Classifications

• • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
  • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
  • F16F—SPRINGS; SHOCK-ABSORBERS; MEANS FOR DAMPING VIBRATION
  • F16F15/00—Suppression of vibrations in systems; Means or arrangements for avoiding or reducing out-of-balance forces, e.g. due to motion
  • F16F15/10—Suppression of vibrations in rotating systems by making use of members moving with the system
  • F16F15/12—Suppression of vibrations in rotating systems by making use of members moving with the system using elastic members or friction-damping members, e.g. between a rotating shaft and a gyratory mass mounted thereon
  • F16F15/1202—Suppression of vibrations in rotating systems by making use of members moving with the system using elastic members or friction-damping members, e.g. between a rotating shaft and a gyratory mass mounted thereon the damping action being at least partially controlled by centrifugal masses

Definitions

• the present invention is directed to a damper disk used for a clutch disk of an automobile or the like.
• a damper disk used for a clutch disk of an automobile or the like.
• the relative torsional operation between an input-side member and an output-side member is determined according to operating conditions.
• devices for temporary regulation More specifically, the present invention provides a disk in which an input member and an intermediate member are connected by a strong damper spring, and an intermediate member and an output member are connected by a weak damper spring. It is intended for a device for temporarily restricting the relative torsional movement with members.
• a locker is required in response to a change in the relative angular position between the input member and the output member.
• the arm moves between the torsional operation restriction position and the release position. That is, in the device described in this publication, the position of the lock arm is controlled by positively utilizing the centrifugal force, as is clear from the description in the lower half of the lower right column on page 13 of the publication. Absent.
• a damper disk with two types of damper springs connected in series via an intermediate member may cause the following problems at low speed rotation.
• a jerky running state will occur due to the effect of a weak damper spring.
• the present invention seeks to provide a structure that solves the above problems.o
• the input member, the intermediate member and the output member are arranged concentrically and rotatably relative to each other, and the input member and the intermediate member are connected to each other in a circumferential direction by a strong damper spring.
• the output members are connected in their circumferential direction by a weak damper spring,
• a support shaft extending in the axial direction is provided, and the lock arm extending substantially in the circumferential direction is rotatably supported by the support shaft so as to be movable between an engaged position and a released position.
• the center of gravity of the drum is displaced in the circumferential direction with respect to the center of the spindle, so that the centrifugal force caused by the rotation of the disc allows the lick arm to rotate from the release position to the engagement position,
• a return spring for urging the hook arm from the engagement position to the release position is provided, and an engagement portion with which the mouth arm is circumferentially engaged at the engagement position is provided on the output member.
• the centrifugal force of the lock arm overcomes the urging force of the return spring, whereby the mouth arm moves to the engagement position and engages with the output member.
• the relative twisting operation between the intermediate member and the output member is prevented.
• the buckle arm is returned to the release position by the urging force of the return spring, and the intermediate member and the output member can perform a twisting operation.
• FIG. 1 is a partially cutaway front view of a damper disk employing the embodiment of the present invention
• FIG. 2 is a cross-sectional view taken along the line II-II of FIG. 1
• FIG. 3 is an enlarged partial view of FIG. The figure is an enlarged partial view of FIG.
• FIG. 1 is a partially cutaway front view of the embodiment of the present invention
• FIG. 2 is a sectional view taken along the line III-III of FIG.
• the output hub 2 connected to the output shaft 1 (only the center line is shown in FIG. 2) is provided with a small-diameter output flange 3 (output member) integrally on the outer periphery.
• a pair of annular sub-plates 5 (intermediate members) fit the inner circumference to or close to the outer circumference of the hub 2 It is arranged in a state.
• a pair of annular side plates 6 and 7 are arranged around the hub 2 on both sides of the pair of sub plates 5.
• a facing 9 is attached to the outer periphery of the side plate 6 via a cushioning plate 8. Torque from the engine to the side plate 6 via the forcing 9 and the cushioning plate 8 by pressing the forcing 9 against the engine flywheel (not shown) with a pressure plate (not shown). Is introduced.
• the inner periphery of the side plate 6 is supported on the outer periphery of the hub 2 via a bush 10, and the inner periphery of one sub-plate 5 is also supported on the outer periphery of the bush 10.
• the two side plates 6 and 7 are fixed to each other at a plurality of locations on the outer peripheral portion by axial stopper pins 11. Both sub-plates 5 are also fixed to each other at a position radially inward of the stopper pin 11 in the disk radial direction by sub-pins 12 in the axial direction.
• damper springs 15 compression coil springs
• Each damper spring 15 is accommodated in a window provided in the sub plate 5 and the side plates 6 and 7, and the sub plate 5 and the side plates 6 and 7 are connected in the disk circumferential direction.
• Two weak damper springs 16 are provided near the inner periphery of the disk.
• Each damper spring 16 is accommodated in a notch provided on the outer peripheral portion of the flange 3, and a notch provided on the inner peripheral portion of the subplate 5 has ears of a spring receiver 17 on which both ends are seated.
• the subplate 5 and the flange 3 are connected circumferentially by this damper spring 16 Have been.
• the torque introduced from the facing 9 to the side plates 6 and 7 is transmitted to the sub plate 5 via the damper spring 15 and from the sub plate 5 via the damper spring 16. It is transmitted to flange 3, hub 2, and output shaft 1.
• friction washer 20 is provided between the inner peripheral portion of each subplate 5 and the flange 3 as shown in FIG. Or, a wave spring 21 is interposed.
• a friction plate 22 is arranged between each of the side plates 6 and 7 and the sub plate 5 adjacent thereto.
• the flexion plate 22 has a bent claw 23 on the outer periphery, and the claw 23 is inserted into a circumferential notch 24 provided on the side plates 6 and 7.
• a friction washer 25 having a large friction coefficient is arranged between each friction plate 22 and the sub plate 5.
• a friction washer 26 having a small frictional force is arranged between the side plate 6 and the friction plate 22 adjacent thereto.
• a friction plate 27 is arranged between the other side plate 7 and the friction plate 22 to cause friction between the friction plate 27 and the friction plate 22 adjacent thereto.
• a friction washer 26 with low power is arranged.
• the friction plate 27 is fitted in such a manner that the bent claw portion on the outer periphery cannot be moved relative to the notch on the inner periphery of the side plate 7 in the circumferential direction.
• a cone spring 28 is interposed between the friction plate 27 and the side plate 7.
• the friction plate 22 When the side plates 6 and 7 are twisted with respect to the sub plate 5, the friction plate 22 has a large friction coefficient while the torsion angle is small because the friction coefficient of the friction washer 25 is large. Therefore, the friction washer 26 having a small coefficient of friction has friction with the surface thereof.
• the torsion angle reaches a predetermined value
• the claw portion 23 comes into contact with the edge of the notch 24, so that the friction plate 22 can rotate further relative to the side plates 6, 7. Therefore, thereafter, the friction plate 22 moves together with the side plates 6 and 7, and a strong frictional force is generated on the surface of the friction washer 25.
• the frictional force is generated in this manner, and the vibration of the transmission torque can be effectively absorbed by the magnitude of the frictional force changing stepwise according to the torsion angle.
• the above mechanism includes the above-described pin 30 (support shaft), a lock arm 31 and a return spring 32, which use the above-mentioned sub-pins 12. It is built into the inner periphery of the disk as follows.
• the pins 30 are provided at a plurality of locations radially inward of the sub-pins 12 and spaced apart in the circumferential direction of the disk. Each sub-pin 30 extends between the two sub-plates 5 and 5 in the disk axis direction, and both ends are fitted into holes of the sub-plate 5.
• the lock arm 3] is a plate-like member having a bent structure that extends substantially in the disk circumferential direction, and two lock arms are used for the entire disk.
• the lock arm 31 is disposed between the sub-plates 5 and 5, and the rear end in the disk rotation direction R is rotatably supported by one of the plurality of pins 30. That is, the center of gravity of the log arm 31 is displaced forward of the pin 30 in the disk rotation direction. Therefore, when centrifugal force due to the rotation of the disk is generated in the mouth arm 31, the centrifugal force becomes Acts to move the hook arm 31 radially outward with respect to the pin 3 ⁇ in the disk radius direction.
• the mouth arm 31 includes a pair of side portions 35 (FIG. 3) extending along the surface of each sub-plate 5 and two connecting portions 36, 37 connecting the side portions 35 together. It has.
• One connecting portion 36 is continuous with the ⁇ portion of the both sides 35 on the outer side in the disk radial direction near the pin 30.
• the rear end of the connecting portion 36 in the disk rotation direction R protrudes beyond the side portion 35 to form an engaging portion 40.
• the other connecting portion 37 is continuous with the outer edge of the front end of the side portion 35 in the disk rotation direction.
• the flange 3 is provided with a notch (engaging portion 41) in its outer peripheral portion in the vicinity of the engaging portion 40, so that the engaging portion 41 is engaged with the engaging portion 41. Has become.
• the return spring 32 is constituted by a torsion spring having a small number of coil turns, and its coil portion is fitted on the outer periphery of a collar attached to one of the two adjacent sub-pins 12.
• the straight line portion is engaged with the outer periphery of the other sub-pin 12 from the inside in the disk radial direction.
• the other straight portion of the return spring 32 is longer, and is engaged with the connecting portion 36 from the outside in the disk radial direction on the connecting portion 37 side of the pin 30.
• the mouth arm 31 moves radially outward due to its own centrifugal force, overcoming the elasticity of the return spring 32, and the two-dot chain line. Occupies the engagement position indicated by.
• the engaging portion 40 enters the engaging portion 41, so that the rotation of the flange 3 relative to the lock arm 31 (that is, the sub-plate 5) is restricted.
• the lock arm 31 engages with the pin 37 or the sub-pin 12 at the connection portion 37 or the vicinity thereof, thereby preventing movement beyond a predetermined range. Have been.
• the operation of the lockarm 31 for regulating the relative rotation between the intermediate member (subplate 5) and the output member (flange 3) is adjusted in accordance with the centrifugal force (that is, the disk). (According to the number of rotations), the structure shown in the figure is applied to the clutch disk of the car to prevent the car from being jerky when the accelerator pedal is operated in a very low-speed driving state. Can be prevented.

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• Engineering & Computer Science (AREA)
• General Engineering & Computer Science (AREA)
• Physics & Mathematics (AREA)
• Acoustics & Sound (AREA)
• Aviation & Aerospace Engineering (AREA)
• Mechanical Engineering (AREA)
• Mechanical Operated Clutches (AREA)

Applications Claiming Priority (2)

Publications (1)

Family

ID=13799909

Family Applications (1)

Country Status (3)

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Citations (4)

Family Cites Families (3)

• 1989
  • 1989-07-14 JP JP8334789U patent/JPH0322130U/ja active Pending
• 1990
  • 1990-06-22 WO PCT/JP1990/000817 patent/WO1991001455A1/ja active Application Filing
  • 1990-06-22 DE DE19904091245 patent/DE4091245T1/de not_active Ceased

Patent Citations (4)

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