WO2021193116A1 - Dispositif d'amortisseur et dispositif de démarrage - Google Patents

Dispositif d'amortisseur et dispositif de démarrage Download PDF

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Publication number
WO2021193116A1
WO2021193116A1 PCT/JP2021/009873 JP2021009873W WO2021193116A1 WO 2021193116 A1 WO2021193116 A1 WO 2021193116A1 JP 2021009873 W JP2021009873 W JP 2021009873W WO 2021193116 A1 WO2021193116 A1 WO 2021193116A1
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WO
WIPO (PCT)
Prior art keywords
damper
torque
input
elastic body
damper device
Prior art date
Application number
PCT/JP2021/009873
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English (en)
Japanese (ja)
Inventor
昌昭 山口
啓悟 後藤
康太郎 津田
保成 小原
良 小林
一能 伊藤
賢亮 坂本
貴嗣 本田
祐卓郎 山口
Original Assignee
アイシン・エィ・ダブリュ工業株式会社
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・エィ・ダブリュ工業株式会社 filed Critical アイシン・エィ・ダブリュ工業株式会社
Priority to CN202180023406.XA priority Critical patent/CN115315583A/zh
Publication of WO2021193116A1 publication Critical patent/WO2021193116A1/fr

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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
    • F16F15/131—Suppression of vibrations in rotating systems by making use of members moving with the system using elastic members or friction-damping members, e.g. between a rotating shaft and a gyratory mass mounted thereon the rotating system comprising two or more gyratory masses
    • F16F15/133—Suppression of vibrations in rotating systems by making use of members moving with the system using elastic members or friction-damping members, e.g. between a rotating shaft and a gyratory mass mounted thereon the rotating system comprising two or more gyratory masses using springs as elastic members, e.g. metallic springs
    • F16F15/134—Wound springs
    • 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
    • F16H—GEARING
    • F16H45/00—Combinations of fluid gearings for conveying rotary motion with couplings or clutches
    • F16H45/02—Combinations of fluid gearings for conveying rotary motion with couplings or clutches with mechanical clutches for bridging a fluid gearing of the hydrokinetic type
    • 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
    • F16H—GEARING
    • F16H47/00—Combinations of mechanical gearing with fluid clutches or fluid gearing
    • F16H47/06—Combinations of mechanical gearing with fluid clutches or fluid gearing the fluid gearing being of the hydrokinetic type

Definitions

  • the present disclosure relates to a damper device including an input element, an intermediate element and an output element, and a starting device including the damper device.
  • a first rotating member connected to an engine
  • a second rotating member intermediate element
  • a second rotating member that is connected to a transmission and can rotate relative to the first rotating member
  • a third rotating member that can rotate relative to each other
  • a first damper having a plurality of first elastic members that elastically connect the first rotating member and the second rotating member in the rotational direction
  • a damper mechanism is known that includes a second damper that elastically connects a member and a third rotating member in the rotational direction and starts operation with a torque smaller than the minimum operating torque of the first damper (for example, a patent). Reference 1).
  • the first damper has the characteristics of low rigidity and high hysteresis torque
  • the second damper has the characteristics of low rigidity and low hysteresis torque.
  • the first elastic member of the first damper is provided on either one of the first and second rotating members in a state of being compressed in advance in the rotation direction. As a result, the first elastic member is not compressed and only the second damper operates until the input torque transmitted from the engine to the first rotating member exceeds the minimum operating torque according to the compressed state of the first elastic member. Absorbs and attenuates torsional vibration.
  • the third rotating member is formed with a plurality of windows for accommodating three types of second elastic bodies constituting the second damper so as to be located inside the first elastic body in the radial direction. A gap having a different length in the rotation direction is secured between the two-coil spring and the corresponding window portion so that the second damper operates in three stages.
  • the first damper mechanism since the first elastic member is provided on either the first or second rotating member in a pre-compressed state, the first damper mechanism has a relatively small twist angle. The substantial rigidity of the damper is increased. Therefore, even when the rigidity of the second damper is low, the input torque transmitted from the engine to the first rotating member and the torque transmitted from the transmission side to the third rotating member (deceleration torque due to resistance) are generally the same. When they become equal, only the vibration (vibration torque) from the engine is transmitted to the transmission side, and there is a possibility that noise or the like is generated.
  • the first to third rotating members of the damper mechanism particularly the second rotating member, vibrate between the engine and the transmission.
  • the vibration of the second rotating member may be transmitted to the transmission side to generate noise or the like.
  • the main object of the present invention is to provide a damper device capable of satisfactorily suppressing the vibration of the rotating element when the torque transmitted from the engine to the input element suddenly decreases, and a starting device equipped with the damper device.
  • the damper device of the present disclosure transmits torque between a plurality of rotating elements including an input element connected to an engine, an intermediate element and an output element connected to a transmission, and the input element and the intermediate element.
  • a damper device including a first damper including one elastic body and a second damper including a second elastic body that transmits torque between the intermediate element and the output element.
  • the first or second elastic body which has high rigidity or hysteresis, is between the input element and the intermediate element or when torque is not transmitted between the input element and the output element.
  • the first or second elastic body of the first and second dampers which is supported by a gap in the rotation direction between the intermediate element and the output element and has low rigidity or hysteresis, is the intermediate element and the second elastic body. It is arranged in a pre-compressed state between the output element or between the input element and the intermediate element.
  • one of the first and second dampers having a higher rigidity or hysteresis is the first or second elastic body when torque is not transmitted between the input element and the output element. It is supported with a gap in the direction of rotation between the input element and the intermediate element or between the intermediate element and the output element. As a result, when the difference between the torque transmitted from the engine to the input element and the torque transmitted from the transmission side to the output element becomes extremely small, one of the first and second dampers having higher rigidity or hysteresis is input. It will be supported with a gap in the direction of rotation between the element and the intermediate element or between the intermediate element and the output element.
  • the first or second elastic body of the first and second dampers having low rigidity or hysteresis is in a state of being pre-compressed between the intermediate element and the output element or between the input element and the intermediate element. Placed in. Thereby, when the torsional angle (absolute value) of the other of the first and second dampers having a low rigidity or hysteresis is relatively small, the substantial rigidity of the other can be increased. Therefore, when the torque transmitted from the engine to the input element is suddenly reduced, it is possible to satisfactorily suppress the vibration of the rotating element, particularly the intermediate element.
  • FIG. 1 is a schematic configuration diagram showing the starting device 1 of the present disclosure
  • FIG. 2 is a cross-sectional view showing the starting device 1.
  • the starting device 1 shown in these drawings is mounted on a vehicle V (for example, a front-wheel drive vehicle) including an engine (internal combustion engine) EG as a prime mover.
  • the starting device 1 can rotate coaxially with the front cover 3 as an input member connected to the crankshaft of the engine EG, the pump impeller (input side fluid transmission element) 4 fixed to the front cover 3, and the pump impeller 4.
  • It includes a turbine runner (fluid transmission element on the output side) 5, a damper hub 7 as an output member connected to the transmission TM, a lockup clutch 8, a damper device 10 connected to the damper hub 7, and the like.
  • the transmission TM includes a primary shaft PS as a drive-side rotation shaft, a secondary shaft SS as a driven-side rotation shaft extending in parallel with the primary shaft PS, and a primary provided on the primary shaft PS.
  • a mechanical continuously variable transmission (CVT) including a pulley (not shown), a secondary pulley provided on the secondary shaft SS (not shown), and a transmission belt (not shown) wound around the primary pulley and the secondary pulley.
  • the primary shaft PS of the transmission TM is connected to the input shaft IS fixed to the damper hub 7 via the forward / backward switching mechanism BF.
  • the secondary shaft SS of the transmission TM is connected to the left and right drive shaft DS and the drive wheel DW via a gear mechanism and a differential DF (not shown).
  • the forward / backward switching mechanism BF is a planetary gear mechanism (not shown) including a rotating element connected to the input shaft IS and a rotating element connected to the primary shaft PS, and the clutch C1 is a hydraulic multi-plate friction engaging element. And brake B1.
  • the brake B1 of the forward / reverse switching mechanism BF is released and the clutch C1 is engaged, the power transmitted to the input shaft IS is directly transmitted to the primary shaft PS of the transmission TM.
  • the primary shaft PS rotates in the direction opposite to the rotation direction of the input shaft IS (engine EG).
  • both the clutch C1 and the brake B1 are released, the connection between the input shaft IS and the primary shaft PS is released.
  • the pump impeller 4 of the starting device 1 includes a pump shell (not shown) tightly fixed to the front cover 3 and a plurality of pump blades (not shown) arranged on the inner surface of the pump shell.
  • the turbine runner 5 includes a turbine shell 50 and a plurality of turbine blades 51 arranged on the inner surface of the turbine shell 50, and a fluid chamber defined by a front cover 3 and a pump impeller 4. It is arranged in 9.
  • the inner peripheral portion of the turbine shell 50 is fixed to the turbine hub 52 rotatably supported by the damper hub 7 via a plurality of rivets.
  • the pump impeller 4 and the turbine runner 5 face each other, and a stator 6 (see FIG.
  • the stator 6 includes a plurality of stator blades, and the rotation direction of the stator 6 is set to only one direction by the one-way clutch 60.
  • the pump impeller 4, the turbine runner 5 and the stator 6 function as a torque converter by the action of the stator 6 when the rotation speed difference between the pump impeller 4 and the turbine runner 5 is large, and function as a fluid coupling when the rotation speed difference between the two becomes small. do.
  • the stator 6 and the one-way clutch 60 may be omitted so that the pump impeller 4 and the turbine runner 5 function only as fluid couplings.
  • the lockup clutch 8 locks up and releases the lockup that (mechanically) connects the pump impeller 4 and the turbine runner 5, that is, the front cover 3 and the damper hub 7 (input shaft IS) via the damper device 10. It is to be executed selectively.
  • the lockup clutch 8 is a hydraulic single-plate friction clutch that moves axially with respect to the input shaft IS inside the front cover 3 and near the inner wall surface of the front cover 3 on the engine EG side.
  • the lock-up piston 80 is freely arranged, and the friction material 81 attached to the outer peripheral side and the front cover 3 side surface of the lock-up piston 80 is included.
  • a lockup chamber (release side oil chamber) (not shown) facing the fluid chamber 9 is defined between the lockup piston 80 and the front cover 3 via the lockup piston 80.
  • the lockup chamber is connected to a flood control device (not shown) via an oil passage or the like formed on the input shaft IS or the like.
  • the lockup clutch 8 By making the oil pressure in the lockup chamber lower than the oil pressure in the fluid chamber 9 by the hydraulic control device, the lockup clutch 8 can be engaged and the front cover 3 and the damper hub 7 can be connected via the damper device 10. can.
  • the lockup clutch 8 is released to connect the front cover 3 and the damper hub 7. It can be released.
  • the lockup clutch 8 may be a hydraulic multi-plate friction clutch.
  • the damper device 10 has a drive member (input element) 11, a first intermediate member (first intermediate element) 12, and a second intermediate member (second intermediate element) as rotating elements. ) 15 and a driven member (output element) 16.
  • the damper device 10 is a plurality of (for example, two in this embodiment) outer springs as a first elastic body arranged close to the outer periphery of the damper device 10 as a torque transmission element (torque transmission elastic body).
  • (Input-side elastic body) SP1 and the first inner spring (intermediate elasticity) as the second elastic body having a plurality and the same number (for example, three in this embodiment) arranged radially inside the outer spring SP1.
  • Body SP21 and second inner spring (output side elastic body) SP22.
  • the "axial direction” basically indicates the extending direction of the central axis (axial center) of the starting device 1 and the damper device 10 unless otherwise specified.
  • the “diameter direction” is basically the radial direction of the starting device 1, the damper device 10, the rotating element such as the damper device 10, that is, the center of the starting device 1 and the damper device 10, unless otherwise specified.
  • the extending direction of a straight line extending from an axis in a direction orthogonal to the central axis (radial direction) is shown.
  • the “circumferential direction” is basically along the circumferential direction of the starting device 1, the damper device 10, the rotating element such as the damper device 10, that is, the rotating direction of the rotating element, unless otherwise specified. Indicates the direction.
  • the outer spring SP1 is an arc coil spring
  • the first and second inner springs SP21 and SP22 are linear coil springs having the same specifications as each other.
  • the plurality of outer springs SP1 act in parallel between the drive member 11 and the first intermediate member 12 to form the first damper D1 (see FIG. 1) of the damper device 10.
  • the plurality of first inner springs SP21 act in parallel between the first intermediate member 12 and the second intermediate member 15, and the plurality of second inner springs SP22 include the second intermediate member 15 and the driven member 16. Act in parallel between.
  • the plurality of first inner springs SP21 and the plurality of second inner springs SP22 act in series via the second intermediate member 15 to form the second damper D2 of the damper device 10.
  • the spring constants of the outer springs SP1, the first and second inner springs SP21, and SP22 are the rigidity of the first damper D1
  • the combined spring constants of the plurality of outer springs SP1 are the rigidity of the second damper D2. That is, it is determined to be larger than the combined spring constants of the plurality of first and second inner springs SP21 and SP22.
  • spring seats 90 are attached (fitted) to both ends of each outer spring SP1.
  • the hysteresis of the first damper D1 is larger than the hysteresis of the second damper D2, that is, the plurality of first and second inner springs SP21 and SP22.
  • the hysteresis of the first damper D1 is the torque transmitted from the outer spring SP1 to the first intermediate member 12 as the relative displacement between the drive member 11 (input element) and the driven member 16 (output element) increases. It is quantified as the difference between the torque transmitted from the outer spring SP1 to the first intermediate member 12 when the relative displacement between the drive member 11 and the driven member 16 decreases.
  • the hysteresis of the second damper D2 is the torque transmitted from the second inner spring SP 22 to the driven member 16 when the relative displacement between the drive member 11 and the driven member 16 increases, and the drive member 11 and the driven member 16. It is quantified as the difference from the torque transmitted from the second inner spring SP 22 to the driven member 16 when the relative displacement with 16 decreases.
  • the specifications of the first and second inner springs SP21 and SP22 may be different from each other.
  • the outer spring SP1 may be a linear coil spring
  • the first and second inner springs SP21 and SP22 may be arc coil springs.
  • the drive member 11 of the damper device 10 is formed in an annular shape and is fixed to the lockup piston 80 so as to be located in the outer peripheral side region in the fluid chamber 9.
  • the drive member 11 includes an annular fixing portion 111, a plurality of (for example, two in the present embodiment) spring supporting portions 112 extending in an arc shape, and a plurality of (for example, in the present embodiment, 4).
  • the torque transmission portion (elastic body contact portion) 113 is included.
  • the fixing portion 111 is fixed to the lockup piston 80 of the lockup clutch 8 via a plurality of rivets.
  • the plurality of spring support portions 112 extend axially from the outer peripheral portion of the fixed portion 111 toward the pump impeller 4 and the turbine runner 5 so as to support (guide) the inner peripheral portion of the corresponding outer spring SP1. There is.
  • the plurality of torque transmission portions 113 of the drive member 11 are extended outward in the radial direction from the outer peripheral portion of the fixed portion 111 so as to form a pair and line up at intervals in the circumferential direction. ing.
  • the two torque transmission portions 113 paired with each other face each other at a distance corresponding to the sum of the natural length of the outer spring SP1 and the thickness of the spring seats 90 attached to both ends of the outer spring SP1.
  • each torque transmission portion 113 includes a claw portion 113a extending in the axial direction toward the pump impeller 4 and the turbine runner 5 on the radial outer side of the spring support portion 112.
  • an annular spring support portion 80a for supporting the plurality of outer springs SP1 is formed on the outer peripheral portion of the lockup piston 80 together with the spring support portion 112 of the drive member 11.
  • the first intermediate member 12 includes an annular first plate member 13 and an annular second plate member 14.
  • the first plate member 13 is arranged so as to be close to the turbine runner 5 and is rotatably supported by the damper hub 7.
  • the first plate member 13 includes a plurality of (for example, three in this embodiment) spring support portions 131 and a plurality of (for example, three in this embodiment) spring support portions.
  • the elastic body contact portion) 133i and the like are included.
  • the plurality of spring support portions 131 are formed on the first plate member 13 so as to be arranged at intervals (equally spaced) in the circumferential direction.
  • the plurality of spring support portions 132 are formed on the first plate member 13 so as to be arranged at intervals (equally spaced) in the circumferential direction inside the plurality of spring support portions 131 in the radial direction, and correspond to each other via the window portion.
  • the spring support portion 131 and the first plate member 13 face each other in the radial direction.
  • the plurality of first outer torque transmitting portions 133o are formed so as to form a pair on the outer peripheral portion of the first plate member 13 so as to be arranged at intervals in the circumferential direction.
  • each first outer torque transmitting portion 133o paired with each other have an interval longer than the sum of the natural length of the outer spring SP1 and the thickness of the spring seats 90 attached to both ends of the outer spring SP1. And face each other.
  • each first outer torque transmitting portion 133o includes a claw portion 133a extending axially toward the lockup piston 80, as shown in FIG.
  • One inner torque transmitting portion 133i is provided between the spring supporting portions 131 and 132 (adjacent window portions) adjacent to each other along the circumferential direction.
  • the second plate member 14 of the first intermediate member 12 has an inner diameter larger than that of the first plate member 13, is arranged close to the lockup piston 80 (front cover 3), and is arranged via a plurality of rivets. It is connected (fixed) to the first plate member 13.
  • the second plate member 14 includes a plurality of spring support portions 141 (for example, three in this embodiment) and a plurality of spring support portions 142 (for example, three in this embodiment).
  • a plurality of (for example, three in this embodiment) torque transmission portions (elastic body contact portions) 143 and a short cylindrical portion 144 are included.
  • the plurality of spring support portions 141 are formed on the second plate member 14 so as to be arranged at intervals (equally spaced) in the circumferential direction.
  • the plurality of spring support portions 142 are formed on the second plate member 14 so as to be arranged at intervals (equally spaced) in the circumferential direction inside the plurality of spring support portions 141 in the radial direction, and correspond to each other via the window portion.
  • the spring support portion 141 and the second plate member 14 face each other in the radial direction.
  • the plurality of torque transmission portions 143 are provided one by one between the spring support portions 141 and 142 (adjacent window portions) adjacent to each other along the circumferential direction.
  • the second intermediate member 15 is an annular plate body, and includes a plurality of (for example, three in this embodiment) torque transmission portions (elastic body contact portions) 153 (see FIG. 3).
  • the plurality of torque transmission units 153 extend radially inward from the inner peripheral portion of the second intermediate member 15, and are arranged at intervals (equally spaced) in the circumferential direction.
  • the second intermediate member 15 is arranged between the first plate member 13 and the second plate member 14 in the axial direction, and is provided by the inner peripheral surface of the cylindrical portion 144 of the second plate member 14. It is rotatably supported (aligned).
  • the driven member 16 is an annular plate body, and is formed at intervals in the circumferential direction and extends outward in the radial direction (for example, three in the present embodiment) of torque transmission portions (elastic body contact portions) 163. including. As shown in FIG. 2, the driven member 16 is arranged between the first plate member 13 and the second plate member 14 of the first intermediate member 12 in the axial direction and is fixed to the damper hub 7 via a plurality of rivets. (Concatenated).
  • the plurality of outer springs SP1 are supported (guided) from the radial outer side and the turbine runner 5 side (transmission TM side) by the spring support portion 80a of the lockup piston 80, and the plurality of spring support portions 112 of the drive member 11. It is supported (guided) from the inside in the radial direction. As a result, the plurality of outer springs SP1 are arranged in the outer peripheral side region in the fluid chamber 9. Further, in the mounted state of the damper device 10, that is, in the state where torque is not transmitted between the drive member 11 and the driven member 16, each torque transmitting portion 113 of the drive member 11 is mounted on the end of the corresponding outer spring SP1. It comes into contact with the spring seat 90. As a result, in the mounted state of the damper device 10, each outer spring SP1 is held by two torque transmission portions 113 paired with each other of the drive member 11. The spring seat 90 may be omitted from the damper device 10.
  • each spring support portion 131 of the first plate member 13 faces the corresponding spring support portion 141 of the second plate member 14, and the first Each spring support 132 of the plate member 13 faces the corresponding spring support 142 of the second plate member 14.
  • the spring support portions 131, 141 facing each other and the spring support portions 132, 142 located radially inside the spring support portions 131, 141 have one corresponding first and second inner springs SP21 and SP22, respectively. Support (guide) one by one.
  • the plurality of first and second inner springs SP21 and SP22 are alternately spaced in the radial direction of the plurality of outer springs SP1 so as to overlap the plurality of outer springs SP1 in the radial direction. Is arranged in.
  • each inner torque transmission portion 133i of the first plate member 13 of the first intermediate member 12 and each torque transmission portion 143 of the second plate member 14 are different from each other in the spring support portion 131.
  • 132, 141, 142 abut between the first and second inner springs SP21, SP22 supported by the ends of both.
  • each torque transmission portion 153 of the second intermediate member 15 is supported by the same spring support portions 131, 132, 141 and 142 and is paired with each other between the first and second inner springs SP21 and SP22. Contact the end of the.
  • first and second inner springs SP21 and SP22 are connected in series via the torque transmission portion 153 of the second intermediate member 15, so that the outer spring SP1, that is, the first damper D1 is radially inside. It is possible to further reduce the rigidity of the second damper D2 arranged in.
  • a spring seat (not shown) may be attached to the ends of the first inner spring SP21 and the second inner spring SP22.
  • the first plate member 13 of the first intermediate member 12 is in a state where the damper device 10 is attached, that is, a state in which torque is not transmitted between the drive member 11 and the driven member 16, and each first outer torque transmission unit 133o. Is arranged so as to face the spring seat 90 attached to the end of the corresponding outer spring SP1 via a slight gap G, as shown in FIG. That is, in the mounted state of the damper device 10, at least one of the two first outer torque transmission portions 133o paired with each other of the first plate member 13 does not abut on the spring seat 90 of the corresponding outer spring SP1. ..
  • the claw portion 133a of the first outer torque transmission portion 133o of the first plate member 13 is arranged inside the claw portion 113a of the torque transmission portion 113 of the drive member 11 in the radial direction as shown in FIG. NS.
  • each torque transmission portion 163 of the driven member 16 is between the first and second inner springs SP21 and SP22 supported by spring support portions 131, 132, 141 and 142 which are different from each other. It abuts on both ends.
  • the driven member 16 is connected to the drive member 11 via the plurality of outer springs SP1, the first intermediate member 12, the plurality of first inner springs SP21, the second intermediate member 15, and the plurality of second inner springs SP22. It becomes possible to do.
  • each outer spring SP1 has two torque transmission portions 113 paired with each other of the drive member 11. It is placed between the two without being pre-compressed.
  • each first inner spring SP21 includes the corresponding inner torque transmission unit 133i and torque transmission unit 143 of the first intermediate member 12, the corresponding torque transmission unit 163 of the driven member 16, and the second intermediate member 15. It is arranged in a pre-compressed state with the corresponding torque transmission unit 153.
  • each of the second inner springs SP22 has the corresponding torque transmission portion 153 of the second intermediate member 15, the corresponding torque transmission portion 163 of the driven member 16, and the first intermediate member 12 in the mounted state of the damper device 10. It is arranged in a pre-compressed state between the corresponding inner torque transmission unit 133i and the torque transmission unit 143.
  • the damper device 10 has an input side stopper 17 that regulates the relative rotation between the drive member 11 and the first intermediate member 12 and a first intermediate member as stoppers that regulate the relative rotation between the drive member 11 and the driven member 16.
  • the input side stopper 17 includes a stopper portion 114 formed on the drive member 11 and a pair of stopper portions formed on the outer peripheral portion of the second plate member 14 so as to face each other via the outer spring SP1. Consists of. As shown in FIGS. 2 and 3, the stopper portion 114 is formed by further extending a part of each spring support portion 112 of the drive member 11 toward the pump impeller 4 and the turbine runner 5 in the axial direction. .. As a result, the input side stoppers 17 are provided at two locations in the circumferential direction with respect to the damper device 10.
  • each stopper portion 114 of the drive member 11 is arranged between the corresponding pair of stopper portions of the second plate member 14 so as not to come into contact with the side surface of each stopper portion.
  • Each stopper 114 of the drive member 11 comes into contact with one side surface of a pair of stoppers of the second plate member 14 located on both sides as the drive member 11 and the first intermediate member 12 rotate relative to each other.
  • the relative rotation of the drive member 11 and the first intermediate member 12 and the twist of each outer spring SP1 are regulated.
  • the output-side stopper 18 is composed of a stopper portion 134 extending axially from the inner peripheral portion of the first plate member 13 and an arc-shaped opening 164 formed in the driven member 16 (see FIG. 3). ).
  • a plurality of stopper portions 134 are provided on the first plate member 13, and the driven member 16 is provided with the same number of openings 164 as the stopper portions 134, and the output side stopper 18 is provided.
  • the damper device 10 is provided at a plurality of locations (for example, three locations in the present embodiment) in the circumferential direction.
  • each stopper portion 134 of the first plate member 13 is inserted into the corresponding opening 164 of the driven member 16 so as not to abut on the inner wall surfaces on both sides defining the opening 164. Is done.
  • the stopper portion 134 of the first plate member 13 hits one of the inner wall surfaces of the openings 164 located on both sides as the first intermediate member 12 and the driven member 16 rotate relative to each other. Touch.
  • the relative rotation of the first intermediate member 12 and the driven member 16 and the twist of each first inner spring SP21 and each second inner spring SP22 are regulated.
  • the input side stopper 17 (specifications of the drive member 11, the first intermediate member 12, the outer spring SP1, etc.) and the output side stopper 18 (first intermediate member 12, the second intermediate member 15, driven member 16, etc.)
  • the specifications of the first and second inner springs SP21, SP22, etc.) are the output side stopper 18 and the input side stopper when the torque transmitted to the front cover 3, that is, the input torque to the drive member 11 increases. It is configured (set) to operate in the order of 17. That is, in the damper device 10, the input torque to the drive member 11 reaches a torque (first value: predetermined value) T1 smaller than the torque T2 (second value) corresponding to the maximum twist angle ⁇ max of the damper device 10.
  • the output side stopper 18 regulates the relative rotation of the first intermediate member 12 and the driven member 16 (twisting of the first inner spring SP21). Further, when the input torque to the drive member 11 reaches the torque T2, the relative rotation (twisting of the outer spring SP1) between the drive member 11 and the first intermediate member 12 is regulated by the input side stopper 17. As a result, the damper device 10 has a two-stage (two-stage) damping characteristic.
  • a dynamic damper 20 is connected to the first intermediate member 12, which is a rotating element (first rotating element) of the damper device 10.
  • the dynamic damper 20 is a plurality of (for example, two in this embodiment) vibration-absorbing springs (vibration-absorbing elastic bodies) arranged between the mass body 21 including the turbine runner 5 and the mass body 21 and the first intermediate member 12. ) SPd and is included.
  • the "dynamic damper” is a mechanism for dampening the vibration by adding anti-phase vibration to the vibrating body at a frequency (engine rotation speed) corresponding to the resonance frequency of the vibrating body, and the vibrating body (the present embodiment).
  • the first intermediate member 12 is configured by connecting a spring (elastic body) and a mass body so as not to be included in the torque (average torque) transmission path. That is, by adjusting the rigidity of the vibration absorbing spring SPd and the weight of the mass body 21, the dynamic damper 20 can attenuate the vibration at a desired frequency.
  • the mass body 21 of the dynamic damper 20 includes an annular member 22 connected to the turbine runner 5 in addition to the turbine runner 5.
  • the annular member 22 includes an annular connecting plate 220 and a plurality of (three in the present embodiment) annular plates 221, 222, 223.
  • the inner peripheral portion of the connecting plate 220 is fixed to the turbine hub 52 via a plurality of rivets together with the inner peripheral portion of the turbine shell 50 so that the connecting plate 220 faces the back surface of the turbine runner 5 at a distance. ..
  • the connecting plate 220 includes a plurality of torque transmitting portions (elastic body contact portions) 225 extending in the axial direction from the outer peripheral portion at intervals in the circumferential direction (for example, four in the present embodiment).
  • the plurality of torque transmission units 225 are formed symmetrically with respect to the axial center of the annular member 22 so as to be close to each other by two (pair).
  • the two torque transmission units 225 paired with each other have an interval corresponding to the sum of the natural length of the vibration absorbing spring SPd and the thickness of the spring seat 91 mounted (fitted) on both ends of the vibration absorbing spring SPd. And face each other.
  • the annular plates 221, 222, 223 have the same outer diameter, are overlapped so that their outer peripheral surfaces form a single circumferential surface, and are fixed to the connecting plate 220 via a plurality of rivets. .. Further, as shown in FIG. 2, the inner diameter of the annular plate 222 is larger than the inner diameter of the annular plate 221 and the inner diameter of the annular plate 223 is larger than the inner diameter of the annular plate 222. This makes it possible to arrange the connecting plate 220 and the plurality of annular plates 221, 222, 223 in the region near the outer peripheral portion of the turbine runner 5, which tends to be a dead space.
  • the first plate member 13 of the first intermediate member 12 to be connected to the dynamic damper 20 is radially outwardly separated from the spring support portion 131 at intervals in the circumferential direction.
  • a plurality of (for example, four in this embodiment) second outer torque transmission units 135 that project so as to be included are included.
  • the plurality of second outer torque transmission portions 135 are the shafts of the first plate member 13 so as to be close to each other by two (pair) between the first outer torque transmission portions 133o adjacent to each other without the outer spring SP1.
  • Each includes a claw portion 135a that is formed symmetrically with respect to the center and extends axially toward the lockup piston 80.
  • the two second outer torque transmitting portions 135 (claw portions 135a) paired with each other correspond to the sum of the natural length of the vibration absorbing spring SPd and the thickness of the spring seats 91 attached to both ends of the vibration absorbing spring SPd. Oppose at regular intervals.
  • Each vibration absorbing spring SPd is a straight coil spring having the same specifications in this embodiment.
  • the vibration absorbing spring SPd may be an arc coil spring.
  • each vibration absorbing spring SPd is provided between a pair of torque transmission portions 225 of the connecting plate 220 (annular member 22) and a pair of second parts of the first plate member 13 (first intermediate member 12). It is arranged between the outer torque transmission units 135. That is, the spring seats 91 attached to both ends of each vibration absorbing spring SPd come into contact with the corresponding torque transmitting portions 225 and the second outer torque transmitting portion 135, respectively.
  • each vibration absorbing spring SPd that is, the dynamic damper 20 is connected to the first intermediate member 12 of the damper device 10.
  • the plurality of vibration absorbing springs SPd are arranged one by one between two outer springs SP1 adjacent to each other so as to be arranged in the circumferential direction on the same circumference as the outer spring SP1.
  • each vibration absorbing spring SPd overlaps the outer spring SP1 in both the axial direction and the circumferential direction of the starting device 1 and the damper device 10.
  • the claw portion 135a of each second outer torque transmission portion 135 of the first plate member 13 and the torque transmission portion 225 of the connecting plate 220 are aligned in the radial direction of the damper device 10.
  • the claw portion 135a of the second outer torque transmission portion 135 abuts on the spring seat 91 of the corresponding vibration absorbing spring SPd radially inside the torque transmission portion 225 of the connecting plate 220.
  • the spring seat 91 may be omitted from the dynamic damper 20.
  • the dynamic damper 20 (damper device 10) includes a stopper 23 that regulates the relative rotation between the annular member 22 (mass body 21) and the first plate member 13 (first intermediate member 12).
  • the stopper 23 (specifications of the first intermediate member 12, the annular member 22, the vibration absorbing spring SPd, etc.) is formed by the annular member 22 and the first intermediate member 12 before each vibration absorbing spring SPd is completely contracted. It is configured (set) to regulate relative rotation.
  • the stopper 23 may be omitted from the dynamic damper 20.
  • the drive member 11 which is a rotating element (second rotating element) to which the dynamic damper 20 is not connected is driven with the drive member 11 by the input side and output side stoppers 17 and 18.
  • An additional contact portion 113x is provided so as to abut the spring seat 91 attached to the end portion of the vibration absorbing spring SPd before the relative rotation with the member 16 is restricted.
  • the additional contact portion 113x is the rotation direction (arrow direction in FIG. 3, hereinafter, “positive” when the drive member 11 is rotated by the power from the engine EG (during driving) in the mounted state of the damper device 10.
  • the plurality of torque transmission portions 113 that come into contact with the spring seats 90 attached to the ends of the outer spring SP1 on the downstream side (traveling direction side) in the "rotation direction"). That is, the plurality of torque transmission portions 113 (including the claw portion 113a) that come into contact with the spring seat 90 attached to the downstream end portion of the outer spring SP1 in the normal rotation direction in the mounted state of the damper device 10 have a strength surface. It is extended in the circumferential direction to the downstream side (traveling direction side) in the normal rotation direction so as to have a circumference longer than the circumference required by the above. In the present embodiment, the end portion of the torque transmission portion 113 extended in the circumferential direction on the downstream side in the normal rotation direction is used as the additional contact portion 113x.
  • each additional contact portion 113x does not abut on the spring seat 91 of the corresponding vibration absorbing spring SPd of the dynamic damper 20, and the drive member 11 is positive with respect to the first intermediate member 12.
  • the spring seat 91 of the corresponding vibration absorbing spring SPd can be brought into contact with the spring seat 91.
  • each additional contact portion 113x has the input torque to the drive member 11 set to the torque T1 before the relative rotation between the drive member 11 and the first intermediate member 12 is restricted by the input side stopper 17.
  • the above two torque transmissions are made to come into contact with the spring seat 91 of the corresponding vibration absorbing spring SPd.
  • the circumference of the portion 113 (the angle around the axis of the damper device 10 that defines the circumference) is determined. That is, the first intermediate member 12 of the drive member 11 until each additional contact portion 113x abuts on the spring seat 91 of the corresponding vibration absorbing spring SPd and the drive member 11 (second rotating element) is connected to the vibration absorbing spring SPd.
  • the rotation angle with respect to is smaller than the rotation angle of the drive member 11 with respect to the driven member 16 until all of the input side and output side stoppers 17 and 18 are activated.
  • the claw portion 113a included in the additional contact portion 113x is partially arranged in the radial direction with the torque transmission portion 225 on the radial outside of the torque transmission portion 225 of the annular member 22 ( Overlap).
  • the claw portion 135a of the second outer torque transmission portion 135 of the first plate member 13 the torque transmission portion 225 of the annular member 22, and the claw portion 113a included in the additional contact portion 113x. (The end) will be lined up from the inside to the outside in this order.
  • the claw portion 133a of the first outer torque transmission portion 133o of the first plate member 13 is radially inside the claw portion 113a of the torque transmission portion 113 of the drive member 11. It abuts on the spring seat 90 of the corresponding outer spring SP1.
  • interference between the claw portion 113a of the additional contact portion 113x, the torque transmission portion 225 of the annular member 22, and the claw portion 135a of the second outer torque transmission portion 135 of the first plate member 13 is eliminated, and the drive member 11 It is possible to eliminate the interference between the claw portion 113a of the torque transmission portion 113 and the claw portion 133a of the first outer torque transmission portion 133o of the first plate member 13.
  • the torque from the engine EG is applied to the front cover 3, while the lockup clutch 8 of the starting device 1 executes the lockup and the input side and output side stoppers 17 and 18 are not operating.
  • the driven member 16 and the damper hub 7 are transmitted to the input shaft IS.
  • the fluctuation of the torque transmitted from the engine EG to the front cover 3 is mainly the first damper D1 and the second damper D2 of the damper device 10 acting in series, that is, the outer springs SP1, 1 and 1 and acting in series. It is damped (absorbed) by the second inner springs SP21 and SP22.
  • the mass body 21 (turbine runner 5 and the annular member 22) is subjected to the fluctuation torque transmitted to the first intermediate member 12. ) Swings with respect to the first intermediate member 12.
  • the vibration of the first intermediate member 12 can be damped by applying the vibration of the opposite phase from the oscillating mass body 21 to the first plate member 13.
  • the vibration from the engine EG can be damped (absorbed) by the dynamic damper 20, and more specifically, the vibration peak can be divided into two and the overall vibration level can be lowered. Therefore, the vibration damping performance of the damper device 10 can be further improved.
  • the first damper D1 that is, the plurality of outer springs SP1 and the plurality of vibration absorbing springs SPd act in parallel between the drive member 11 and the first intermediate member 12. However, it functions as an elastic body that transmits torque between the two.
  • the vibration absorbing spring SPd functions as an elastic body for transmitting torque between the drive member 11 and the first intermediate member 12, so that the second damper D2, that is, the first one is used.
  • the second inner springs SP21 and SP22 can be made more rigid.
  • the plurality of outer springs SP1 (first elastic body) included in the first damper D1 having high rigidity and hysteresis are in the mounted state. That is, in a state where torque is not transmitted between the drive member 11 and the driven member 16, a gap in the rotational direction between the drive member 11 and the first intermediate member 12 (maximum, twice the gap G). ) Is supported. Therefore, while the lockup is being executed, for example, the accelerator pedal of the vehicle V is loosely depressed on a downhill road, and the torque (driving torque) transmitted from the engine EG to the drive member 11 (front cover 3) and the road surface resistance.
  • the outer springs SP1 of the first damper D1 are the drive member 11 and the first. It comes to be supported with a gap in the rotation direction from the intermediate member 12.
  • the first damper D1 of the damper device 10 has a so-called idle running section (dead zone), and the torque transmitted from the engine EG to the drive member 11 and the driven member 16 from the transmission TM side.
  • the torque is substantially transmitted by the first damper D1, that is, the plurality of outer springs SP1. It disappears. Therefore, in the starting device 1, when the torque from the engine EG and the torque from the transmission TM side become substantially equal, the transmission of the torque by the first damper D1, that is, the plurality of outer springs SP1 is cut off, and the torque is cut off from the engine EG.
  • Vibration (fluctuation torque) can be suppressed from being transmitted to the input shaft IS (forward / backward switching mechanism BF and transmission TM) side.
  • the clutch C1 and the brake B1 of the forward / reverse switching mechanism BF can satisfactorily suppress the vibration of the friction plate and the separator plate caused by the vibration (fluctuation torque) from the engine EG and the generation of noise at the spline fitting portion.
  • the gap G at the time of assembling the outer spring SP1 is adapted in advance through experiments and analysis.
  • the first and second inner springs SP21 and SP22 included in the second damper D2 which has lower rigidity and hysteresis than the first damper D1 are located between the first intermediate member 12 and the driven member 16. That is, it is arranged in a pre-compressed state between the first intermediate member 12 and the second intermediate member 15 or between the second intermediate member 15 and the driven member 16.
  • the first and second inner springs SP21 and SP22 of the second damper D2 located inside the first damper D1 (outer spring SP1) in the radial direction are the first intermediate member 12 and the driven member 16. It is arranged in a pre-compressed state between them.
  • the second damper D2 includes a second intermediate member 15 and a first inner spring SP21 (intermediate elastic body) arranged in a precompressed state between the first intermediate member 12 and the second intermediate member 15.
  • a second inner spring SP22 (output side elastic body) arranged in a precompressed state between the second intermediate member 15 and the driven member 16.
  • the torque transmission system from the turbine runner 5 including the vibration absorbing spring SPd and the second damper D2 to the damper hub 7 Resonance may occur.
  • the first and second inner springs SP21 of the second damper D2 do not change the rigidity of the vibration absorbing spring SPd, that is, the spring constant (specifications), in response to the demand for the dynamic damper 20.
  • the frequency of the resonance can be shifted to the high frequency (high rotation) side or the low frequency (low rotation) side by adjusting the rigidity of the SP22, that is, the spring constant.
  • the resonance of the torque transmission system including the vibration absorbing spring SPd and the second damper D2 becomes apparent when the lockup is released. It becomes possible to suppress it. Further, when a relatively large torque is transmitted from the engine EG to the front cover 3 with the lockup released, the stopper 23 operates. As a result, it is possible to suppress the transmission of torque from the turbine runner 5 to the first intermediate member 12 in a state where each vibration absorbing spring SPd is completely contracted, and to further improve the durability of each vibration absorbing spring SPd.
  • the outer spring SP1 of the first damper D1 which has higher rigidity and hysteresis than the second damper D2, drives when torque is not transmitted between the drive member 11 and the driven member 16.
  • the first and second inner springs SP21 and SP22 of the second damper D2 which are supported with a gap in the rotation direction between the member 11 and the first intermediate member 12 and have lower rigidity and hysteresis than the first damper D1, are first. It is arranged in a pre-compressed state between the intermediate member 12 and the driven member 16, but is not limited to this.
  • one of the first and second dampers D1 and D2 which has high rigidity, has a rotation direction between the corresponding rotating elements when torque is not transmitted between the drive member 11 and the driven member 16.
  • the other elastic body which is supported by the gap in the above and has low rigidity, may be arranged in a pre-compressed state between the corresponding rotating elements.
  • one of the first and second dampers D1 and D2 having a high hysteresis has a rotation direction between the corresponding rotating elements when torque is not transmitted between the drive member 11 and the driven member 16.
  • the other elastic body, which is supported by the gap in the above and has a low hysteresis may be arranged in a pre-compressed state between the corresponding rotating elements.
  • the drive member 11 (second rotating element) may be connected to the vibration absorbing spring SPd by the additional contact portion 113x contacting the torque transmission portion 225 of the annular member 22, for example.
  • the additional contact portion 113x and the output side stopper 18 are subjected to relative rotation between the first intermediate member 12 and the driven member 16 after each additional contact portion 113x comes into contact with the spring seat 91 of the corresponding vibration absorbing spring SPd. It may be configured to be regulated. Further, the additional contact portion 113x may be separated from the torque transmission portion 113 so as to be aligned with the torque transmission portion 113 in the circumferential direction.
  • the rotating element (first rotating element) to which the dynamic damper 20 is connected may be a rotating element other than the first intermediate member 12 such as the drive member 11, and the vibration absorbing spring SPd is not connected to the dynamic damper 20.
  • the rotating element (second rotating element) connected to may be a rotating element other than the drive member 11, such as the first intermediate member 12.
  • the transmission TM may be a stepped transmission including at least one friction engaging element that does not require the forward / backward switching mechanism BF.
  • the damper device of the present disclosure includes a plurality of input elements (11) connected to the engine (EG), intermediate elements (12), and output elements (16) connected to the transmission (TM).
  • a damper device (10) including a second damper (D2) including a second elastic body (SP21, SP22) that transmits torque to and from the output element (16) the first and second dampers (D1). , D2), the first or second elastic body (SP1, SP21, SP22) having a higher rigidity or hysteresis transmits torque between the input element (11) and the output element (16).
  • the first When not, the first is supported by a gap in the rotational direction between the input element (11) and the intermediate element (12) or between the intermediate element (12) and the output element (16).
  • the first or second elastic body (SP1, SP21, SP22) of the first and second dampers (D1, D2) having low rigidity or hysteresis is the intermediate element (12) and the output element (16). It is arranged in a pre-compressed state between the input element (11) and the intermediate element (12).
  • one of the first and second dampers having a higher rigidity or hysteresis is the first or second elastic body when torque is not transmitted between the input element and the output element. It is supported with a gap in the direction of rotation between the input element and the intermediate element or between the intermediate element and the output element. As a result, when the difference between the torque transmitted from the engine to the input element and the torque transmitted from the transmission side to the output element becomes extremely small, one of the first and second dampers having higher rigidity or hysteresis is input. It will be supported with a gap in the direction of rotation between the element and the intermediate element or between the intermediate element and the output element.
  • the first or second elastic body of the first and second dampers having low rigidity or hysteresis is in a state of being pre-compressed between the intermediate element and the output element or between the input element and the intermediate element. Placed in. Thereby, when the torsional angle (absolute value) of the other of the first and second dampers having a low rigidity or hysteresis is relatively small, the substantial rigidity of the other can be increased. Therefore, when the torque transmitted from the engine to the input element is suddenly reduced, it is possible to satisfactorily suppress the vibration of the rotating element, particularly the intermediate element.
  • the first damper (D1) may include a plurality of the first elastic bodies (SP1)
  • the second damper (D2) may include a plurality of the second elastic bodies (SP21, SP22).
  • the synthetic spring constant of the plurality of first elastic bodies (SP1) may be larger than the synthetic spring constant of the plurality of second elastic bodies (SP21, SP22). .. That is, when torque is not transmitted between the input element and the output element, the first elastic body of the first damper, which has higher rigidity than the second damper, rotates in the rotation direction between the input element and the intermediate element.
  • the second elastic body of the second damper which has a lower rigidity than that of the first damper, may be arranged in a precompressed state between the intermediate element and the output element.
  • the second damper (D2) may be arranged inside the first damper (D1) in the radial direction of the damper device (10). This makes it possible to reduce the hysteresis of the second damper (second elastic body) and increase the substantial rigidity when the twist angle of the second damper is relatively small.
  • the intermediate element may include a first intermediate element (12) and a second intermediate element (15) included in the second damper (D2), and the second elastic body may include.
  • An intermediate elastic body (SP21) arranged in a precompressed state between the first intermediate element (12) and the second intermediate element (15), the second intermediate element (15), and the output element. It may include an output side elastic body (SP22) which is arranged in a state of being compressed in advance with (16).
  • the starting device of the present disclosure includes an input member (3) connected to the engine (EG), an output element (16), and a speed change in the starting device (1) including any of the damper devices (10).
  • the damper device (10) is between a mass body (21) including the turbine runner (5) and one of the mass body (21) and the input element (11) and the intermediate element (12).
  • the torque transmitted from the engine (EG) to the input element (11) by the other of the input element (11) and the intermediate element (12) is predetermined. When the value (T1) or more, it is connected to the vibration absorbing elastic body (SPd).
  • the input element and the vibration absorbing elastic body including the turbine runner A dynamic damper that applies anti-phase vibration to one of the intermediate elements is configured. Thereby, the vibration damping performance of the damper device can be further improved.
  • the lockup is executed by the lockup clutch and the torque transmitted from the engine to the input element is equal to or more than a predetermined value
  • the other of the input element and the intermediate element is connected to the vibration-absorbing elastic body, and the vibration-absorbing elasticity is connected to the vibration-absorbing elastic body.
  • the body functions as an elastic body that transmits torque between the input element and the intermediate element.
  • the resonance frequency can be shifted to the high frequency (high rotation) side.
  • the transmission (TM) may be a continuously variable transmission connected to the output member (7) via a forward / backward switching mechanism (BF) including friction engaging elements (C1, B1). ..
  • a forward / backward switching mechanism including friction engaging elements (C1, B1).
  • the invention of the present disclosure can be used in the manufacturing field of a damper device, a starting device, and the like.

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

Abstract

La présente invention concerne un dispositif d'amortisseur, lequel dispositif comprend un premier amortisseur comprenant un premier corps élastique pour transmettre un couple entre un élément intermédiaire et un élément d'entrée accouplé à un moteur et un second amortisseur comprenant un second corps élastique pour transmettre un couple entre l'élément intermédiaire et un élément de sortie accouplé à une transmission. Quand il n'y a pas de transmission de couple entre l'élément d'entrée et l'élément de sortie, le premier corps élastique, etc., dans l'un des premier et second amortisseurs avec une plus grande rigidité ou hystérésis est supporté avec un espace entre, par exemple, l'élément d'entrée et l'élément intermédiaire dans une direction de rotation, tandis que le second corps élastique, etc., dans l'autre des premier et second amortisseurs, est positionné dans un état pré-comprimé entre, par exemple, l'élément intermédiaire et l'élément de sortie. Ceci permet une bonne réduction des vibrations transmises à partir du moteur vers la transmission quand le couple à partir du côté moteur et le couple à partir du côté de transmission deviennent approximativement égaux et des vibrations d'un élément rotatif dans le dispositif d'amortisseur quand le couple à partir du côté moteur a soudainement diminué.
PCT/JP2021/009873 2020-03-27 2021-03-11 Dispositif d'amortisseur et dispositif de démarrage WO2021193116A1 (fr)

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JPH11173381A (ja) * 1997-12-12 1999-06-29 Exedy Corp ダンパー
JP2009507194A (ja) * 2005-09-08 2009-02-19 ルーク ラメレン ウント クツプルングスバウ ベタイリグングス コマンディートゲゼルシャフト トルクコンバータのための緩衝装置
JP4755000B2 (ja) * 2006-03-14 2011-08-24 株式会社エクセディ ダンパー機構
JP2016142404A (ja) * 2015-02-05 2016-08-08 富士重工業株式会社 トルクコンバータ

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EP0216476A1 (fr) * 1985-08-26 1987-04-01 Borg-Warner Automotive, Inc. Plateau mené d'embrayage avec répartition du décalage de friction
JP2000352442A (ja) * 1999-06-14 2000-12-19 Exedy Corp ダンパーディスク組立体
JP2015086965A (ja) * 2013-10-31 2015-05-07 株式会社エクセディ フライホイール組立体
JP6394406B2 (ja) * 2015-01-15 2018-09-26 アイシン精機株式会社 ダンパ装置
CN209324929U (zh) * 2018-10-19 2019-08-30 郑州宇通客车股份有限公司 一种扭转减振器及使用该扭转减振器的车辆

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Publication number Priority date Publication date Assignee Title
JPH11173381A (ja) * 1997-12-12 1999-06-29 Exedy Corp ダンパー
JP2009507194A (ja) * 2005-09-08 2009-02-19 ルーク ラメレン ウント クツプルングスバウ ベタイリグングス コマンディートゲゼルシャフト トルクコンバータのための緩衝装置
JP4755000B2 (ja) * 2006-03-14 2011-08-24 株式会社エクセディ ダンパー機構
JP2016142404A (ja) * 2015-02-05 2016-08-08 富士重工業株式会社 トルクコンバータ

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