JP3225182B2 - Spring seat, damper mechanism and torsional characteristic changing method - Google Patents

Description

DETAILED DESCRIPTION OF THE INVENTION

[0001]

The present invention relates to a spring seat, a damper mechanism and a method for changing its torsional characteristics.

[0002]

2. Description of the Related Art For example, a clutch disk assembly used for a clutch device of a vehicle includes a disk-shaped input side plate,
An output-side hub having an integral flange on the outer periphery, and a coil spring disposed between the input-side plate and the flange to restrict relative rotation between the two. A punched window hole for accommodating the coil spring is formed in the flange. Both ends in the circumferential direction of the coil spring are in contact with the edge of the window hole. Further, the input side plate is formed with support portions for supporting both ends in the circumferential direction of the coil spring. Thus, when the input side plate rotates, torque is transmitted to the hub via the coil spring.

Further, a clutch disc assembly of a separated hub type in which a flange of an output side hub is separated from a hub portion and both are connected by a small coil spring is also used. In this clutch disk assembly, the torsion angle is widened and two-stage characteristics are obtained. At both ends of the small coil spring, a pair of spring seats is arranged. The flange and the hub have teeth that are circumferentially spaced and mesh with each other.

[0004]

In the conventional clutch disk assembly, the teeth of the hub are arranged in a free state with a phase shift between the teeth of the flange on the negative side (opposite in the rotational direction). That is, the torsion angle of the hub with respect to the flange is wide on the positive side (rotational direction) and narrow on the negative side.

However, it is necessary to suppress the generation of abnormal noise by changing the torsional angle characteristics depending on the type of vehicle. The twist angle can be changed by changing the shapes of the flange and the hub, but processing these members increases the cost. An object of the present invention is to make it possible to change the torsional characteristics of a damper mechanism at low cost.

[0006]

According to a first aspect of the present invention, there is provided a spring seat for receiving both ends of a coil spring disposed between an input rotary member and an output rotary member. It has. The seat portion abuts one end of the coil spring and has a first supported surface supported by one of the input rotary member and the output rotary member, and a second supported surface supported by the other and protruding from the first supported surface. . The insertion portion extends from the seat portion into the coil spring.

According to a second aspect of the present invention, there is provided a spring seat for receiving both ends of a coil spring disposed between an input rotary member and an output rotary member, and includes a pair of first and second spring seats. . The first spring seat includes a first seat portion and a first insertion portion. First
The seat portion abuts one end of the coil spring and has a first supported surface supported by one of the input rotary member and the output rotary member, and a second supported surface supported by the other and protruding from the first supported surface. . First insertion portions, Ru extends from the seat portion in the coil spring. The second spring seat includes a second seat portion and a second insertion portion. The second seat portion is in contact with the other end of the coil spring, is supported by the other of the input rotary member and the output rotary member, the third supported surface, and is supported by one of the input rotary member and the output rotary member and is supported by the third rotary member. And a fourth supported surface protruding from the surface. The second insertion portion extends from the second seat portion into the coil spring.

According to a third aspect of the present invention, in the spring seat according to the second aspect, the first spring seat and the second spring seat have the same shape. The damper mechanism according to claim 4 is arranged between the input rotating member, the output rotating member arranged to be rotatable relative to the input rotating member within a predetermined angle range, and between the input rotating member and the output rotating member. A coil spring and a spring seat according to claim 2 or 3 are provided.

According to a fifth aspect of the present invention, there is provided a method for changing a torsional characteristic of a damper mechanism, comprising: an input rotating member; an output rotating member arranged to be rotatable relative to the input rotating member within a predetermined angle range;
In a damper mechanism having a coil spring disposed between an input rotary member and an output rotary member, a spring seat disposed at both ends of the coil spring and supported by the input rotary member and the output rotary member includes By shifting the height of the first supported surface supported and the second supported surface supported by the output rotating member, the phase of the input rotating member and the output member in the free state is changed. Changing the phase of the input side member and the output side member by this method is easy and inexpensive.

[0010]

DETAILED DESCRIPTION OF THE PREFERRED EMBODIMENTS A clutch disk assembly 1 according to an embodiment of the present invention shown in FIG. 1 has a torque from an engine (not shown) arranged on the left side of FIG. 1 arranged on the right side of FIG. For transmitting and shutting off to a transmitted transmission (not shown). In FIG. 1, OO
Is the rotation axis of the clutch disk assembly 1, and the direction of the arrow R1 in FIGS. 2 and 11 is the rotation direction.

The clutch disk assembly 1 mainly includes:
The hub 2 as an output-side member, the clutch disk 3 and the retaining plate 4 as an input-side member, the sub-plate 5 as an intermediate member, and the relative rotation between the sub-plate 5 and the hub 2 are limited. Of the small coil spring 6, the large coil spring 7 arranged between the plates 3, 4 and the sub-plate 5 so as to limit the relative rotation of the two, and the plates 3, 4 and the hub 2 And a frictional resistance generating mechanism 8 that generates a predetermined frictional force when relative rotation occurs between them.

The hub 2 is located at the center of the clutch disc assembly 1 and is connected to a transmission shaft (not shown). The hub 2 has a cylindrical boss 2 extending in the axial direction.
a and a flange 2b integrally formed on the outer periphery of the boss 2a
It is composed of A plurality of projections 2c are formed on the outer periphery of the flange 2b at equal intervals in the circumferential direction. As shown in FIG. 3, notches 2d for receiving both ends in the circumferential direction of the small coil spring 6, which will be described later, are formed at two locations facing the flange 2b in the radial direction. Boss 2
The shaft of the transmission (not shown)
Is formed with a spline hole 2e for spline engagement.

A sub plate 5 is arranged on the outer periphery of the flange 2b of the hub 2. The sub-plate 5 is a disk-shaped plate. As is apparent from FIG. 2, the sub-plate 5 has four protrusions 5a extending radially outward. Each protruding portion 5a is formed with a window hole 5b extending in the circumferential direction. An outer notch 5c is formed between each protrusion 5a. A hub 2 is provided on the inner peripheral side of the sub plate 5.
The inner projection 5d is formed in a portion corresponding to the space between the projections 2c. A predetermined circumferential gap is provided between the protrusion 2c and the inner protrusion 5d, so that the hub 2 and the sub-plate 5 can rotate by a predetermined angle.

[0014] In the inner peripheral side of the sub Plate 5, the hub 2
An inner notch 5e is formed at two places corresponding to the notch 2d. A small coil spring 6 is arranged in the notch 2d and the inner notch 5e. Seat members 40 are arranged at both ends of the small coil spring 6. As shown in detail in FIG. 11, the seat member 40 includes a disc-shaped seat portion 41 and an insertion portion 42 extending from the seat portion 41 into the small coil spring 6. The seat portion 41 includes a first supported portion 43 and a second supported portion 44 which protrudes in a circumferential direction from the first supported portion 43. R
In the sheet member 40 on the first side, the first supported portion 43 is supported by the inner notch 5e, and the second supported portion 44 is supported by the notch 2d. Conversely, in the sheet member 40 on the R2 side,
The first supported portion 43 is supported by the notch 2d, and the second supported portion 44 is supported by the inner notch 5e. As a result,
The notch 2d is shifted in phase toward the R1 side with respect to the inner notch 5e. In this way, in the free state, the projection 2c of the hub 2 is arranged at the center in the circumferential direction between the inner projections 5d of the sub plate 5. That is, from the free state, the hub 2 can rotate relative to the sub-plate 5 by 5 degrees on the R1 side and the R2 side, respectively.

If the portion supported by one member on the outer end face of the seat portion 41 does not protrude, the notch 2d and the inner notch 5e have the same phase. In this case, in the free state, the protrusion 2c of the hub 2 is
And are shifted to the R2 side. That is, from the free state, the hub 2 can rotate relative to the sub-plate 5 by 7 ° toward the R1 side and 3 ° relative to the R2 side. That is, in this embodiment, by changing the torsional characteristics of the hub 2 and the sub-plate 5 over between conventional small coil springs 6 by changing the shape of the sheet member 40. As described above, the shape change of the sheet member 40 is easier and less expensive than the shape change of the cutout portion of the hub or the sub plate. Further, since all the sheet members 40 have the same shape, the manufacturing cost is reduced.

The characteristic of the torsion angle is not limited to this embodiment, but may be changed to various angles.
The clutch plate 3 and the retaining plate 4 are arranged on both sides of the sub plate 5. The clutch plate 3 and the retaining plate 4 are a pair of substantially disk-shaped members, and are rotatably disposed on the outer peripheral side of the boss 2 a of the hub 2. The clutch plate 3 and the retaining plate 4 are fixed to each other by an abutment pin 11 at an outer peripheral portion. The contact pin 11 passes through an outer notch 5 c formed in the sub-plate 5. Since a predetermined gap is secured in the circumferential direction between the contact pin 11 and the outer notch 5c, the plates 3, 4 and the sub-plate 5 can be relatively rotated.

On the outer periphery of the clutch disk 3, a friction connecting portion 10 is arranged. The friction connecting portion 10 mainly includes an annular cushioning plate 12 and a friction facing 13. The cushioning plate 12 has an annular portion 12 a fixed to the clutch plate 3 by a contact pin 11. A plurality of cushioning portions 12b are formed on the outer periphery of the cushioning plate. Friction facings 13 are fixed to both surfaces of the cushioning portion 12b. An engine-side flywheel (not shown) is disposed on the left side of the friction facing 13 in FIG. 1, and when the friction facing 13 is pressed against the flywheel by a pressure plate (not shown), the clutch disc assembly 1 Engine-side torque is input.

Window holes 3a and 4a are formed in the clutch plate 3 and the retaining plate 4 at positions corresponding to the window holes 5b of the sub-plate 5, respectively. The large coil spring 7 is disposed in the window holes 3a and 4a. Pressing portions 3b cut and raised outward in the axial direction are provided on both radial sides of each window hole 3a and window hole 4a,
A holding portion 4b is formed.

There are a total of four large coil springs 7,
It is accommodated in each window hole 5b. 7th coil spring 7
Inside, a small diameter coil spring 8 is arranged.
Both ends of the springs 7 and 8 in the circumferential direction are provided with respective window holes 5 b and 3 a
And 4a are in contact with both circumferential ends. The large coil spring 7 described above is provided on the retaining plate 4.
Pressing portion 4b and clutch plate 3 pressing portion 3
The movement in the radially outward and axial directions is restricted by b.

On the inner peripheral side of the clutch plate 3 and the retaining plate 4, four holes 3c, 4c with which a part (described later) of the frictional resistance generating mechanism 8 engages are formed at regular intervals in the circumferential direction. I have. Next, the frictional resistance generating mechanism 8 will be described. The frictional resistance generating mechanism 8 is formed of an annular member disposed on the outer peripheral side of the boss 2a between the inner peripheral portion of the clutch plate 3 and the inner peripheral portion of the retaining plate 4 in the axial direction. The members constituting the frictional resistance generating mechanism 8 are a first friction washer 14, a second friction washer 15, a first cone spring 16, a second cone spring 17, and a third friction washer 18.

The first friction washer 14 is a disc-shaped resin plate. 1st friction washer 1
4, as shown in FIGS. 5 to 7, the inner peripheral end is close to the boss 2 a, and one side surface is in contact with the flange 2 b of the hub 2 and the side surface of the projection 2 c on the transmission side. First
The friction washer 14 has a disk portion 14a and an annular protrusion 14b protruding from the inner peripheral side of the disk portion 14a toward the transmission. An annular cutout groove 14c is formed in the annular protrusion 14b on the transmission side. Further, four protrusions 14d extending radially outward are formed on the outer periphery of the disk portion 14a.

A first cone spring 16 is disposed between the first friction washer 14 and the retaining plate 4 in the axial direction. The outer peripheral end of the first cone spring 16 is supported by the retaining plate 4, and the inner peripheral end is in contact with an annular notch groove 14 c formed in an annular protrusion 14 b of the first friction washer 14. The first cone spring 16 is arranged in a compressed state and urges the first friction washer 14 toward the flange 2 b and the protrusion 2 c of the hub 2. The first cone spring 16 has a plurality of notches formed on the outer peripheral side. The notch is formed to reduce a change in the urging force of the first cone spring 16 when the posture of the first cone spring 16 changes due to wear of the first friction washer 14.

The second friction washer 15 is shown in FIG.
10 is a disc-shaped member, as is apparent from FIG.
On the outer peripheral side of the friction washer 14, the first friction washer 14 is disposed substantially concentrically and concentrically with the plane on which the first friction washer 14 is disposed. The second friction washer 15 is formed of the same material as the first friction washer 14, and has the same friction coefficient. The second friction washer 15 includes a disc 15a and a disc 15a.
And an annular protruding portion 15b protruding toward the transmission on the inner peripheral side of the vehicle. The engine-side end surface of the disk portion 15 a is in contact with the inner peripheral end surface of the sub-plate 5.
Four notches 15e are formed at equal intervals in the circumferential direction on the transmission-side end face of the annular projection 15b. The projection 14d of the first friction washer 14 is engaged in the notch 15e so as to be relatively non-rotatable in the circumferential direction and movably in the axial direction. A predetermined gap is provided between the projection 14d and the recess 15e in the axial direction. Four protrusions extending toward the transmission are formed between the recesses 15e on the annular protrusion 15b. This projection is composed of two snap projections 15c and two rod-shaped projections 15d. Here, protrusions of the same type are arranged so as to oppose each other in the radial direction. Snap projection 15
c is divided into two by a slit extending in the axial direction, and has a hook-shaped snap at the tip. The snap projection 15c is inserted into a hole 4c formed in the retaining plate 4. Note that the second friction washer 15 is less likely to come off the retaining plate 4 in the axial direction due to the snap portion formed on the snap projection 15c. The rod-shaped projection 15d is inserted into another hole 4c of the retaining plate 4.

The second cone spring 17 is disposed between the second friction washer 15 and the retaining plate 4 in the axial direction. The second cone spring 17 has a plurality of notches formed on the inner peripheral side. The notch is formed when the posture of the second cone spring 17 changes due to wear of the second friction washer 15.
It is formed to reduce the change in the urging force of the cone spring 17. The second cone spring 17 is arranged in a compressed state, and the outer peripheral end thereof is
, And the inner peripheral end, ie, the projection 17b, is in contact with the transmission-side side surface of the annular projection 15b of the second friction washer 15. Thus, the second cone spring 17 urges the second friction washer 15 toward the transmission-side side surface of the sub-plate 5. At this time, the urging force of the second cone spring 17 is set to be larger than the urging force of the first cone spring 16. The notch 17 a of the second cone spring 17 is provided with the second friction washer 15.
Snap projection 15c, rod-shaped projection 15d and concave portion 15
e, so that the second cone spring 17 and these members do not interfere with each other.

A third friction washer 18 is disposed axially between the inner peripheral portion of the clutch plate 3 and the inner peripheral ends of the flange 2b of the hub 2 and the sub plate 5. The third friction washer 18 is formed of the same material as the first friction washer 14 and the second friction washer 15, and has the same friction coefficient. The third friction washer 18 has a transmission side surface in contact with the side surface of the flange 2 b and the inner peripheral end side surface of the sub plate 5, and an engine side surface in contact with the clutch plate 3. A snap projection 18 a (see FIG. 1) extending toward the engine in the axial direction is formed on the outer peripheral portion of the third friction washer 18.
8a is engaged in a hole 3c formed in the clutch plate 3. The snap projection 18a has the same shape as the snap projection 15c of the second friction washer 15 described above. An annular projection 18b is formed on the inner peripheral portion of the third friction washer 18 so as to extend toward the engine in the axial direction. The inner peripheral end of the clutch plate 3 is in contact with the outer peripheral side of the annular protrusion 18b.

Next, the operation of the clutch disk assembly 1 will be described. When the friction facing 13 is pressed against a flywheel (not shown) on the engine side, the torque of the flywheel on the engine side increases the clutch plate 3.
And input to the retaining plate 4. This torque is transmitted to the hub 2 via the large coil spring 7, the coil spring 8, the sub plate 5, and the small coil spring 6, and further transmitted to a transmission-side shaft (not shown).

Flywheel on engine side (not shown)
When the torsional vibration is transmitted from the clutch plate assembly 1 to the clutch disk assembly 1, periodic relative rotation occurs between the plates 3, 4 and the hub 2. Each of the springs 6 to 8 is compressed, and friction is generated by the frictional resistance generating mechanism 8. At this time, hysteresis occurs in the relationship between the torsion angle and the torsion torque.

In the small range of the torsion angle, the small coil spring 6 is compressed in the circumferential direction, and the first friction washer 14 and the third friction washer 18
Slides on the flange 2b and the protrusion 2c of the hub 2. Due to the characteristics of low rigidity and low hysteresis torque at this time, torsional vibration having a small displacement angle is effectively attenuated.

In a large range of the torsion angle, the small coil spring 6 is compressed and the sub-plate 5 and the hub 2 rotate integrally, and relative rotation occurs between these and the plates 3 and 4. At this time, the large coil spring 7 and the coil spring 8 are compressed, the first friction washer 14 slides on the flange 2b of the hub 2, and the second friction washer 15 slides on the inner peripheral side surface of the sub plate 5, Further, the third friction washer 18 slides on the flywheel side surface of the flange 2 b of the hub 2 and the inner peripheral side flywheel side surface of the sub plate 5. Here, since the urging force of the second cone spring 17 is set to be larger than the urging force of the first cone spring 16, a large frictional force is generated. Due to the characteristics of high rigidity and high hysteresis torque at this time, torsional vibration having a large displacement angle is effectively attenuated.

As described above, appropriate characteristics can be obtained depending on the type of the torsional vibration.
Is effective in damping torsional vibration.

[0031]

According to the present invention, in the spring seat, the height of the first supported surface supported by the input rotary member and the height of the second supported surface supported by the output rotary member are shifted, so that the free state is achieved. To change the phase of the input rotary member and the output member. Changing the phase of the input side member and the output side member by this method is easy and inexpensive.

[Brief description of the drawings]

FIG. 1 is a schematic longitudinal sectional view of a clutch disk assembly as one embodiment of the present invention.

FIG. 2 is a partially cut-away view taken along the arrow II in FIG. 1;

FIG. 3 is a plan view of a hub.

FIG. 4 is a sectional view taken along line IV-IV of FIG. 3;

FIG. 5 is an enlarged view of a circle A in FIG. 1;

FIG. 6 is a plan view of a first friction washer.

7 is a sectional view taken along line VI-VI of FIG.

FIG. 8 is a plan view of a second friction washer.

FIG. 9 is a sectional view taken along line IX-IX of FIG. 8;

FIG. 10 is a sectional view taken along line XX of FIG . 8 ;

FIG. 11 is a plan view around a flange.

──────────────────────────────────────────────────続 き Continued on front page (58) Field surveyed (Int.Cl. ⁷ , DB name) F16F 15/123 F16F 15/134 F16D 11/00-23/14

Claims (5)

(57) [Claims] 1. A spring seat for receiving both ends of a coil spring disposed between an input rotary member and an output rotary member, the spring seat being in contact with one end of the coil spring and being connected to the input rotary member and the output rotary member. A sheet portion having a first supported surface supported on one side and a second supported surface supported by the other and protruding from the first supported surface; and an insertion portion extending from the seat portion into the coil spring. Spring seat provided. 2. A pair of spring seats for receiving both ends of a coil spring disposed between an input rotary member and an output rotary member, wherein the spring seat is formed by a pair of first and second spring seats. The first spring seat is in contact with one end of the coil spring, and a first supported surface supported by one of the input rotation member and the output rotation member and a second surface supported by the other and protrudes from the first supported surface. A first seat portion having a second supported surface, and a first insertion portion extending from the first seat portion into the coil spring, wherein the second spring seat is provided at the other end of the coil spring. A third supported surface that abuts and is supported by the other of the input rotary member and the output rotary member; and the third supported surface supported by the one of the input rotary member and the output rotary member A second sheet portion having a fourth supported surfaces to more projecting, second extending said coil inner spring from said seat portion
A spring seat comprising an insertion portion. 3. The spring seat according to claim 2, wherein said first spring seat and said second spring seat have the same shape. 4. An input rotating member, an output rotating member arranged so as to be rotatable relative to the input rotating member within a predetermined angle range, and a coil spring arranged between the input rotating member and the output rotating member. A damper mechanism comprising: the spring seat according to claim 2. 5. An input rotating member, an output rotating member arranged to be rotatable relative to the input rotating member within a predetermined angle range, and a coil spring arranged between the input rotating member and the output rotating member. A method of changing the torsional characteristics of a damper mechanism comprising: a first spring supported by the input rotary member in a spring seat disposed at both ends of the coil spring and supported by the input rotary member and the output rotary member. Twist of a damper mechanism that changes the phase of the input rotary member and the output member in a free state by shifting the height of a supported surface and a second supported surface supported by the output rotary member. How to change characteristics.