WO2013140562A1 - 捩り振動減衰装置 - Google Patents
捩り振動減衰装置 Download PDFInfo
- Publication number
- WO2013140562A1 WO2013140562A1 PCT/JP2012/057295 JP2012057295W WO2013140562A1 WO 2013140562 A1 WO2013140562 A1 WO 2013140562A1 JP 2012057295 W JP2012057295 W JP 2012057295W WO 2013140562 A1 WO2013140562 A1 WO 2013140562A1
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- WO
- WIPO (PCT)
- Prior art keywords
- torque transmission
- cam
- torque
- torsional vibration
- vibration damping
- Prior art date
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Classifications
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- 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
- F16F15/121—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 using springs as elastic members, e.g. metallic springs
- F16F15/1213—Spiral springs, e.g. lying in one plane, around axis of rotation
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- 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
- F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
- F16D13/00—Friction clutches
- F16D13/58—Details
- F16D13/60—Clutching elements
- F16D13/64—Clutch-plates; Clutch-lamellae
-
- 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
- F16F15/1204—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 with a kinematic mechanism or gear system
- F16F15/1205—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 with a kinematic mechanism or gear system with a kinematic mechanism, i.e. linkages, levers
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- 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
- F16F15/30—Flywheels
-
- 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
- F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
- F16D3/00—Yielding couplings, i.e. with means permitting movement between the connected parts during the drive
- F16D3/02—Yielding couplings, i.e. with means permitting movement between the connected parts during the drive adapted to specific functions
- F16D3/12—Yielding couplings, i.e. with means permitting movement between the connected parts during the drive adapted to specific functions specially adapted for accumulation of energy to absorb shocks or vibration
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- 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
- F16F2230/00—Purpose; Design features
- F16F2230/0052—Physically guiding or influencing
- F16F2230/0064—Physically guiding or influencing using a cam
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- Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
- Y10—TECHNICAL SUBJECTS COVERED BY FORMER USPC
- Y10T—TECHNICAL SUBJECTS COVERED BY FORMER US CLASSIFICATION
- Y10T74/00—Machine element or mechanism
- Y10T74/21—Elements
- Y10T74/2121—Flywheel, motion smoothing-type
- Y10T74/2131—Damping by absorbing vibration force [via rubber, elastomeric material, etc.]
Definitions
- the present invention relates to a torsional vibration damping device, and in particular, transmits torque between a first rotating member and a second rotating member so that rotational torque is transmitted between a first rotating member and a second rotating member.
- the present invention relates to a torsional vibration damping device connected in a relatively rotatable manner via a member and an elastic member.
- a drive source such as an internal combustion engine or an electric motor is connected to a wheel or the like via a drive transmission system having a speed reducer or the like, and power is transmitted from the drive source to the wheel via the drive transmission system.
- the drive transmission system connected to the drive source generates, for example, a jumble sound or a booming sound due to torsional vibration using a rotational fluctuation caused by a torque fluctuation of the internal combustion engine as a vibration source.
- the jagged noise is a jagged noise generated when a pair of idling gears of a transmission gear set collides with a torsional vibration caused by a rotational fluctuation caused by a torque fluctuation of an internal combustion engine.
- the muffled noise is an abnormal noise generated in the vehicle interior due to vibration caused by torsional resonance of the drive transmission system using the torque fluctuation of the internal combustion engine as an excitation force.
- the torsional resonance of the drive transmission system is, for example, in a steady region.
- a drive source such as an internal combustion engine or an electric motor is connected to wheels and the like to transmit rotational torque from the drive source and torsional vibration between the drive source and a drive transmission system having a transmission gear set is absorbed.
- a torsional vibration damping device is known (see, for example, International Publication No. 2011-067815 (Patent Document 1)).
- This torsional vibration damping device has a cam surface on the outer peripheral portion, a cam portion configured such that the curvature of the cam surface changes along the circumferential direction, and a cam portion provided on the same axis as the cam portion. Are provided between the cam plate and the disc plate and elastically deformed when the cam portion and the disc plate rotate relative to each other.
- the torsional vibration damping device is provided on the disk plate when one end contacts the cam surface of the cam part and the other end is biased by the elastic member, and the cam part and the disk plate rotate relative to each other.
- An arm member is provided that transmits rotational torque between the cam portion and the disk plate by rotating about the rotation axis and elastically deforming the elastic member.
- the range of the torsion angle between the cam portion and the disk plate can be widened by swinging the arm member as the cam portion rotates to elastically deform the elastic member. it can. For this reason, the torsional rigidity between the cam portion and the disk plate can be lowered as a whole, and the vibration damping performance can be improved by sufficiently attenuating the jagged noise and the booming noise.
- a rotation provided on the disk plate is used as a torque transmission member that transmits rotational torque between the cam portion and the disk plate.
- An arm member that can rotate around a moving shaft is used. Since it is necessary to house the arm member inside the torsional vibration damping device, the extension length of the elastic member in the circumferential direction of the disk plate is limited, and the elastic deformation amount of the elastic member in the circumferential direction is limited. For this reason, it is difficult to receive a large reaction force in the circumferential direction from the elastic member, it is difficult for the torsional vibration damping device to generate a large torsional rigidity, and there is still room for improvement.
- the present invention has been made in view of the above problems, and a main object thereof is to provide a torsional vibration damping device capable of increasing torsional rigidity without increasing the elastic member in the radial direction.
- the torsional vibration damping device includes a first rotating member, a second rotating member, an elastic member, a cam member, a torque transmitting member, and a socket member.
- the first rotating member and the second rotating member are provided on the same axis.
- the elastic member is provided between the first rotating member and the second rotating member.
- the elastic member is elastically deformable in the rotation direction of the first rotating member.
- the cam member is provided on the same axis as the first rotating member.
- the cam member rotates integrally with the first rotating member.
- the cam member has a cam surface whose diameter changes along the rotation direction of the first rotation member.
- the torque transmission member contacts the cam surface and transmits rotational torque between the first rotating member and the second rotating member.
- the socket member is provided between the torque transmission member and the elastic member.
- the socket member holds the end of the elastic member on the torque transmission member side.
- the socket member has a contact surface that contacts the torque transmission member.
- the entire torque transmission member is provided so as to be capable of reciprocating in the radial direction of the first rotating member as the cam member rotates. The torque transmission member elastically compresses the elastic member in the rotation direction when the first rotation member moves radially outward.
- the second rotating member is provided with a guide portion that guides the torque transmitting member in the radial direction.
- the contact surface of the socket member is preferably inclined with respect to the radial direction of the first rotating member.
- the torsional vibration damping device includes a holding member that holds an end portion of the elastic member on the side away from the torque transmission member, and the socket member moves along the rotation direction as the torque transmission member moves radially outward. Move in the direction approaching the holding member.
- the torque transmission member preferably has a substantially cylindrical outer shape.
- the torque transmitting member is provided rotatably with respect to the shaft portion, the shaft portion, the first rotating body contacting the cam surface, and rotatably with respect to the shaft portion, A second rotating body that contacts the contact surface, and the first rotating body has an outer diameter that is smaller than the outer diameter of the second rotating body.
- the torque transmission member includes a main body having a cylindrical outer peripheral surface and a covering portion that covers the outer peripheral surface, and the covering portion has a smaller coefficient of friction than a forming material of the main body. It is made of material.
- the torsional rigidity can be increased without increasing the elastic member in the radial direction.
- FIG. 2 is a cross-sectional view of the torsional vibration damping device taken along line II-II shown in FIG.
- FIG. 3 is a cross-sectional view of the torsional vibration damping device as viewed in the direction of arrow B in FIG. 2.
- FIG. 3 is a cross-sectional view of the torsional vibration damping device as viewed in the direction C of FIG.
- It is a side view which shows the structure of an example of a torque transmission device. It is a side view which shows the structure of the other example of a torque transmission apparatus. It is a side view which shows the structure of the further another example of a torque transmission apparatus.
- FIG. 6 is a front view of the torsional vibration damping device when the torsion angle of the cam member with respect to the disc plate is ⁇ 45 °. It is a graph which shows the relationship between the twist angle of a torsional vibration damping device, and a torque.
- FIG. 1 is a front view of a torsional vibration damping device 1 according to the present embodiment.
- FIG. 2 is a cross-sectional view of the torsional vibration damping device 1 along the line II-II shown in FIG. 3 is a cross-sectional view of the torsional vibration damping device 1 as viewed in the direction of the arrow B in FIG. 4 is a cross-sectional view of the torsional vibration damping device 1 as viewed in the direction of the arrow C in FIG.
- the torsional vibration damping device 1 includes a driving side rotating member 3, a driven side rotating member 2, and a pair of coil springs 4 as elastic members.
- a rotational torque from an internal combustion engine (not shown) that is a drive source is input to the drive side rotation member 3.
- the driven side rotating member 2 transmits the rotational torque input to the driving side rotating member 3 to a transmission of a drive transmission system (not shown).
- the driving side rotating member 3 and the driven side rotating member 2 are provided on the same axis.
- the coil spring 4 is provided between the driving side rotating member 3 and the driven side rotating member 2.
- the coil spring 4 is elastically deformed so as to be compressed in the rotational direction of the driving side rotating member 3 and the driven side rotating member 2 when the driving side rotating member 3 and the driven side rotating member 2 rotate relative to each other.
- the driven side rotating member 2 includes a boss member 5 as a first rotating member and a cam member 6.
- the boss member 5 is spline-fitted to the outer periphery of the input shaft 21 of the drive transmission transmission.
- the cam member 6 is provided on the same axis as the boss member 5 on the outer periphery of the boss member 5 and rotates integrally with the boss member 5.
- the boss member 5 and the cam member 6 may be integrally formed.
- the boss member 5 and the cam member 6 are formed separately, and spline portions are formed on the outer peripheral portion of the boss member 5 and the inner peripheral portion of the cam member 6, respectively.
- the boss member 5 and the cam member 6 are spline-fitted. May be combined.
- the drive side rotation member 3 includes a pair of disk plates 7 and 8 as a second rotation member and a clutch disk 10.
- the disc plates 7 and 8 are provided on the same axis as the boss member 5 and are disposed on both sides of the boss member 5 in the axial direction.
- the disc plates 7 and 8 are fixed to each other by a pin 9 and a connecting shaft 18 at a predetermined interval in the axial direction, and are integrated by a simple configuration.
- Circular center holes 7a and 8a are formed at the center of the disk plates 7 and 8, and the boss member 5 is accommodated in the center holes 7a and 8a.
- the pin 9 and the connecting shaft 18 are bridged to the disk plates 7 and 8, and both end portions in the axial direction are formed with large diameters, so that the pins 9 and the connecting shaft 18 are locked to the disk plates 7 and 8.
- the disk plates 7 and 8 are integrally rotated by the connecting shaft 18 and the pin 9 so as to rotate integrally.
- the clutch disk 10 is provided radially outward of the disk plate 7 and includes a cushioning plate 11 and friction materials 12a and 12b.
- the cushioning plate 11 is composed of a ring-shaped member that undulates in the thickness direction, and is fixed to the disk plates 7 and 8 by pins 9.
- the friction materials 12 a and 12 b are fixed to both surfaces of the cushioning plate 11 by rivets 13.
- the friction members 12a and 12b are located between a flywheel (not shown) fixed to the crankshaft of the internal combustion engine and a pressure plate of a clutch cover fixed to the flywheel with bolts.
- the friction materials 12a and 12b are pressed against the pressure plate and frictionally engaged with the flywheel and the pressure plate, whereby the rotational torque of the internal combustion engine is input to the disk plates 7 and 8.
- a pair of receiving holes 14 and 15 are formed in the disk plates 7 and 8, respectively.
- the receiving holes 14 and 15 are formed to be separated from each other in the circumferential direction of the disk plates 7 and 8.
- the pair of receiving holes 14 and 15 are formed so as to face each other in the axial direction of the disk plates 7 and 8, and each receive the coil spring 4.
- the coil spring 4 is provided so as to be elastically deformable in the circumferential direction of the disk plates 7 and 8.
- the circumferential direction of the disk plates 7 and 8 and the boss member 5 is the rotational direction of the disk plates 7 and 8 and the boss member 5 provided on the same axis, and is naturally the same direction.
- the housing holes 14 and 15 are curved along the circumferential direction of the disk plates 7 and 8, and the coil spring 4 is in a natural state, that is, in a state before being attached to the housing holes 14 and 15. 7 and 8 are curved in the same direction as the circumferential direction. For this reason, when the coil spring 4 is accommodated in the accommodation holes 14 and 15, the coil spring 4 is curved.
- the receiving holes 14 and 15 are punched by a press on the outer peripheral side of the coil spring 4, and both end portions in the circumferential direction of the disk plates 7 and 8 are closed ends.
- the disk plates 7 and 8 include outer support pieces 14 c and 15 c that extend in the circumferential direction along the radially outer edges of the receiving holes 14 and 15, and the receiving holes 14.
- Inner support pieces 14d and 15d extending in the circumferential direction along the radially inner edge are provided.
- the outer support pieces 14 c and 15 c and the inner support pieces 14 d and 15 d protrude outward in the axial direction of the disk plates 7 and 8.
- the circumferential end 1 a of the coil spring 4 is held by a socket member 16.
- the other end of the coil spring 4 in the circumferential direction is held by a spring seat 17.
- the socket member 16 and the spring seat 17 are accommodated in the accommodation holes 14 and 15. Both ends in the circumferential direction of the coil spring 4 are supported on both ends in the circumferential direction of the receiving holes 14 and 15 by the socket member 16 and the spring seat 17.
- the socket member 16 and the spring seat 17 are formed with protrusions on the surface facing the coil spring 4.
- This protrusion has a height corresponding to one or two turns of both ends of the coil spring 4 in the circumferential direction. Both ends of the coil spring 4 in the circumferential direction are inserted into the protrusions, and the winding spring start and end in the winding direction are engaged with the protrusions, thereby preventing the coil spring 4 from rotating and the socket member 16 and It can be attached to the spring seat 17.
- the closed ends of both end portions in the circumferential direction of the receiving holes 14 and 15 are contact portions 14 a and 15 a that contact the circumferential end portion of the socket member 16, and the spring seat 17.
- the abutting portions 14b and 15b with which the circumferential ends of the abutting portions abut are configured.
- the circumferential end of the socket member 16 contacts the contact portions 14a and 15a
- the circumferential end of the spring seat 17 contacts the contact portions 14b and 15b.
- the socket member 16 and the spring seat 17 engage with the outer support pieces 14c and 15c and the inner support pieces 14d and 15d, respectively, and come out of the receiving holes 14 and 15 by the outer support pieces 14c and 15c and the inner support pieces 14d and 15d. Is prevented.
- the radially inner end and the radially outer end of the socket member 16 and the spring seat 17 have shapes along the curved surfaces of the radially inner end and the radially outer end of the receiving holes 14 and 15.
- the socket member 16 has a shape that can move smoothly along the receiving holes 14 and 15 as the coil spring 4 is elastically deformed.
- a torque transmission member 19 having a substantially cylindrical outer shape is disposed between the socket member 16 and the cam member 6, a torque transmission member 19 having a substantially cylindrical outer shape is disposed.
- the disc plates 7 and 8 are formed with fitting holes 20 extending in the radial direction of the disc plates 7 and 8, and the torque transmitting member 19 is fitted into the fitting holes 20.
- the torque transmission member 19 engages with a fitting hole 20 formed in the disk plates 7 and 8 so that the entire torque transmission member 19 can reciprocate in the radial direction of the disk plates 7 and 8 in which the fitting hole 20 extends. Is provided.
- the fitting hole 20 has a function as a guide portion that guides the torque transmitting member 19 in the radial direction of the disk plates 7 and 8.
- the fitting hole 20 functions as a guide portion
- grooves may be formed in the disk plates 7 and 8.
- the torque transmission member 19 is attached to the disk plates 7 and 8 by engagement between a protrusion formed on one of the surface of the disk plates 7 and 8 and an end of the torque transmission member 19 and a recess formed on the other. You may guide to radial direction.
- the socket member 16 has a contact surface with which the outer peripheral surface of the torque transmission member 19 contacts.
- the contact surface is composed of a linear tapered surface 16a that is inclined with respect to the radial direction and the circumferential direction of the disk plates 7 and 8. That is, the socket member 16 of the present embodiment is formed in a wedge shape having a tapered surface 16a.
- a part of the outer peripheral surface of the torque transmission member 19 is in contact with the tapered surface 16 a of the socket member 16.
- the other part of the outer peripheral surface of the torque transmission member 19 is in contact with the cam surface 6 a of the cam member 6.
- the cam member 6 has a cam surface 6a configured so that the cam diameter continuously changes along the circumferential direction.
- the diameter of the cam surface 6a is the initial position shown in FIG. 1 where the torsion angle between the disk plates 7 and 8 and the cam member 6 is minimum (the torsion angle is approximately 0 °), that is, the disk plates 7 and 8 and the cam member. 6 is the smallest in the portion in contact with the torque transmission member 19 when in the neutral position where the twisting force 6 is not twisted.
- the torsional angle between the disk plates 7 and 8 and the cam member 6 increases, the position of the torque transmission member 19 on the cam surface 6a changes, and the diameter of the cam surface 6a gradually increases as the position changes.
- the cam member 6 of the present embodiment has a point-symmetric shape with respect to the central axes of the disc plates 7 and 8 and has the same curvature across the central axes of the disc plates 7 and 8.
- the initial position of the cam member 6 is set so that the torque transmission member 19 contacts the cam surface 6a having a small diameter when the twist angle between the disk plates 7 and 8 and the boss member 5 is the minimum.
- the torque transmitting member 19 is disposed on the innermost side in the radial direction of the disk plates 7 and 8, and the extension length of the coil spring 4 in the circumferential direction of the disk plates 7 and 8 is the maximum. It is.
- the socket member 16 holds one end portion 4a which is an end portion of the coil spring 4 on the side close to the torque transmission member 19.
- the spring seat 17 as a holding member holds the other end which is the end of the coil spring 4 on the side away from the torque transmission member 19.
- the socket member 16 is provided between the torque transmission member 19 and the coil spring 4.
- the socket member 16 smoothly moves in the direction approaching the spring seat 17 along the peripheral edges of the accommodation holes 14 and 15, and causes the elastic deformation of the coil spring 4 to be compressed. On the other hand, when the coil spring 4 is elastically deformed so as to be extended, the socket member 16 moves smoothly in a direction away from the spring seat 17.
- a hysteresis torque generating mechanism 22 is interposed between the disk plates 7 and 8 and the cam member 6.
- the hysteresis torque generating mechanism 22 includes annular friction members 23, 24, 25, 26 and a disc spring 27.
- the surfaces of the friction materials 23 and 24 are made of a member having a predetermined friction coefficient, and are fixed to the outer peripheral surface in the axial direction of the cam member 6 with an adhesive.
- the friction members 23 and 24 are integrally provided with pins, and the friction members 23 and 24 are attached to the cam member 6 by fitting the pins into pin holes formed on the outer circumferential surface of the cam member 6 in the axial direction. It may be attached.
- the surface of the friction material 25 is composed of a member having a predetermined friction coefficient, and is fixed to the inner peripheral surface of the disk plate 7 with an adhesive.
- a pin or the like may be provided integrally with the friction material 25 and the pin may be attached to the disc plate 7 by fitting the pin into a pin hole formed on the inner peripheral surface of the disc plate 7.
- the friction material 26 is composed of a member having a predetermined friction coefficient on the surface, and a plurality of pins 26a are integrally provided on the outer circumferential surface in the radial direction.
- the pin 26 a is fitted into a pin hole 8 b formed on the inner peripheral surface of the disk plate 8, and the friction material 26 is attached to the inner peripheral surface of the disk plate 8.
- the disc spring 27 is formed in a conical shape, and is interposed between the friction material 26 and the disc plate 8.
- the disc spring 27 generates an elastic force in the axial direction of the cam member 6, thereby bringing the friction material 24 and the friction material 26 into frictional contact with each other, and bringing the friction material 23 and the friction material 25 into frictional contact with each other.
- the cam member 6 and the disk plates 7 and 8 are brought into frictional contact with each other to generate hysteresis torque between the cam member 6 and the disk plates 7 and 8.
- FIG. 5 is a side view showing a configuration of an example of the torque transmission member 19.
- An example torque transmission member 19 illustrated in FIG. 5 includes a solid cylindrical shaft portion 190 and bearings 191, 192, and 193 assembled to the shaft portion 190.
- the bearings 191, 192, and 193 are provided with an axis that is the center of rotation.
- Bearings 191, 192, 193 include an inner ring, an outer ring, and a rolling element.
- the inner rings of the bearings 191, 192 and 193 are annular members fixed to the shaft portion 190.
- the outer rings of the bearings 191, 192, and 193 are annular members that share the center with the shaft portion 190, and are rotatably provided to the shaft portion 190.
- the rolling elements of the bearings 191, 192, 193 are rotatably supported between the inner ring and the outer ring.
- the bearing 193 (193a), the bearing 192 (192a), the bearing 191, the bearing 192 (192b), and the bearing 193 (193b) are sequentially arranged from one end to the other end of the shaft 190 along the extending direction of the shaft 190. Is arranged.
- the bearings 193 a, 192 a, 191, 192 b, and 193 b are sequentially arranged in the extending direction of the shaft portion 190 with a space between each other.
- the outer ring of the bearing 191 has a function as a first rotating body that contacts the cam surface 6a of the cam member 6 and rolls with respect to the cam surface 6a.
- the outer ring of the bearing 192 (192a, 192b) has a function as a second rotating body that contacts the tapered surface 16a of the socket member 16 and rolls relative to the tapered surface 16a.
- the outer ring of the bearing 193 (193a, 193b) is in contact with the inner peripheral surface of the fitting hole 20 formed in the disk plates 7 and 8, and rolls against the inner peripheral surface of the fitting hole 20. It has a function as a rotating body.
- the bearing 191 has an outer diameter smaller than the outer diameter of the bearings 192 and 193.
- the outer ring of the bearing 191 that contacts the cam member 6 is formed to have a smaller diameter than the other bearings 192 and 193.
- FIG. 6 is a side view showing the configuration of another example of the torque transmission member 19. Unlike the torque transmission member of the example shown in FIG. 5, the torque transmission member 19 of another example shown in FIG. 6 does not have a bearing between the bearings 192a and 192b.
- the outer diameter of the shaft portion 190 shown in FIG. 6 is the same as the outer diameter of the bearing 191 shown in FIG. 5 and is smaller than the outer diameter of the bearings 192 and 193.
- the cam surface 6a of the cam member 6 contacts the cylindrical outer peripheral surface of the shaft portion 190 between the bearing 192a and the bearing 192b, and slides with respect to the outer peripheral surface.
- the torque transmission member 19 having the configuration shown in FIG. 6 can avoid interference between the shaft portion 190 and the tapered surface 16a of the socket member 16 by defining the diameter of the shaft portion 190 to be smaller than the diameters of the bearings 192 and 193. . Compared to the torque transmission member shown in FIG. 5, one bearing is reduced, so that a lower cost torque transmission member 19 can be provided.
- FIG. 7 is a side view showing the configuration of still another example of the torque transmission member 19. Unlike the torque transmission member shown in FIGS. 5 and 6, the torque transmission member 19 in the example shown in FIG. 7 does not have a bearing.
- a torque transmission member 19 shown in FIG. 7 has a cylindrical main body 196.
- the main body 196 has a cylindrical outer peripheral surface.
- the outer peripheral surface of the main body 196 is covered with a covering portion 198.
- the covering portion 198 is formed by providing a material for forming the covering portion 198 on the outer peripheral surface of the main body 196 by any method such as coating.
- the covering portion 198 is made of a material having a smaller coefficient of friction than the material for forming the main body 196.
- the forming material of the covering portion 198 may be DLC (Diamond-like Carbon) which is a material having a small friction coefficient.
- the torque transmission member 19 shown in FIG. 7 slides on the outer peripheral surface on which the covering portion 198 is formed with respect to the cam surface 6 a of the cam member 6, the tapered surface 16 a of the socket member 16, and the inner peripheral surface of the fitting hole 20. Move. Since the entire outer peripheral surface of the torque transmission member 19 is formed of a material that has a small friction coefficient and can be easily slid, it is possible to easily reciprocate the torque transmission member 19 in the radial direction without using a bearing. it can. Since the entire outer peripheral surface of the torque transmission member 19 can easily slide with respect to other members, the interference between the bearing that contacts the cam member 6 and the socket member 16 as described above does not become a problem. .
- the bearing width is small and the contact area is small. During this period, the contact stress between the bearing and the socket member 16 is increased.
- the torque transmission member 19 has the slide pin shape shown in FIG. 7, the contact width between the torque transmission member 19 and the cam surface 6a and between the torque transmission member 19 and the taper surface 16a can be increased. Since it can be increased, the contact stress can be reduced.
- FIG. 8 is a front view of the torsional vibration damping device when the torsion angle of the cam member 6 with respect to the disk plates 7 and 8 is + 30 °.
- FIGS. 9 and 10 which will be described later, illustrate a state in which the disk plates 7 and 8 are rotated in the counterclockwise direction (R2 direction) from the state of FIG. 1 in response to the rotational torque of the internal combustion engine.
- R2 direction counterclockwise direction
- the description will be made assuming that the cam member 6 is twisted in the clockwise direction (R1 direction) on the positive side with respect to the disk plates 7 and 8. The cam member 6 is twisted to the positive side with respect to the disk plates 7 and 8 when the vehicle is accelerated.
- the friction materials 12a and 12b are pressed against the pressure plate and frictionally engaged with the flywheel and the pressure plate, whereby the rotational torque of the internal combustion engine is input to the disk plates 7 and 8.
- the relative rotation between the disk plates 7 and 8 and the cam member 6 is small, that is, the torsion angle between the disk plates 7 and 8 and the cam member 6 is small near 0 °.
- the cam member 6 is positioned at the initial position and rotates integrally with the boss member 5.
- the torque transmission member 19 presses the cam member 6 by the reaction force acting from the coil spring 4
- the disk is interposed via the coil spring 4 provided between the disk plates 7 and 8 and the boss member 5.
- a rotational torque is transmitted between the plates 7 and 8 and the boss member 5.
- the compression amount of the coil spring 4 is small, the torsional rigidity between the disk plates 7 and 8 and the boss member 5 is small.
- the cam member 6 has an elliptical cam surface 6a, and the rotation radius of the cam surface 6a when the cam member 6 rotates changes in the circumferential direction.
- a torque transmission member 19 is provided between the cam member 6 and the coil spring 4, and the outer peripheral surface of the torque transmission member 19 contacts the cam surface 6 a of the cam member 6 and the tapered surface 16 a of the socket member 16.
- the cam member 6 acts on the torque transmission member 19 in a direction in which the torque transmission member 19 is pressed against the socket member 16.
- the torque transmission member 19 receives a force from the cam surface 6 a of the cam member 6 and is pressed toward the tapered surface 16 a of the socket member 16.
- the socket member 16 converts a radial force that the cam member 6 presses the torque transmission member 19 into a circumferential force that is a direction in which the coil spring 4 extends.
- the coil spring 4 is biased by the cam member 6 via the torque transmission member 19, and the coil spring 4 is elastically compressed in the circumferential direction.
- the diameter of the cam surface 6a increases from the initial position of the cam member 6 as the torsion angle between the disk plates 7 and 8 and the boss member 5 increases. Therefore, when the disk plates 7 and 8 and the boss member 5 rotate relative to each other and the torsion angle between the disk plates 7 and 8 and the boss member 5 increases, the torque transmission member 19 is pressed against the cam surface 6a of the cam member 6, It moves radially outward along the radial direction of the disk plates 7 and 8, which is the direction in which the fitting hole 20 extends.
- the displacement in the radial direction of the torque transmission member 19 is converted into a displacement in the circumferential direction via the tapered surface 16a of the socket member 16. Therefore, when the torque transmission member 19 moves outward in the radial direction of the disk plates 7 and 8, the socket member 16 moves in the circumferential direction. As the socket member 16 moves toward the spring seat 17 along the peripheral edges of the accommodation holes 14, 15, the coil spring 4 is compressed in the circumferential direction. Since one end portion in the circumferential direction of the spring seat 17 is in contact with the contact portions 14b and 15b of the accommodation holes 14 and 15, the socket member 16 moves toward the spring seat 17 along the periphery of the accommodation holes 14 and 15. As a result, the coil spring 4 is compressed.
- the coil spring 4 when the torque transmission member 19 biases the coil spring 4 through the socket member 16, the coil spring 4 is elastically deformed and compressed along the circumferential direction.
- the coil spring 4 that is elastically deformed generates a biasing force that attempts to restore its shape. Due to the reaction force of the coil spring 4 to be compressed, a force inward in the radial direction acts on the torque transmission member 19 from the tapered surface 16a of the socket member 16, and the torque transmission member 19 presses the cam member 6 with a strong pressing force. To do.
- the rotational torque of the disk plates 7 and 8 is reliably transmitted to the cam member 6 via the coil spring 4 and the torque transmission member 19. Accordingly, the torsional vibration between the disk plates 7 and 8 and the boss member 5 can be absorbed and damped while the power of the internal combustion engine is transmitted from the disk plates 7 and 8 to the boss member 5.
- FIG. 9 is a front view of the torsional vibration damping device when the torsion angle of the cam member 6 with respect to the disk plates 7 and 8 is + 70 °.
- the torque transmitting member 19 moves along the cam surface 6a as shown in FIG.
- the torque transmission member 19 is pressed by the cam surface 6 a of the cam member 6, the torque transmission member 19 further moves outward in the radial direction of the disk plates 7 and 8.
- the radial displacement of the torque transmission member 19 is converted into a circumferential displacement via the tapered surface 16a of the socket member 16.
- the socket member 16 further moves toward the spring seat 17 along the peripheral edges of the accommodation holes 14 and 15, thereby further compressing the coil spring 4 in the circumferential direction. Therefore, the torsional vibration between the disk plates 7 and 8 and the boss member 5 can be absorbed and attenuated while the power of the internal combustion engine is transmitted from the disk plates 7 and 8 to the boss member 5.
- FIG. 10 is a front view of the torsional vibration damping device when the torsion angle of the cam member 6 with respect to the disk plates 7 and 8 is + 90 °.
- the cam member 6 has a top 6b.
- the top portion 6b is a portion of the cam surface 6a that is farthest from the boss member 5, and is a portion having the largest diameter in the cam surface 6a.
- the torque transmission member 19 rides on the top portion 6b of the cam surface 6a.
- the disk plate 7 and 8 idles with respect to the cam member 6 by the torque transmission member 19 getting over the top 6b.
- the cam member 6 can function as a torque limiter during vehicle acceleration.
- an excessive torque is input to the disk plates 7 and 8
- FIG. 11 is a front view of the torsional vibration damping device when the torsion angle of the cam member 6 with respect to the disk plates 7 and 8 is ⁇ 45 °.
- the driving torque of the internal combustion engine is reduced and engine braking is generated, so that rotational torque is input to the cam member 6 from the input shaft 21 of the transmission.
- the rotational fluctuation due to the torque fluctuation of the internal combustion engine is small during deceleration, the fluctuation torque between the disk plates 7 and 8 and the cam member 6 is small, so that the cam member 6 is relative to the disk plates 7 and 8. It will be twisted in the negative counterclockwise direction (R2 direction).
- the diameter of the cam surface 6a increases as the torsional angle between the disk plates 7 and 8 and the cam member 6 increases from the initial position of the cam member 6. Therefore, when the torque transmission member 19 is pressed by the cam surface 6 a of the cam member 6 whose diameter gradually increases, the torque transmission member 19 moves outward in the radial direction of the disk plates 7 and 8.
- the radial displacement of the torque transmitting member 19 is converted into the circumferential displacement via the socket member 16 as in acceleration.
- the socket member 16 compresses the coil spring 4 in the circumferential direction by moving toward the spring seat 17 along the peripheral edges of the accommodation holes 14 and 15. Accordingly, the torsional vibration between the disk plates 7 and 8 and the cam member 6 can be absorbed and damped while transmitting the power of the drive transmission system from the cam member 6 to the disk plates 7 and 8.
- the cam member 6 is twisted to either the acceleration side or the deceleration side with respect to the disk plates 7 and 8. Even in such a case, a certain hysteresis torque can be generated between the disk plates 7 and 8 and the cam member 6.
- FIG. 12 is a graph showing the relationship between the torsional angle and the torque of the torsional vibration damping device 1.
- FIG. 12 shows the torsional characteristics between the disk plates 7 and 8 and the cam member 6, the torsion angle between the disk plates 7 and 8 and the cam member 6 in this embodiment, and the output output from the cam member 6. The relationship with torque is shown.
- the horizontal axis in FIG. 12 is the relative torsion angle of the cam member 6 with respect to the disk plates 7 and 8, and the vertical axis is the output torque output from the cam member 6, that is, the torsional rigidity.
- the output torque on the vertical axis corresponds to the reaction force (spring stiffness) of the cam member 6 against the disk plates 7 and 8.
- the coil spring 4 contracts as the torsion angle of the cam member 6 with respect to the disk plates 7 and 8 increases, so that the pressing force applied to the cam member 6 by the torque transmission member 19 is reduced. growing. And the output torque becomes large because the pressing force to the cam member 6 by the torque transmission member 19 becomes large. The change in output torque at this time becomes a curved torsional characteristic that changes continuously.
- the outer peripheral surface of the torque transmission member 19 contacts the cam surface 6 a of the cam member 6, and the cam member 6 presses the coil spring 4 via the torque transmission member 19 as the cam member 6 rotates.
- the reaction force from the coil spring 4 to the torque transmission member 19 is changed.
- the twist angle between the disk plates 7 and 8 and the cam member 6 accompanying the rotation of the cam member 6 can be widened.
- the torsional characteristics between the disk plates 7 and 8 and the cam member 6 can be made non-linear, and the rotational torque can be smoothly transmitted from the disk plates 7 and 8 to the boss member 5.
- the torsional characteristics and the magnitude of the torsion angle when the disk plates 7 and 8 and the cam member 6 rotate relative to each other are the shape of the cam surface 6 a of the cam member 6, the spring constant of the coil spring 4, and the torque transmission member 19. By adjusting the shape and the like, it is possible to set an arbitrary twist characteristic and twist angle.
- the torsional vibration damping device 1 when the torsional vibration damping device 1 is interposed between a vehicle drive source and a transmission having a transmission gear set, the torsion angle between the disk plates 7 and 8 and the cam member 6 is small. In some cases, the torsional rigidity between the disk plates 7 and 8 and the cam member 6 can be made low torsional characteristics.
- the internal combustion engine that is the drive source It is possible to attenuate the torsional vibration caused by the rotational fluctuation caused by the torque fluctuation as a vibration source, and to suppress the generation of a rattling sound from the gear pair of the transmission in an unloaded state.
- the torsional rigidity can be reduced as a whole by widening the range of the torsional angle between the disc plates 7 and 8 and the cam member 6, it is transmitted from the disc plates 7 and 8 to the boss member 5.
- torsional vibration caused by rotational fluctuations caused by torque fluctuations of the internal combustion engine is attenuated to suppress the jagged noise generated by the collision of the idle gear pairs of the transmission gear set. Can do.
- the coil spring 4 can be reduced in rigidity, when the torsional angle between the disk plates 7 and 8 and the cam member 6 is large, the torsional vibration due to the torsional resonance of the drive transmission system is attenuated and the coil spring 4 is confined. Generation of sound can be suppressed.
- the torsional vibration damping device 1 of the present embodiment has the torque transmission member 19 that reciprocally moves along the radial direction of the disk plates 7 and 8, and the outer periphery of the torque transmission member 19. A part of the surface is brought into contact with the cam surface 6 a of the cam member 6, and another part of the outer peripheral surface of the torque transmission member 19 is brought into contact with the tapered surface 16 a of the socket member 16. Thereby, the coil spring 4 and the cam member 6 can be connected via the socket member 16 and the torque transmission member 19.
- the torsional angle between the disk plates 7 and 8 and the boss member 5 is simplified by simply providing the coil spring 4, the socket member 16, the torque transmission member 19 and the cam member 6 between the disk plates 7 and 8 and the boss member 5. Thus, it is possible to provide the torsional vibration damping device 1 capable of widening the range.
- the circumferential direction is used to transmit the rotational torque. It is not necessary to provide a conventional arm member that extends to Therefore, the extension length of the coil spring 4 in the circumferential direction can be increased. Therefore, it is possible to provide the torsional vibration damping device 1 with improved torsional rigidity without increasing the size of the torsional vibration damping device 1 by increasing the coil spring 4 in the radial direction. Since the amount of elastic deformation of the coil spring 4 in the circumferential direction can be increased, fluctuations in rotational torque can be absorbed more efficiently.
- the torque transmission members 19 sandwich the cam member 6 with the central axes of the disk plates 7 and 8 interposed therebetween. become. For this reason, when the cam member 6 biases the coil spring 4 via the torque transmission member 19, the torque transmission member 19 sandwiches the central axes of the disk plates 7 and 8 by the reaction force of the coil spring 4. Can be held with a strong pressing force. Therefore, the rotational torque can be more reliably transmitted from the disk plates 7 and 8 to the boss member 5, and the disk plates 7 and 8 and the boss member 5 can be reliably rotated integrally.
- the socket member 16 that holds one end portion of the coil spring 4 in the circumferential direction has a tapered surface 16a that contacts the outer peripheral surface of the torque transmission member 19, and this The tapered surface 16 a is provided to be inclined with respect to the radial direction that is the moving direction of the torque transmission member 19. For this reason, the radial displacement of the torque transmitting member 19 is converted into a circumferential displacement by the socket member 16.
- the coil spring 4 By moving the socket member 16 in the circumferential direction, the coil spring 4 can be greatly elastically deformed in the circumferential direction. Therefore, the reaction force acting on the torque transmission member 19 from the coil spring 4 can be increased, and the transmission performance of the rotational torque from the disk plates 7 and 8 to the boss member 5 can be improved.
- the socket member 16 and the coil spring 4 are accommodated in the accommodating holes 14 and 15 extending in the circumferential direction, the radial displacement of the torque transmitting member 19 is more reliably changed to the circumferential displacement of the socket member 16.
- the coil spring 4 can be elastically deformed more reliably. Since the coil spring 4 is configured to bend along the accommodation holes 14 and 15 in a natural state, when the torque transmission member 19 is displaced radially outward, the torque transmission member 19 is interposed via the socket member 16. The coil spring 4 can be greatly urged in the circumferential direction. For this reason, the reaction force which acts on the torque transmission member 19 from the coil spring 4 can be enlarged efficiently.
- a hysteresis torque generating mechanism 22 When a hysteresis torque generating mechanism 22 is interposed between the disk plates 7 and 8 and the boss member 5, a certain hysteresis torque is generated when the disk plates 7 and 8 and the cam member 6 rotate relative to each other. For this reason, during acceleration / deceleration with a large rotational torque transmitted from the disk plates 7 and 8 to the boss member 5, a hysteresis torque is generated against a large torsional vibration caused by a rotational fluctuation caused by a torque fluctuation of the internal combustion engine. Can be made.
- two torque transmission members 19 are provided, and torque transmission is performed at two locations of the cam member 6 by the pair of torque transmission members 19, but the number of torque transmission members is arbitrary. May be.
- the number of torque transmission members 19 may be one, or the cam member 6 may be formed in a three-pronged shape and torque transmission may be performed at three locations by three torque transmission members.
- the driving side rotating member includes the clutch disk 10 and the disk plates 7 and 8, and the driven side rotating member includes the boss member 5.
- the present invention is not limited to this configuration. That is, the driven side rotating member may include the boss member 5 as the first rotating member, and the driven side rotating member may include the disk plates 7 and 8 as the second rotating member.
- the torsional vibration damping device 1 is interposed between the internal combustion engine of the vehicle and the drive system having the transmission.
- the torsional vibration damping device can be applied to any device as long as it has a drive source that transmits to the drive shaft and a drive system that transmits the rotational torque output from the driven side rotation member.
- a torsional vibration damping device of the present embodiment is applied to a hybrid damper or the like that is interposed between an output shaft of an internal combustion engine and a power split mechanism that splits power into an electric motor and a wheel-side output shaft. 1 may be applied. Further, the torsional vibration damping device 1 of the present embodiment may be applied to a lockup damper or the like interposed between the lockup clutch device of the torque converter and the transmission gear set. Further, the torsional vibration damping device 1 of the present embodiment may be applied between the differential case and the ring gear provided on the outer peripheral portion of the differential case.
- the torsional vibration damping device has an effect that the torsional rigidity can be increased without increasing the elastic member in the radial direction, and between the first rotating member and the second rotating member. It is useful as a torsional vibration damping device or the like in which a first rotating member and a second rotating member are connected to each other through a torque transmitting member and an elastic member so as to transmit rotational torque.
- 1 Torsional vibration damping device 2 driven side rotating member, 3 driving side rotating member, 4 coil spring, 4a one end, 5 boss member, 6 cam member, 6a cam surface, 6b top, 7, 8 disc plate, 14, 15 housing hole, 16 socket member, 16a taper surface, 19 torque transmitting member, 20 fitting hole, 190 shaft portion, 191, 192, 192a, 192b, 193, 193a bearing, 196 body, 198 covering portion.
Abstract
Description
Claims (7)
- 第1の回転部材(5)と、
前記第1の回転部材(5)と同一軸線上に設けられた第2の回転部材(7,8)と、
前記第1の回転部材(5)と前記第2の回転部材(7,8)との間に設けられ、前記第1の回転部材(5)の回転方向に弾性変形可能な弾性部材(4)と、
前記第1の回転部材(5)と同一軸線上に設けられ、前記第1の回転部材(5)と一体回転し、前記回転方向に沿って径が変化するカム面(6a)を有する、カム部材(6)と、
前記カム面(6a)に接触し、前記第1の回転部材(5)と前記第2の回転部材(7,8)との間で回転トルクを伝達するトルク伝達部材(19)と、
前記トルク伝達部材(19)と前記弾性部材(4)との間に設けられ、前記弾性部材(4)の前記トルク伝達部材(19)側の端部(4a)を保持し、前記トルク伝達部材(19)に接触する接触面(16a)を有するソケット部材(16)と、を備え、
前記トルク伝達部材(19)は、前記カム部材(6)の回転に伴ってその全体が前記第1の回転部材(5)の径方向に往復移動自在に設けられ、前記第1の回転部材(5)の径方向外方への移動時に前記弾性部材(4)を前記回転方向に弾性的に圧縮する、捩り振動減衰装置(1)。 - 前記第2の回転部材(7,8)には、前記トルク伝達部材(19)を前記径方向に導くガイド部(20)が設けられている、請求項1に記載の捩り振動減衰装置(1)。
- 前記接触面(16a)は、前記径方向に対して傾斜する、請求項1または請求項2に記載の捩り振動減衰装置(1)。
- 前記弾性部材(4)の前記トルク伝達部材(19)から離れる側の端部を保持する保持部材(17)を備え、
前記ソケット部材(16)は、前記トルク伝達部材(19)が前記径方向外方に移動するに従って、前記回転方向に沿って前記保持部材(17)に近接する方向に移動する、請求項1から請求項3のいずれかに記載の捩り振動減衰装置(1)。 - 前記トルク伝達部材(19)は、略円柱状の外形を有する、請求項1から請求項4のいずれかに記載の捩り振動減衰装置(1)。
- 前記トルク伝達部材(19)は、軸部(190)と、前記軸部(190)に対し回転自在に設けられ、前記カム面(6a)に接触する第1の回転体(191)と、前記軸部(190)に対し回転自在に設けられ、前記接触面(16a)に接触する第2の回転体(192)と、を含み、
前記第1の回転体(191)は、前記第2の回転体(192)の外径よりも小さい外径を有する、請求項5に記載の捩り振動減衰装置(1)。 - 前記トルク伝達部材(19)は、円筒状の外周面を有する本体(196)と、前記外周面を被覆する被覆部(198)とを含み、
前記被覆部(198)は、前記本体(196)の形成材料よりも小さい摩擦係数を有する材料により形成されている、請求項5に記載の捩り振動減衰装置(1)。
Priority Applications (5)
Application Number | Priority Date | Filing Date | Title |
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CN201280071665.0A CN104204604B (zh) | 2012-03-22 | 2012-03-22 | 扭转振动衰减装置 |
EP12871922.6A EP2829767B1 (en) | 2012-03-22 | 2012-03-22 | Torsional vibration damping device |
PCT/JP2012/057295 WO2013140562A1 (ja) | 2012-03-22 | 2012-03-22 | 捩り振動減衰装置 |
JP2014505891A JP5817918B2 (ja) | 2012-03-22 | 2012-03-22 | 捩り振動減衰装置 |
US14/379,065 US9546708B2 (en) | 2012-03-22 | 2012-03-22 | Torsional vibration damper |
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PCT/JP2012/057295 WO2013140562A1 (ja) | 2012-03-22 | 2012-03-22 | 捩り振動減衰装置 |
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WO2013140562A1 true WO2013140562A1 (ja) | 2013-09-26 |
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PCT/JP2012/057295 WO2013140562A1 (ja) | 2012-03-22 | 2012-03-22 | 捩り振動減衰装置 |
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US (1) | US9546708B2 (ja) |
EP (1) | EP2829767B1 (ja) |
JP (1) | JP5817918B2 (ja) |
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DE102015014396A1 (de) * | 2015-11-06 | 2017-05-11 | Man Truck & Bus Ag | Kupplungsscheibe für eine lösbare Drehmoment-Übertragungseinrichtung |
DE102019208247A1 (de) * | 2019-06-06 | 2020-12-10 | Zf Friedrichshafen Ag | Drehmomentübertragungseinrichtung |
CN110686043A (zh) * | 2019-10-31 | 2020-01-14 | 重庆宗申无级变速传动有限公司 | 一种无级变速器及其缓冲机构 |
Citations (5)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
JPS57173620A (en) * | 1981-04-20 | 1982-10-26 | Daikin Mfg Co Ltd | Clutch disc |
JPS5937455U (ja) * | 1982-09-02 | 1984-03-09 | トヨタ自動車株式会社 | トルク変動低減フライホイ−ル |
JPS6375630U (ja) * | 1986-11-05 | 1988-05-20 | ||
JPH09280317A (ja) * | 1996-04-08 | 1997-10-28 | Toyota Motor Corp | フライホイール |
WO2011067815A1 (ja) | 2009-12-03 | 2011-06-09 | トヨタ自動車株式会社 | トルク変動吸収装置 |
Family Cites Families (11)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US2590579A (en) | 1948-09-17 | 1952-03-25 | Sarazin Gilles Francois | Torsional vibration damper |
US5374218A (en) * | 1983-11-15 | 1994-12-20 | Luk Lamellen Und Kupplungsbau Gmbh | Assembly for compensation of fluctuations of torque |
US4585427A (en) | 1985-03-26 | 1986-04-29 | Borg-Warner Automotive, Inc. | Long travel series damper for continuously variable transmission |
FR2714435B1 (fr) * | 1993-12-23 | 1996-02-09 | Valeo | Dispositif d'amortissement pour la compensation d'à-coups de rotation et embrayage à friction comportant un tel dispositif. |
US6010408A (en) * | 1994-05-02 | 2000-01-04 | Eaton Corporation | Torsion isolator with active counterweight |
DE102008017352A1 (de) * | 2007-09-10 | 2009-03-12 | Magna Powertrain Ag & Co Kg | Zweimassenschwungrad |
WO2010022697A1 (de) * | 2008-09-01 | 2010-03-04 | Luk Lamellen Und Kupplungsbau Beteiligungs Kg | Zweimassenschwungrad |
EP2644935B1 (en) * | 2010-11-26 | 2017-09-06 | Toyota Jidosha Kabushiki Kaisha | Torsional vibration damping device |
JP5772983B2 (ja) * | 2011-12-22 | 2015-09-02 | トヨタ自動車株式会社 | 捩り振動減衰装置 |
JP2013174294A (ja) * | 2012-02-24 | 2013-09-05 | Toyota Motor Corp | 捩り振動減衰装置 |
WO2013150615A1 (ja) * | 2012-04-04 | 2013-10-10 | トヨタ自動車株式会社 | トルク変動吸収装置および変速機 |
-
2012
- 2012-03-22 WO PCT/JP2012/057295 patent/WO2013140562A1/ja active Application Filing
- 2012-03-22 JP JP2014505891A patent/JP5817918B2/ja active Active
- 2012-03-22 CN CN201280071665.0A patent/CN104204604B/zh not_active Expired - Fee Related
- 2012-03-22 US US14/379,065 patent/US9546708B2/en active Active
- 2012-03-22 EP EP12871922.6A patent/EP2829767B1/en not_active Not-in-force
Patent Citations (5)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
JPS57173620A (en) * | 1981-04-20 | 1982-10-26 | Daikin Mfg Co Ltd | Clutch disc |
JPS5937455U (ja) * | 1982-09-02 | 1984-03-09 | トヨタ自動車株式会社 | トルク変動低減フライホイ−ル |
JPS6375630U (ja) * | 1986-11-05 | 1988-05-20 | ||
JPH09280317A (ja) * | 1996-04-08 | 1997-10-28 | Toyota Motor Corp | フライホイール |
WO2011067815A1 (ja) | 2009-12-03 | 2011-06-09 | トヨタ自動車株式会社 | トルク変動吸収装置 |
Non-Patent Citations (1)
Title |
---|
See also references of EP2829767A4 |
Also Published As
Publication number | Publication date |
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US9546708B2 (en) | 2017-01-17 |
EP2829767B1 (en) | 2018-01-03 |
CN104204604A (zh) | 2014-12-10 |
JP5817918B2 (ja) | 2015-11-18 |
EP2829767A4 (en) | 2016-06-08 |
CN104204604B (zh) | 2015-10-21 |
JPWO2013140562A1 (ja) | 2015-08-03 |
US20150007687A1 (en) | 2015-01-08 |
EP2829767A1 (en) | 2015-01-28 |
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