JPH0211767B2 - - Google Patents

Description

DETAILED DESCRIPTION OF THE INVENTION The present invention relates primarily to a damper disk assembly suitable for a clutch disk for an automobile.

Conventionally, damper disks with multi-stage rigidity and multi-stage hysteresis torque characteristics are constructed by fitting a sub-side plate in addition to an annular side plate to a hub that integrally has an outward flange, and using various types of torsion springs. A damper disk is known which has a torsion angle θ-torsion torque T characteristic as shown in FIG. 1 by elastically connecting these parts.

In the damper disk having the characteristics shown in FIG. 1, the torsional rigidity changes in three stages from the neutral state to the maximum twist, and the hysteresis torque changes in two stages. Here, the low torsion angle region (o ~
θ ₁ ) to absorb torque vibration of low torque,
The torsional rigidity is set low, and the hysteresis torque is also set low. For this reason, for example, when used in the clutch disc of a vehicle, the characteristic of this low torsion angle range makes it effective in reducing noise during idling and floating, but on the other hand, it is effective in suppressing noise during take-in and take-out during driving (when the accelerator is slightly applied). There is a problem in that when a quick depressing/releasing operation is performed, it may induce or aggravate the shaking of the vehicle body.

In view of the above-mentioned problems, the present invention has been developed so that when the torsional torque suddenly changes, when returning from the high torsional angle region, the first stage rigidity region having low torsional torque and low hysteresis torque characteristics is not passed through, and the torsional torque is directly changed to the negative side. By shifting to the second stage rigidity range, even if sudden torque fluctuations occur such as during tape-in and tape-out, torque fluctuations are reliably absorbed without inducing or aggravating problems such as vehicle body rocking. The present invention will now be described based on the drawings.

FIG. 2 is a partial vertical cross-sectional view of the damper disk according to the present invention applied to a clutch disk for an automobile. The central hub 1 has a spline 2 on its inner peripheral surface that fits into an output shaft (not shown).
The outer peripheral side has a flange 3 that projects in a direction perpendicular to the center line O ₁ -O ₁ . Two annular sub-side plates 4 and 5 are attached to the hub 1 on both sides of the flange 3.
It is rotatably supported by both plates 4 and 5.
are integrally connected by installing sub-pins 6 parallel to the center line O ₁ -O ₁ . A notch 7 extending in the circumferential direction is formed on the outer periphery of the flange 3, and window holes 8, 9 are formed in both plates 4, 5 at positions facing the notch 7.
A weak first torsion spring 10 (coil spring) is contracted in the window holes 8 and 9 so as to extend substantially in the circumferential direction. Two annular main plates 11, 1 are further provided on both sides of both plates 4, 5.
2 (clutch plate and retaining plate)
is rotatably supported by the hub 1, and both plates 11 and 12 are integrally connected by a stop pin 13 extending parallel to the center line _O1 - _O1 . An annular intermediate plate 14 is arranged between the sub-side plates 4 and 5 on the outside of the flange 3, and a stop pin 13 passes through the outer periphery of the plate 14, so that the main plates 1
1 and 12, and a side plate 15 is formed by the main plates 11 and 12 and the intermediate plate 14. Approximately rectangular window holes 1 extending in the circumferential direction are formed in opposing positions on the outer periphery of each plate 4, 5, 11, 12, and 14.
6, 17, 18, 19, 20 are formed,
A strong second torsion spring 21 (coil spring) extending in the circumferential direction is compressed.

The sub-pin 6 is slidably fitted into a circumferentially elongated hole 22 drilled in the intermediate plate 14, and the stop pin 13 is fitted into a circumferential hole 22 formed at the outer peripheral end of the sub-side plates 4, 5. It fits into the notches 23 and 24 which are long in the direction so as to be slidable in the circumferential direction. Main plate 11 and sub side plate 4
An annular resin washer 25 is interposed on the inner circumferential side between the main plate 12 and the sub-side plate 5, and a friction washer 2 is interposed on the inner circumferential side between the main plate 12 and the sub-side plate 5.
6. A friction plate 27 and a cone spring 28 that biases the friction plate 27 toward the plate 5 are interposed. Further, friction washers 29 and 30 are also interposed between the flange 3 and both sub-side plates 4 and 5. An annular facing 32 is fixed to the outer periphery of the main plate 11 via a cushioning plate 31.

Further, a key 33 extending parallel to the center line O ₁ -O ₁ passes through the flange 3, the sub-side plates 4, 5, and the intermediate plate 14. As shown in FIG. 3, the key 33 is a member with a substantially rectangular cross section, and the center
Two of them are provided on opposite sides of _O1 .
A notch 34 extending in the circumferential direction for fitting the key 33 is formed on the outer periphery of the flange 3, and a recess 35 having a circumferential length that allows the key 33 to fit is formed at one end of the notch 34 with a substantially radius. It is formed in such a way that it is concave inward. The bottom surface of the notch 34 is formed in a curved shape centered on the center _O1 , and the inner peripheral end surface of the key 33 is also formed in a corresponding curved shape. A recess 36 recessed toward the outer periphery is formed at a position approximately corresponding to the notch 34 on the inner periphery of the intermediate plate 14 that rotatably fits on the outer periphery of the flange 3 . The end surface is formed in a curved shape centered on the center _O1 , and the outer peripheral portion of the key 33 is abutted and engaged with one circumferential end of the recess 36 in FIG. 3, which shows the free state. Sub-side plates 4 and 5 are formed with substantially rectangular holes 37 and 38 that are substantially the same width as the circumferential direction of the key 33, into which the key 33 is fitted, and the inner circumferential end surfaces of the holes 37 and 38 are The concave portion 35 is disposed on substantially the same circumference as the bottom surface, and the outer circumferential end surface is disposed on substantially the same circumference as the outer circumferential end surface of the concave portion 36 . Note that the window hole 20 (18, 1
9) are of two types, one of which has both circumferential end surfaces matching the circumferential end surfaces of the window holes 17 (16) of the sub-side plates 4 and 5 in the free state (right side in Fig. 3). , both ends of the spring 21 are window holes 2
0 (18, 19) and window hole 17 (16), respectively. The other window hole 20 (18, 19)
The spring 21 has both ends shortened by a distance L ₁ in the circumferential direction with respect to the window holes 16 and 17, and is fitted into the spring 21.
are in pressure contact only with the window holes 20 (18, 19).

Next, the operation will be explained. When the facing 32 is pressed against the flywheel of the engine by a pressure plate (not shown) in FIG. 2, torque is transmitted from the flywheel to the facing 32, plate 31, side plate 15, spring 21,
It is transmitted to the output shaft via the sub-side plates 4 and 5, the spring 10, the flange 3, and the hub 1.

For example, when a torsional torque is applied to the facing 32 of the spline hub 1 in the direction of arrow _X1 in FIG. 3, the torque vibration is absorbed by the following operation. The following description will be made based on FIG. 1 showing the torsion angle θ-torsion torque T characteristic.

(First stage) When the side plate 15 is twisted with respect to the flange 3 from the neutral state in the _X1 direction (Fig. 3), when the torsion angle θ is between o and _θ1 , the first torsion spring 10 Since the second torsion spring 21 has a high rigidity,
The spring 21 acts like a rigid body and rotates the side plate 15 and the sub-side plates 4 and 5 integrally. As a result, torsion occurs between the plates 4, 5 and the flange 3, compressing the spring 10 and causing slippage on the surfaces of the friction washers 29, 30, generating a slight frictional torque.
The relationship A in FIG. 1 is obtained. At the same time, the side plate 15 and sub-side plates 4 and 5 rotate together in the _X1 direction from _the neutral state shown in FIG. The angle θ becomes θ ₁ .

(Second stage) In the state shown in FIG. 4b, the key 33 contacts the circumferential end surface of the notch 34, and the hub 1
Twisting does not proceed between the and sub-side plates 4 (5), and they are integrated via the key 33. Therefore, when the torsion angle θ is between θ ₁ and _{θ 2} , the space between the plate 4 (5) and the side plate 15 is twisted, and the spring 2 of the springs 21 that is not provided with the distance L ₁
1 is compressed, slippage occurs on the surfaces of washers 25 and 26, and frictional torque is generated, resulting in the relationship B in FIG. 1. At the same time, the side plate 15 further rotates relative to the flange 3 from the state shown in FIG. Then the state becomes c. On the other hand, by twisting the side plate 15 with respect to the sub-side plate 4 (5) integrated with the flange 3 via the key 33, the distance L ₁ in FIG. 3 is shortened, and when it becomes zero, the torsion angle θ becomes θ ₂ .

(Third stage) When the torsion angle θ is between θ ₂ and _{θ 3} , all the springs 21 are compressed, and the relationship C in FIG. 1 is obtained. When the torsion angle θ reaches θ ₃ , the stop pin 13 shown in FIG. 3 comes into contact with the circumferential end surfaces of the notches 23 and 24, and the plate 15 and the plates 4 and 5 are integrally connected via the stop pin 13. Torque from facing 32 (FIG. 2) is transmitted directly to hub 1.

(When returning from the maximum torsional angle θ ₃ ) In this case, the operation differs depending on whether the torsional angular velocity is small or large.

(a) When the torsional angular velocity is small; the operation is in the opposite direction to the above operation, and due to the friction of washers 25, 26, 29, and 30, the relationships C', B', and A' in FIG. 1 are obtained. In the first stage (o to θ ₁ ), the hysteresis torque obtained by the friction of the friction washers 29 and 30 is set to be extremely small, and A and A' are shown as the same straight line.

In this case, side plate 15 for hub 1
When the key 36 returns from the maximum torsion angle θ ₃ and the recess 36 is positioned on the outer circumferential side of the key 33 fitted in the recess 35, the key 33 comes out in the outer circumferential direction due to the centrifugal force, and the spring 10 (FIG. 3) With the relative rotation of the sub-side plate 4 in the reverse _X1 direction due to the repulsive force, the key 33 rotates in the reverse _X1 direction.

(b) When the torsional angular velocity is high; the side plate 15 rapidly rotates in the opposite _X1 direction relative to the hub 1.
Therefore, in this case, even when the recess 36 is located on the outer circumferential side of the key 33, the key 33 is not given an opportunity to be pulled out by centrifugal force, as shown in FIG. 4d. That is, due to the repulsive force of the spring 10 in a compressed state and the spring 21 (FIG. 3) that is momentarily expanded once and compressed again, the end surface 35a on the center side of the notch 34 of the recess 35 and the hole 37 (3)
8) and the end surface 37a on the end side of the notch 34 receive a force in a direction toward each other, thereby causing the key 3
3 is held. The clamping force of these end surfaces 35a and 37a (clamping portions) maintains a lever state that overcomes centrifugal force. The key 33 is connected to the recess 35 and the holes 37 and 38.
While the flange 3 and the sub-side plate 4 (5) are fitted together, the flange 3 and the sub-side plate 4 (5) are in a state of being integrally connected, and the first stage operation accompanying the expansion and contraction of the first torsion spring 10 does not occur. do not have.

Therefore, in this case, the disk exhibits characteristics without a low hysteresis torque region (first stage), and the characteristics are as shown in FIG.

(In the case of twisting from the free state in the _reverse The low hysteresis torque portion of the first stage never disappears.

As explained above, in the present invention, the flange 3 of the hub 1 which is an output member, the sub-side plate 4,
5 are connected in the disk circumferential direction by a weak first torsion spring 10, and the sub-side plates 4 and 5 and the input plate (intermediate plate 14) are connected in the disk circumferential direction by a strong second torsion spring 21. In the damper disk, a key 33 is disposed near the flange 3 and the outer periphery so as to be movable between a radially inner engagement position and a radially outer disengagement position.

The sub-side plates 4 and 5 are provided with guide engagement holes 37 and 38 for accommodating the key 33 so as to be movable between the two positions and immovable in the circumferential direction. Further, the flange 3 is provided with an engagement recess 35 in which the key 33 in the engagement position engages without being able to move in the circumferential direction when the sub-side plates 4, 5 and the flange 3 are twisted relative to each other. Furthermore, an input plate (14) and sub-side plates 4, 5
The cam part (inner peripheral part of the plate other than the inclined surface 37 and the recessed part 36) that contacts the key 33 and moves the key 33 from the disengaged position to the engaged position and holds it there when the input plate is twisted by a predetermined angle or more. (14).

Further, the key 33, the guide engagement holes 37, 38 and the engagement recess 35 that abut on the key 33 in the circumferential direction
The frictional force with the edges (37a, 35a) is set to prevent the key from moving from the engaged position to the disengaged position due to centrifugal force when the pressure contact force between the two suddenly and temporarily decreases. are doing.

According to this configuration, for example, a large torque is transmitted in the disk rotation direction, and the second torsion spring 21 is compressed and the input plate (1
1, 12, 14) are twisted relative to the sub-side plates 4, 5, and the torque suddenly and significantly decreases, the key 33 can be held in the previously engaged position and the As a result, the torsional operation characteristics can be transferred from the second stage torsion region on the positive side to the second stage torsion region on the negative side without passing through the first stage torsion region where the torsional rigidity is low. Therefore, according to the present invention, when adopted for a clutch disk for a vehicle, for example, even when sudden torque fluctuations occur such as during tape-in and tape-out, the present invention does not induce or promote defects such as shaking of the vehicle body. This has the advantage of being able to reliably absorb torque fluctuations.

Note that in carrying out the present invention, the following configuration can also be adopted.

(i) In order to back up the extraction of the key 33 from the recess 35, a spring force may be applied to the key 33 radially outward by, for example, disposing a spring on the inner peripheral side of the recess 35.

(ii) The recesses 35 may be provided at both ends of the notch 34 in the circumferential direction. In this case, the characteristics unique to the present invention can be obtained even when twisted in the reverse _X1 direction.

(iii) Pass the key 33 through the main plates 11 and 12, and insert the recess 36 into the main plates 11 and 12.
If the intermediate plate 14 is formed, the intermediate plate 14 can be omitted.

(iv) The springs 10 and 21 are not limited to coil springs; for example, rubber-like elastic bodies may be used.

[Brief explanation of drawings]

1 and 5 are graphs showing the torsion angle-torsion torque characteristics, FIG. 2 is a longitudinal partial side view of the damper disk assembly according to the present invention applied to a clutch disk for an automobile, and FIG. Figure -
FIG. 4 is a vertical partial front view showing the operating state. 1...Hub, 3...Flange,
4, 5...Sub side plate, 10...First torsion spring, 14...Intermediate plate 14
(input plate), 21...second torsion spring, 33...key, 35...engaging recess, 36a
... Inclined surface (cam part), 37, 38 ... Guide engagement hole.

Claims (1)

[Claims] 1. An outward flange is integrally provided on a hub that is an output member, an annular input plate and a pair of sub-side plates are arranged on the radially outer side of the hub, and the flange and sub-side plates are connected to a weak first torsion spring. The sub-side plate and the input plate are connected in the disk circumferential direction by a strong second torsion spring, and the key is placed near the outer circumference of the flange between the radially inner engagement position and the radially outer engagement position. The key is placed on the sub-side plate so that it can be moved between the two positions, and
A guide engagement hole is provided that is accommodated in a manner that cannot be moved in the circumferential direction, and when the sub-side plate and the flange are twisted relative to each other by a predetermined angle, the key in the engagement position is engaged in a way that is not movable in the circumferential direction. An engagement recess is provided in the flange, and a cam part is formed in the input plate that contacts the key to move the key from the disengaged position to the engaged position and hold it there when the input plate and sub-side plate are twisted relative to each other. The frictional force between the key and the edges of the guide engagement hole and the engagement recess that contact the key in the circumferential direction is reduced by centrifugal force when the pressure contact force between the key and the edge decreases suddenly and temporarily. A damper disk assembly configured to prevent a key from moving from an engagement position to a disengagement position due to force.