WO2011062158A1 - Mécanisme de transmission de puissance - Google Patents

Mécanisme de transmission de puissance Download PDF

Info

Publication number
WO2011062158A1
WO2011062158A1 PCT/JP2010/070371 JP2010070371W WO2011062158A1 WO 2011062158 A1 WO2011062158 A1 WO 2011062158A1 JP 2010070371 W JP2010070371 W JP 2010070371W WO 2011062158 A1 WO2011062158 A1 WO 2011062158A1
Authority
WO
WIPO (PCT)
Prior art keywords
plate
coil spring
drive plate
annular member
annular
Prior art date
Application number
PCT/JP2010/070371
Other languages
English (en)
Japanese (ja)
Inventor
三城 鳥居
大介 林
幸久 高士
Original Assignee
アイシン精機株式会社
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by アイシン精機株式会社 filed Critical アイシン精機株式会社
Priority to CN201080052641.1A priority Critical patent/CN102639893A/zh
Priority to JP2011541923A priority patent/JPWO2011062158A1/ja
Publication of WO2011062158A1 publication Critical patent/WO2011062158A1/fr

Links

Images

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
    • F16F15/121—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
    • F16F15/123—Wound springs
    • F16F15/12353—Combinations of dampers, e.g. with multiple plates, multiple spring sets, i.e. complex configurations
    • F16F15/1236—Combinations of dampers, e.g. with multiple plates, multiple spring sets, i.e. complex configurations resulting in a staged spring characteristic, e.g. with multiple intermediate plates
    • F16F15/12366—Combinations of dampers, e.g. with multiple plates, multiple spring sets, i.e. complex configurations resulting in a staged spring characteristic, e.g. with multiple intermediate plates acting on multiple sets of springs

Definitions

  • a torque fluctuation absorber as a power transmission mechanism disclosed in Patent Document 1 is known.
  • This device comprises a drive side member 18 for rotating and transmitting power, an arc-shaped spring 24 disposed in the rotation direction of the drive side member 18 and capable of rotating integrally with the drive side member 18, and the drive side member 18.
  • the driven side member 20 is coaxially disposed with the rotary shaft of the above-mentioned, and motive power is transmitted by the drive side member 18 and the spring 24, and can rotate integrally with the drive side member 18 and the spring 24.
  • the present invention aims to improve the vibration damping function of a damper mechanism in a power transmission mechanism.
  • a plurality of driving side members for rotating and transmitting power, and a plurality of the driving side members arranged in series in the rotational direction of the driving side member are rotatable in unison with the driving side member.
  • the elastic member is coaxially arranged with the rotation shaft of the drive side member, and the power is transmitted by the drive side member through the elastic member, and can be integrally rotated with the drive side member and the elastic member.
  • a support portion is provided to support the elastic member.
  • the annular member has a first restricting portion which restricts the radial movement of the annular member with respect to the annular member.
  • the first restricting portion be a protrusion that protrudes in the radial direction.
  • one of the drive side member and the driven side member protrudes in the radial direction.
  • the elastic member has a plurality of flanges, and the elastic member is disposed between the adjacent flanges, and the flange controls a second restricting portion that restricts the radial movement of the elastic member with respect to the annular member. It is preferable to have.
  • FIG. 2 is a side cross-sectional view of a clutch disc 100 according to an embodiment of the present invention. It is a top view of the clutch disc 100 of FIG. It is a sectional side view of the power transmission mechanism concerning one embodiment of the present invention.
  • FIG. 4 is a top view when the power transmission mechanism is separated along line XX in FIG. 3; It is a top view of the driven plate 4 in FIG. It is a top view of the annular member 5 in FIG.
  • FIG. 5 is a top view of the first drive plate 2a in FIG. 3; It is a top view of the 2nd drive plate 2b in FIG. It is the partially notched top view which showed typically the structure of the clutch disc containing the power transmission mechanism which concerns on Example 1 of this invention.
  • FIG. 4 is a top view when the power transmission mechanism is separated along line XX in FIG. 3; It is a top view of the driven plate 4 in FIG. It is a top view of the annular member 5 in FIG.
  • FIG. 5 is a top
  • FIG. 10 is a cross-sectional view taken along line XX ′ of FIG. 9 schematically showing a configuration of a clutch disk including a power transmission mechanism according to Embodiment 1 of the present invention. It is the top view which showed typically the structure of the power transmission mechanism (pre-damper part) which concerns on Example 1 of this invention.
  • FIG. 12 is a cross-sectional view taken along line YY ′ of FIG. 11 schematically showing the configuration of the power transmission mechanism (pre-damper portion) according to the first embodiment of the present invention. It is the top view which showed typically the structure of the driven plate in the power transmission mechanism (pre-damper part) which concerns on Example 1 of this invention.
  • FIG. 1 is a side sectional view of a clutch disc 100 according to an embodiment of the present invention
  • FIG. 2 is a top view of the clutch disc 100 of FIG.
  • FIG. 3 is a side cross-sectional view of the torque fluctuation absorbing device 1 according to an embodiment of the present invention
  • FIG. 4 is a top view when the torque fluctuation absorbing device 1 is separated along line XX in FIG. It is.
  • torque fluctuation absorbing device 1 as a power transmission mechanism constitutes a clutch disk 100 and is disposed on a power transmission path between an output shaft of an engine and an input shaft of a transmission. It is A plurality of torque fluctuation absorbing devices 1 are provided in series in the direction of rotation (in the direction of the arrow in FIG.
  • drive plate (drive side member) 2 that transmits rotation and transmits power, and is integral with the drive plate 2 Is arranged coaxially with the rotatable coil spring (elastic member) 3 and the rotation axis O of the drive plate 2, and power is transmitted by the drive plate 2 through the coil spring 3 to drive plate 2 and the coil
  • a driven plate (a driven side member) 4 rotatable integrally with the spring 3 and an annular member 5 coaxially arranged with the rotation axis of the drive plate 2 and arranged rotatably relative to the drive plate 2 and the driven plate 4 Is equipped.
  • the driven plate 4 is connected to an input shaft of a transmission (not shown) and rotates integrally with the input shaft of the transmission.
  • FIG. 5 is a top view of the driven plate 4.
  • the driven plate 4 has an annular portion 4a engaged with the input shaft of the transmission through a hole provided in the central portion thereof, and the outer side in the radial direction of the driven plate 4 from the outer peripheral portion of the annular portion 4a.
  • the flange portion 4b radially protrudes toward the Three flanges 4 b are provided at predetermined intervals in the circumferential direction of the driven plate 4 (or in the rotational direction of the driven plate 4 indicated by the arrow in FIG. 5).
  • FIG. 6 is a top view of the annular member 5.
  • the annular member 5 has an annular main body 5a, a protrusion (first regulating portion) 5b, and a support (support) 5c.
  • the protrusion 5b having an arc shape has a diameter from the inner peripheral surface of the main body 5a at a predetermined interval in the circumferential direction of the annular member 5 (or in the rotational direction of the annular member 5 of the arrow in FIG. 6). Three are formed so as to protrude inward in the direction.
  • the support portions 5c are respectively formed so as to protrude further radially inward from the central portion of the inner side surface of the protrusion 5b.
  • each accommodation part 4c is divided into a first accommodation part 4ca and a second accommodation part 4cb by the support part 5c, and one coil spring 3 is accommodated in the first accommodation part 4ca and the second accommodation part 4cb. Ru. Therefore, two coil springs 3 are accommodated in one accommodation portion 4c.
  • one end of the coil spring 3 abuts on the other side surface facing the circumferential direction of the flange portion 4 b of the driven plate 4. The end is in contact with one side surface of the support portion 5 c of the annular member 5 facing the circumferential direction. Further, by disposing the coil spring 3 in the second housing portion 4 cb, one end of the coil spring 3 abuts on the other side surface facing the circumferential direction of the support portion 5 c of the annular member 5. The other end of the flange 4 abuts on one side surface of the flange portion 4 b of the driven plate 4 facing the circumferential direction.
  • the outer peripheral portion facing the radial direction outer side of the annular member 5 at one end of the coil spring 3 housed in the first housing portion 4 ca can be supported on the inner side surface of the convex portion 4 d of the flange portion 4 b
  • the outer peripheral portion of the annular member 5 facing the radially outer side at the other end can be supported by the inner surface of the support portion 5 b of the annular member 5.
  • an outer peripheral portion facing the radial direction outer side of the annular member 5 at one end of the coil spring 3 accommodated in the second accommodation portion 4 cb is made supportable on the inner side surface of the support portion 5 b of the annular member 5.
  • the outer peripheral portion of the annular member 5 at the other end, which faces radially outward, is supportable by the inner side surface of the convex portion 4 d of the flange portion 4 b.
  • the drive plate 2 is connected to a crankshaft of an engine (not shown) and rotates integrally with the crankshaft, and comprises a first drive plate 2 a and a second drive plate 2 b.
  • the first drive plate 2a and the second drive plate 2b have a coupling shaft 2ab (see FIG. 7) provided on the outer peripheral portion of the first drive plate 2a and a coupling hole 2bb provided on the outer periphery of the second drive plate 2b. Integrated by coupling to (see FIG. 8).
  • FIG. 7 is a top view of the first drive plate 2a
  • FIG. 8 is a top view of the second drive plate 2b.
  • the first drive plate 2a and the second drive plate 2b which are integrally configured, have concave portions 2aa and 2ba for accommodating the coil spring 3, the driven plate 4 and the annular member 5, respectively.
  • Recesses 2aa and 2ba have an annular bottom, and the circumferential direction or rotational direction (arrow direction in FIGS. 7 and 8) corresponds to housing 4d of coil spring 3 of driven plate 4 at the bottom.
  • Three window holes 2a1 and 2b1 are formed at predetermined intervals.
  • the first drive plate 2a and the second drive plate 2b are integrally configured, so that the coil spring 3, the driven plate 4 and the annular member 5 are formed by the respective recesses 2aa and 2ba.
  • the housing space which accommodates is formed, and the coil spring 3, the driven plate 4 and the annular member 5 are arrange
  • two coil springs 3 are accommodated in each of the window holes 2a1 and 2b1.
  • the driven plate 4 and the annular member 5 are disposed coaxially with the rotation axis of the drive plate 2 and are relatively rotatable.
  • the inner diameters of the peripheral portions 2ac and 2bc of the recesses 2aa and 2ba of the first drive plate 2a and the second drive plate 2b of the drive plate 2 are made larger than the outermost diameter of the annular member 5. That is, the peripheral wall portions 2ac and 2bc of the recessed portions 2aa and 2ba are located outside the annular member 5 in the radial direction of the annular member 5.
  • the other end of the compressed coil spring 3 presses the side surface of one side of the support 5 c of the annular member 5 by the restoring force, and the other side of the support 5 c presses one end of the coil spring 3.
  • the other end of the compressed coil spring 3 presses the flange portion 4 d of the driven plate 4 by a restoring force to transmit torque to the driven plate 4. The torque is then input to the input shaft of the transmission.
  • the torque fluctuation absorbing device 1 of the present embodiment in the compression of the coil spring 3 accompanying the relative rotation of the drive plate 2 and the driven plate 4, the coil spring 3 and, in particular, the radial direction of the annular member 5 of the coil spring 3 in particular.
  • the outer peripheral portion facing outward does not contact or slide on the drive plate 2, and the vibration damping function of the damper mechanism of the torque fluctuation absorber 1 can be improved.
  • a predetermined clearance always exists between the outer peripheral surface of the annular member 5 and the peripheral wall portions of the recessed portions 2aa and 2ba of the driven plate 2, and the inner peripheral surface of the main body portion 5a of the annular member 5 is driven
  • a predetermined clearance always exists between the outer peripheral surface of the plate 4 (the outer peripheral surface of the flange portion 4 b), and between the inner side surface of the support portion 5 c of the annular member 5 and the outer peripheral surface of the annular portion 4 a of the driven plate 4.
  • the radially outward extension of the annular member 5 of the middle part of the coil spring 3 is suppressed, for example, the middle of the coil spring 3 It is possible to suppress the contact and sliding of the portion with the annular member 5 and to improve the vibration damping function of the damper mechanism of the torque fluctuation absorbing device 1.
  • Each window hole 2a 1 guides expansion and contraction of the coil spring 3.
  • the three window holes 2a1 are disposed at positions shifted by 120 degrees with respect to the rotation center axis of the first drive plate 2a.
  • the window holes 2a1 are arranged along the same circumference (the radial position is the same).
  • the first drive plate 2a is in contact with the second drive plate 2b at a portion not interfering with the operation of the driven plate 4 and the annular member 5 on the surface on the second drive plate 2b side.
  • the coil spring 3 contracts when the pre-damper portion 101 twists (twist between the drive plates 2a and 2b and the driven plate 4), and absorbs a shock due to a difference in rotation between the drive plates 2a and 2b and the driven plate 4 .
  • the coil spring 3 it is possible to use a coil spring (straightly extending linearly) in the expansion and contraction direction (longitudinal direction).
  • the spring force (spring coefficient) of the coil spring 3 is set smaller than the spring force (spring coefficient) of the coil spring 19 in the main damper portion 102.
  • the driven plate 4 is an annular plate-like member disposed on the outer periphery of the outer spline portion 23b of the hub member 23, and is a component of the pre-damper portion 101 (see FIGS. 9 to 13).
  • the driven plate 4 is disposed rotatably with respect to the first drive plate 2a and the second drive plate 2b between the recess 2aa of the first drive plate 2a and the recess 2ba of the second drive plate 2b.
  • the driven plate 4 is disposed so as to be rotatable in a range of a predetermined angle with respect to the annular member 5 radially inward of the annular member 5.
  • the driven plate 4 has three flange portions 4 b extending radially outward from a predetermined position of the outer peripheral end face of the annular portion 4 a.
  • the three flange portions 4 b are disposed at positions shifted by 120 degrees with respect to the rotation center axis of the driven plate 4.
  • the accommodating part 4c for accommodating the two coil springs 3 and the support part 5c of the annular member 5 is provided.
  • An end face of the housing portion 4 c in the circumferential direction is in contact with the coil spring 3 so as to be capable of coming into and coming out of contact.
  • the housing portion 4c has a first housing portion 4ca for housing the coil spring 3 on one side in the circumferential direction of the support portion 5c, and a second one for housing the other coil spring 3 on the other side in the circumferential direction of the support portion 5c. It has the accommodation part 4cb.
  • the driven plate 4 has two convex portions 4 d circumferentially projecting on both sides in the circumferential direction from a position radially outward of the position where it can contact the coil spring 3 at the end face in the circumferential direction of each flange portion 4 b.
  • the convex portion 4 d regulates movement (movement in the radial direction) of the coil spring 3 in the pre-damper portion 101.
  • the driven plate 4 has an inner spline portion 4e formed at an inner peripheral end. The inner spline portion 4 e is non-rotatably engaged with the outer spline portion 23 b of the hub member 23.
  • the annular member 5 is an annular plate-like member disposed radially outside the driven plate 4 and is a component of the pre-damper portion 101 (see FIGS. 9 to 12 and 14).
  • the annular member 5 is disposed rotatably with respect to the first drive plate 2a and the second drive plate 2b between the recess 2aa of the first drive plate 2a and the recess 2ba of the second drive plate 2b.
  • the annular member 5 is rotatably disposed in a range of a predetermined angle with respect to the driven plate 4 at a radially outer side of the driven plate 4.
  • the annular member 5 has three support parts 5c which protrude inward in the radial direction from a predetermined position of the inner peripheral end of the main body part 5a formed in an annular shape.
  • the three support portions 5 c are disposed at positions shifted by 120 degrees with respect to the rotation center axis of the annular member 5.
  • Each support portion 5 c is disposed between the circumferential direction of the two coil springs 3 accommodated in each accommodation portion 4 c of the driven plate 4. Both sides of the end face of each support 5c in the circumferential direction support the end of the coil spring 3.
  • the annular member 5 has two protrusions 5b that protrude in the circumferential direction from the position radially outward of the position where it can contact the coil spring 3 on the end face in the circumferential direction of each support 5c.
  • the convex portion 5 b restricts the movement (movement in the radial direction outer side) of the coil spring 3 in the pre-damper portion 101.
  • the facing 10 is a friction material that can be frictionally engaged with a flywheel (or any other member) that rotates integrally with a crankshaft (not shown) of the engine (see FIGS. 9 and 10).
  • the facing 10 is annularly formed.
  • the facing 10 is fixed to one axial surface (surface on the left side in FIG. 10) of the disc spring 12 by a plurality of rivets 13.
  • the facing 11 is a friction material that can be frictionally engaged with a pressure plate that rotates integrally with a crankshaft (not shown) of the engine (see FIGS. 9 and 10).
  • the facing 11 is annularly formed.
  • the facing 11 is fixed to the other axial surface (the surface on the right side in FIG. 10) of the disk spring 12 by a plurality of rivets 14.
  • those containing rubber, resin, fibers (short fibers, long fibers), particles for adjusting the coefficient of friction ⁇ , and the like can be used.
  • the disc spring 12 is an annular disc-like member having an elastic force against pressing against the disc surface (see FIGS. 9 and 10).
  • the disc spring 12 has facings 10 and 11 attached by rivets 13 and 14 on both sides of the outer peripheral portion.
  • the disk spring 12 is caulked and fixed to one end portion of the plurality of connecting members 17 together with the side plate 15 at the inner peripheral portion.
  • the disc spring 12 rotates integrally with the side plates 15 and 16.
  • the rivet 13 is a member for fixing the facing 10 to one surface (surface on the left side in FIG. 10) in the axial direction of the disk spring 12 (see FIGS. 9 and 10).
  • the side plate 15 is an annular member disposed on one side (left side in FIG. 10) of the flange member 18 in the axial direction so as to be separated from the flange member 18 (see FIGS. 9 and 10).
  • the side plate 15 is caulked and fixed to one end of the plurality of connecting members 17 together with the disc spring 12 at a portion near the outer peripheral end.
  • the side plate 15 rotates integrally with the connecting member 17, the disc spring 12, and the side plate 16.
  • the side plate 15 has six windows 15 a for accommodating the coil spring 19 in the main damper portion 102 of the middle portion.
  • the circumferential end surface of the window portion 15 a is in contact with and separable from the end of the coil spring 19.
  • the window 15 a guides expansion and contraction of the coil spring 19.
  • the window portion 15a is disposed at a position shifted 50 degrees about the rotation center axis of the side plate 15 with respect to one of the window portions 15a adjacent in the circumferential direction, and the other window adjacent in the circumferential direction It is disposed at a position which is offset by 70 degrees with respect to the portion 15a about the central axis of rotation of the side plate 15.
  • the side plate 15 is slidably in contact with the first drive plate 2 a at the pre-damper portion 101 on the inner peripheral side of the main damper portion 102.
  • the side plate 15 is rotatably supported by the hub member 23 via the thrust member 24 at the inner peripheral end.
  • the side plate 15 is rotationally fixed to the thrust member 24 at the inner peripheral end.
  • the side plate 15 is in contact with the thrust member 24 at the surface on the side of the flange member 18 near the inner peripheral end.
  • the side plate 16 is an annular member disposed on the other side (right side in FIG. 10) of the flange member 18 in the axial direction so as to be separated from the flange member 18 (see FIGS. 9 and 10).
  • the side plate 16 is caulked and fixed to the other end of the plurality of connecting members 17 at a portion near the outer peripheral end.
  • the side plate 16 rotates integrally with the connecting member 17, the disc spring 12, and the side plate 15.
  • the side plate 16 has six windows 16 a for accommodating the coil spring 19 in the main damper portion 102 of the middle portion.
  • the circumferential end surface of the window portion 16 a is in contact with and separable from the end of the coil spring 19.
  • the window portion 16 a guides expansion and contraction of the coil spring 19.
  • the window portion 16a is disposed at a position shifted 50 degrees around the rotation center axis of the side plate 16 with respect to one of the window portions 16a adjacent in the circumferential direction, and the other window adjacent in the circumferential direction It is disposed at a position which is offset by 70 degrees with respect to the portion 16 a about the central axis of rotation of the side plate 16.
  • the side plate 16 is engaged with the detent portion 20 a of the thrust member 20 in a non-rotatable and axially movable manner at a portion which does not conflict with the main damper portion 102.
  • the side plate 16 supports one end of the disc spring 21 at a portion on the inner peripheral side of the anti-rotation portion 20 a of the thrust member 20.
  • the side plate 16 supports one end of the disc spring 26 at a portion on the inner peripheral side of the disc spring 21.
  • the side plate 16 is rotatably supported by the hub member 23 via the thrust member 25 at an inner peripheral end.
  • the side plate 16 is rotationally fixed to the thrust member 25 at an inner peripheral end.
  • the connecting member 17 is a member for connecting the side plates 15 and 16 and the disc spring 12 (see FIGS. 9 and 10). At one end of the connecting member 17, the side plate 15 and the disc spring 12 are fixed by caulking. At the other end of the connecting member 17, a side plate 16 is fixed by caulking.
  • the middle portion (body portion) of the connecting member 17 serves as a spacer for keeping the space between the side plate 16 and the disc spring 12. The middle part of the connecting member 17 is inserted into the notch 18b of the blanking member 18, and when the main damper portion 102 is twisted (twist between the side plates 15 and 16 and the flange member 18), the notch is cut out.
  • connection members 17 are arranged at predetermined intervals in the circumferential direction of the side plates 15 and 16.
  • the flange member 18 is an annular plate-like member disposed on the outer periphery of the outer spline portion 23b of the hub member 23 (see FIGS. 9 and 10).
  • the flange member 18 has six windows 18 a for accommodating the coil spring 19 in the main damper portion 102.
  • the circumferential end surface of the window portion 18 a is in contact with the end portion of the coil spring 19 so as to be able to be separated and attached.
  • the middle portion (body portion) of the connection member 17 is inserted into each notch 18b.
  • the end face of the notch 18b in the circumferential direction contacts the middle portion of the connecting member 17 when the main damper portion 102 is twisted (twist of the side plates 15, 16 and the flange member 18), thereby the main damper It becomes a stopper part which controls excessive twist of section 102.
  • the flange member 18 is sandwiched between the second drive plate 2 b and the thrust member 20 on the surface in the axial direction on the inner peripheral side of the main damper portion 102 and is slidable with the thrust member 20.
  • the flange member 18 has an inner spline portion 18c in which an inner spline is formed at an inner peripheral end. The inner spline portion 18c engages with the outer spline portion 23b of the hub member 23 so that the hub member 23 and the flange member 18 can be twisted within a predetermined angle range.
  • the coil spring 19 is a component of the main damper portion 102, and is an elastic member housed in the windows 15a, 16a, 18a formed in the side plates 15, 16 and the flange member 18 (see FIGS. 9 and 10). ). Both ends of the coil spring 19 are in contact with and separable from the end faces of the windows 15a, 16a, 18a in the circumferential direction.
  • the coil spring 19 contracts when the side plates 15 and 16 and the flange member 18 twist, and absorbs the shock due to the difference in rotation between the side plates 15 and 16 and the flange member 18.
  • a coil spring that is straight (extending linearly) in the expansion and contraction direction (longitudinal direction) can be used.
  • the spring force (spring coefficient) of the coil spring 19 is set larger than the spring force (spring coefficient) of the coil spring 3 in the pre-damper portion 101.
  • the disc spring 21 is a disc-shaped spring which is disposed between the thrust member 20 and the side plate 16 and biases the thrust member 20 toward the flange member 18 (see FIGS. 9 and 10).
  • the hub member 23 is a member that outputs rotational power from the dampers 2 and 3 toward an input shaft (not shown) of the transmission (see FIGS. 9 and 10).
  • the hub member 23 has a flange portion 23a extending radially outward from a predetermined portion of the outer periphery of the cylindrical portion.
  • the hub member 23 splines with an input shaft (not shown) on the inner peripheral surface of the cylindrical portion.
  • the hub member 23 relatively rotatably supports the side plate 15 via the thrust member 24 on the outer periphery, and supports the side plate 16 relatively rotatably via the thrust member 25.
  • the flange portion 23a has an outer spline portion 23b in which an outer spline is formed on the outer peripheral surface.
  • the outer spline portion 23b engages with the inner spline portion 18c of the flange member 18 such that the hub member 23 and the flange member 18 can be twisted within a predetermined angle range.
  • the outer spline portion 23 b is non-rotatably engaged with the inner spline portion (4 e in FIG. 11) of the driven plate 4.
  • the flange portion 23 a is slidably held by the thrust members 24 and 25.
  • the thrust member 25 is an annular member disposed between the side plate 16 and the hub member 23 (see FIGS. 9 and 10).
  • the thrust member 25 is disposed between the disc spring 26 and the flange portion 23a in the axial direction, is urged toward the flange portion 23a by the disc spring 26, and is slidably pressed against the flange portion 23a. There is.
  • the thrust member 25 engages with the side plate 16 so as to be non-rotatable and axially movable.
  • the thrust member 25 is also interposed between the side plate 16 and the hub member 23 in the radial direction, and serves as a slide bearing (bush) for supporting the side plate 16 relatively rotatably on the hub member 23.
  • the coil spring 19 acts until the middle part of the connecting member 17 connected to the side plates 15 and 16 abuts on the circumferential end face of the notch 18 b of the flange member 18. At this time, the coil spring 3 of the pre-damper portion 101 rotates integrally with the flange member 18 in the maximum compression state.
  • a predetermined clearance always exists between the outer peripheral surface of the annular member 5 and the peripheral wall portions of the recessed portions 2aa and 2ba of the driven plate 2, and the inner peripheral surface of the main body portion 5a of the annular member 5 is driven
  • a predetermined clearance always exists between the outer peripheral surface of the plate 4 (the outer peripheral surface of the flange portion 4 b), and between the inner side surface of the support portion 5 c of the annular member 5 and the outer peripheral surface of the annular portion 4 a of the driven plate 4.
  • the coil spring 3 When the device 1 rotates, the coil spring 3 is urged radially outward of the annular member 5 by centrifugal force. However, the radially outward movement of the coil spring 3 with respect to the annular member 5 is restricted by the convex portion 4 d of the flange portion 4 b of the driven plate 4 and the convex portion 5 b of the annular member 5. Thereby, the arrangement position of the coil spring 3 can be always maintained at a good position, and the vibration damping function can be exhibited stably.
  • the radially outward extension of the annular member 5 of the middle part of the coil spring 3 is suppressed, for example, the middle of the coil spring 3 It is possible to suppress the contact and sliding of the portion with the annular member 5 and to improve the vibration damping function of the damper mechanism of the torque fluctuation absorbing device 1.

Landscapes

  • 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)

Abstract

L'invention concerne un mécanisme de transmission de puissance selon lequel la fonction d'atténuation de vibrations d'un mécanisme amortisseur est améliorée. Un mécanisme de transmission de puissance est doté d'une plaque d'entraînement qui tourne et qui transmet une puissance, de ressorts enroulés qui sont disposés en série dans la direction de rotation de la plaque d'entraînement et qui peuvent tourner conjointement avec la plaque d'entraînement, d'une plaque entraînée qui est disposée de manière coaxiale à l'axe de rotation de la plaque d'entraînement et qui peut tourner conjointement avec la plaque d'entraînement et les ressorts enroulés grâce à la puissance transmise à la plaque entraînée par la plaque d'entraînement par l'intermédiaire des ressorts enroulés, et d'un élément annulaire qui est coaxial à l'axe de rotation et qui est disposé de manière à être rotatif par rapport à la plaque entraînée et à la plaque d'entraînement. L'élément annulaire est doté de sections de support disposées entre les ressorts enroulés et supportant les ressorts enroulés.
PCT/JP2010/070371 2009-11-19 2010-11-16 Mécanisme de transmission de puissance WO2011062158A1 (fr)

Priority Applications (2)

Application Number Priority Date Filing Date Title
CN201080052641.1A CN102639893A (zh) 2009-11-19 2010-11-16 动力传递机构
JP2011541923A JPWO2011062158A1 (ja) 2009-11-19 2010-11-16 動力伝達機構

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
JP2009-264392 2009-11-19
JP2009264392 2009-11-19

Publications (1)

Publication Number Publication Date
WO2011062158A1 true WO2011062158A1 (fr) 2011-05-26

Family

ID=44059636

Family Applications (1)

Application Number Title Priority Date Filing Date
PCT/JP2010/070371 WO2011062158A1 (fr) 2009-11-19 2010-11-16 Mécanisme de transmission de puissance

Country Status (3)

Country Link
JP (1) JPWO2011062158A1 (fr)
CN (1) CN102639893A (fr)
WO (1) WO2011062158A1 (fr)

Cited By (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2014126245A1 (fr) * 2013-02-18 2014-08-21 株式会社エフ・シ－・シ－ Dispositif amortisseur de couple
WO2017052223A1 (fr) * 2015-09-25 2017-03-30 주식회사 토룩 Module de ressort de compression du type arc pour actionneur élastique en série
WO2018043528A1 (fr) * 2016-08-30 2018-03-08 ヴァレオトランスミッションジャパン株式会社 Dispositif amortisseur
JP2019052727A (ja) * 2017-09-15 2019-04-04 アイシン精機株式会社 ダンパ装置
DE202020102264U1 (de) 2019-04-24 2020-06-09 Aisin Seiki Kabushiki Kaisha Dämpfervorrichtung

Families Citing this family (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN108953414B (zh) * 2017-05-18 2021-11-16 舍弗勒技术股份两合公司 离合器从动盘及离合器

Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPH01316521A (ja) * 1988-06-17 1989-12-21 Atsugi Unisia Corp 捩り振動減衰装置
JPH0462443U (fr) * 1990-09-28 1992-05-28
JPH0552365U (ja) * 1991-12-16 1993-07-13 株式会社大金製作所 ダンパーディスク
DE19753557A1 (de) * 1996-12-11 1998-06-18 Luk Lamellen & Kupplungsbau Torsionsschwingungsdämpfer
JP2009019745A (ja) * 2007-07-13 2009-01-29 Exedy Corp ダンパー機構

Family Cites Families (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPH053774Y2 (fr) * 1984-12-26 1993-01-29
EP0347259B1 (fr) * 1988-06-17 1996-08-14 Unisia Jecs Corporation Amortisseur de vibrations de torsion pour transmission de puissance de véhicule automobile
EP1394440B1 (fr) * 1995-07-24 2005-05-25 Exedy Corporation Ensemble de disque amortisseur contenant un mécanisme de frottement avec des éléments de friction améliorés
DE19654970C2 (de) * 1996-08-05 2002-02-21 Mannesmann Sachs Ag Torsionsschwingungsdämpfer

Patent Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPH01316521A (ja) * 1988-06-17 1989-12-21 Atsugi Unisia Corp 捩り振動減衰装置
JPH0462443U (fr) * 1990-09-28 1992-05-28
JPH0552365U (ja) * 1991-12-16 1993-07-13 株式会社大金製作所 ダンパーディスク
DE19753557A1 (de) * 1996-12-11 1998-06-18 Luk Lamellen & Kupplungsbau Torsionsschwingungsdämpfer
JP2009019745A (ja) * 2007-07-13 2009-01-29 Exedy Corp ダンパー機構

Cited By (10)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2014126245A1 (fr) * 2013-02-18 2014-08-21 株式会社エフ・シ－・シ－ Dispositif amortisseur de couple
JP2014156923A (ja) * 2013-02-18 2014-08-28 F C C:Kk トルクダンパ装置
US9677642B2 (en) 2013-02-18 2017-06-13 Kabushiki Kaisha F.C.C. Torque damper apparatus
WO2017052223A1 (fr) * 2015-09-25 2017-03-30 주식회사 토룩 Module de ressort de compression du type arc pour actionneur élastique en série
KR101785067B1 (ko) 2015-09-25 2017-10-12 주식회사 토룩 직렬 탄성 액추에이터를 위한 아크형 압축 스프링 모듈
WO2018043528A1 (fr) * 2016-08-30 2018-03-08 ヴァレオトランスミッションジャパン株式会社 Dispositif amortisseur
JP2019052727A (ja) * 2017-09-15 2019-04-04 アイシン精機株式会社 ダンパ装置
DE202020102264U1 (de) 2019-04-24 2020-06-09 Aisin Seiki Kabushiki Kaisha Dämpfervorrichtung
JP2020180632A (ja) * 2019-04-24 2020-11-05 アイシン精機株式会社 ダンパ装置
JP7314601B2 (ja) 2019-04-24 2023-07-26 株式会社アイシン ダンパ装置

Also Published As

Publication number Publication date
JPWO2011062158A1 (ja) 2013-04-04
CN102639893A (zh) 2012-08-15

Similar Documents

Publication Publication Date Title
JP5772098B2 (ja) トルク変動吸収装置
JP5272853B2 (ja) トルク変動吸収装置
WO2011062158A1 (fr) Mécanisme de transmission de puissance
KR101080103B1 (ko) 댐퍼 기구
JP5376061B2 (ja) トルク変動吸収装置
JP7014909B2 (ja) ねじり振動ダンパー
JP6965566B2 (ja) トルク変動吸収装置
US20100243404A1 (en) Torque fluctuation absorber
CN111386409B (zh) 带有主阻尼器和附加阻尼器的扭转振动阻尼器
KR101195945B1 (ko) 비선형 특성을 가지는 직렬 연결 토션 댐퍼
US20210025459A1 (en) Torsional vibration, clutch disk and clutch
JP4932926B2 (ja) ダンパー機構
WO2012060263A1 (fr) Amortisseur de chocs dus à la torsion
CN111263866B (zh) 具有可激活摩擦装置的扭转阻尼装置
JP2009150471A (ja) ダンパ装置
JP5388628B2 (ja) ダンパー機構
JP2012067876A (ja) トルク変動吸収装置
US7252593B2 (en) Torsional-vibration damper
EP3636955B1 (fr) Dispositif d'amortisseur
US20070099710A1 (en) Flexible flywheel
CN112833111B (zh) 离合器从动盘及离合器
JP6708566B2 (ja) 動力伝達装置
CN114286902B (zh) 具有两级阻尼的减振结构及车辆用减振器和离合器从动盘
CN117739068A (zh) 减振装置
CN117739067A (zh) 减振装置

Legal Events

Date Code Title Description
WWE Wipo information: entry into national phase

Ref document number: 201080052641.1

Country of ref document: CN

121 Ep: the epo has been informed by wipo that ep was designated in this application

Ref document number: 10831552

Country of ref document: EP

Kind code of ref document: A1

WWE Wipo information: entry into national phase

Ref document number: 2011541923

Country of ref document: JP

WWE Wipo information: entry into national phase

Ref document number: 1201002253

Country of ref document: TH

NENP Non-entry into the national phase

Ref country code: DE

WWE Wipo information: entry into national phase

Ref document number: 5268/CHENP/2012

Country of ref document: IN

122 Ep: pct application non-entry in european phase

Ref document number: 10831552

Country of ref document: EP

Kind code of ref document: A1