteresis loop region where only the friction washer 30 slips. If there is a large torque fluctuation such that the pin 35 abuts the friction plate 32, the friction washer 33 slips, and if the fluctuation of the transmission torque is small after reaching a new torsion angle position, the transmission torque is small. Fluctuates about the torsion angle within a small hysteresis loop region in which only the friction washer 30 can slide.

As described above, according to the present invention, the hub plate and the torque transmitting member are frictionally engaged with each other, and the first friction engaging member having the first friction coefficient and the hub plate are fixed to each other. A pin that is provided, and a plate member that abuts on the pin and integrally rotates when relatively rotated by a predetermined angle with respect to the pin,
Frictionally engaging the plate member and the torque transmission member, and
Since the second frictional engagement member having the second friction coefficient larger than the first friction coefficient is provided, it is possible to obtain a suitable twisting characteristic in any operation region having a different main operation region. It is possible to reduce idle noise, abnormal noise of the drive system, muffled noise in the vehicle interior, and the like. Further, the clutch disk can be shared between different vehicle types, and there is an excellent effect that the production efficiency is improved.

[Brief description of drawings]

FIG. 1 is a side sectional view showing an embodiment of a clutch disc to which the present invention is applied, and FIG. 2 is a partial front view of a main portion of FIG.
FIG. 3 is a twist characteristic diagram of the clutch disc of FIG. 1, and FIG.
FIG. 5 is a side sectional view of a conventional clutch disc, FIG. 5 is a partially cutaway front view taken along the arrow V of FIG. 4, and FIG. 6 is a torsion characteristic diagram of the conventional clutch disc of FIG. 20 ... Clutch disc, 21 ... Clutch plate (first torque transmitting member), 23 ... Hub plate (second torque transmitting member), 25 ... Damper mechanism, 27 ... First hysteresis generating portion, 28 …… Second hysteresis generator.

Claims (1)

[Scope of utility model registration request] 1. A clutch disc having a rotation direction cushioning mechanism between a hub plate and a torque transmission member rotatable relative to the hub plate, wherein the rotation direction cushioning mechanism is provided between the hub plate and the torque transmission member. A spring mechanism that transmits torque according to the relative rotation angle between the members, and a first friction engagement member that frictionally engages the hub plate and the torque transmission member and that has a first friction coefficient. A pin fixed to the hub plate, a plate member that abuts on the pin and integrally rotates when relatively rotated with respect to the pin by a predetermined angle, and a friction member between the plate member and the torque transmission member. And a second coefficient larger than the first coefficient of friction
And a second friction engagement member having a friction coefficient of 1.