WO2018047546A1 - Power transmission device - Google Patents

Power transmission device Download PDF

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Publication number
WO2018047546A1
WO2018047546A1 PCT/JP2017/028363 JP2017028363W WO2018047546A1 WO 2018047546 A1 WO2018047546 A1 WO 2018047546A1 JP 2017028363 W JP2017028363 W JP 2017028363W WO 2018047546 A1 WO2018047546 A1 WO 2018047546A1
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WO
WIPO (PCT)
Prior art keywords
input
output
torsion spring
power transmission
transmission device
Prior art date
Application number
PCT/JP2017/028363
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French (fr)
Japanese (ja)
Inventor
富山　直樹
Original Assignee
株式会社エクセディ
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Publication of WO2018047546A1 publication Critical patent/WO2018047546A1/en

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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
    • F16F15/137—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 the elastic members consisting of two or more springs of different kinds, e.g. elastomeric members and 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

Definitions

  • the present invention relates to a power transmission device, and more particularly to a power transmission device that transmits torque from an input-side member to an output-side member.
  • a power transmission device such as a torque converter with a lock-up mechanism is provided between the engine and the transmission.
  • the power transmission device basically includes an input plate, an output plate, and a damper portion disposed therebetween.
  • Torque is input to the input plate from a member on the engine side such as a flywheel.
  • the output plate is connected to a member on the transmission side.
  • the damper part has a flange and a plurality of coil springs. A part of the input plate is engaged with the flange, and the torque input to the flange is transmitted to the output plate via the coil spring.
  • the engaging portion between the input plate and the flange is composed of a plurality of claws and a groove into which the claws are fitted.
  • a rattling sound is generated due to torque fluctuation during power transmission.
  • a friction locking mechanism is provided to suppress the rattling noise caused by the gap between the meshing portions of the lock-up piston and the drive plate.
  • a corrugated elastic member is disposed at the meshing portion of the teeth so as to suppress rattling noise.
  • Patent Document 1 a friction locking mechanism is provided in order to suppress rattling noise, but an axial space for that is required, and a relatively large number of parts are required. Moreover, in the apparatus of Patent Document 2, a corrugated elastic member is provided. However, this type of elastic member is difficult to manufacture and requires a relatively large arrangement space. Further, the configuration of Patent Document 2 is difficult to apply to an apparatus in which the input plate and the output plate are arranged at positions shifted in the axial direction.
  • An object of the present invention is to enable suppression of rattling noise in a power transmission device with a simple configuration.
  • a power transmission device is a device that transmits torque from an input-side member to an output-side member.
  • the power transmission device includes an input side rotation member, an output side rotation member, and an urging member.
  • the input side rotating member has a first engaging portion, and torque is input from the input side member.
  • the output-side rotating member has a second engaging portion that can be engaged with the first engaging portion in the rotational direction via a predetermined gap, and is arranged side by side with the input-side rotating member in the axial direction. Torque is output to the member.
  • the urging member is disposed between the input side rotation member and the output side rotation member, and can be elastically deformed more than the gap between the first engagement portion and the second engagement portion, and the input side rotation member And at least one of the output side rotation members is urged in the rotation direction.
  • At least one of the input side rotating member and the output side rotating member is biased in the rotational direction by the biasing member.
  • it can be configured such that a gap is secured between the first engaging portion and the second engaging portion of both rotating members by the biasing member in a state where torque is not input.
  • the input torque is transmitted to the output side rotating member via the biasing member and output to the output side member.
  • the torque is directly transmitted from the first engaging portion to the second engaging portion.
  • both the engaging portions are brought into contact with each other by the biasing member in a state where no torque is inputted.
  • the biasing member is a torsion spring.
  • the torsion spring extends from one end of the coil portion, the first arm that engages with the input side rotating member, and extends from the other end of the coil portion, and the tip portion engages with the output side rotating member. And a second arm.
  • the biasing member is constituted by a torsion spring
  • the rattling noise can be suppressed with a simple configuration.
  • the urging member can be easily assembled.
  • the specification can be easily changed by changing the wire diameter, arm length, etc. of the torsion spring.
  • the apparatus further includes a first support member and a second support member arranged at a predetermined interval in the circumferential direction on one of the input side rotation member and the output side rotation member.
  • the urging member is a torsion spring
  • the torsion spring includes a first coil part, a second coil part, a connecting part, a first arm, and a second arm.
  • the first coil portion is supported by the first support member.
  • the second coil portion is supported by the second support member.
  • the connecting portion extends between one end of the first coil portion and one end of the second coil portion.
  • the first arm extends from the other end of the first coil portion, and the distal end engages with the other of the input side rotating member and the output side rotating member.
  • the second arm extends from the other end of the second coil portion, and the distal end engages with the other of the input side member and the output side rotation member.
  • one of the first engagement portion and the second engagement portion is an engagement claw extending in the axial direction and having a first width in the circumferential direction.
  • the other of the first engaging portion and the second engaging portion is an engaging groove having an engaging claw inserted therein and having a second width in the circumferential direction.
  • a power transmission device is a device that transmits torque from an input-side member to an output-side member.
  • the power transmission device includes an input side rotating member, an output side rotating member, and a torsion spring.
  • the input side rotating member has a first engaging portion, and torque is input from the input side member.
  • the output side rotation member has a second engagement portion that can be engaged with the first engagement portion in the rotation direction via a predetermined gap, and outputs torque to the output side member.
  • the torsion spring is disposed between the input side rotation member and the output side rotation member, and is capable of elastic deformation more than the gap between the first engagement portion and the second engagement portion, At least one of the output side rotating members is biased in the rotational direction.
  • the rattling noise can be suppressed with a simple configuration.
  • the torsion spring can be easily assembled. Furthermore, the specification can be easily changed by changing the wire diameter, arm length, etc. of the torsion spring.
  • the rattling noise in the power transmission device can be suppressed with a simple configuration.
  • FIG. 4 is a side view of FIG. 3.
  • FIG. 1 is a cross-sectional view of a power transmission device according to an embodiment of the present invention.
  • An engine (not shown) is arranged on the left side of FIG. 1, and a transmission (not shown) is arranged on the right side of the figure.
  • OO shown in FIG. 1 is a rotational axis of power transmission.
  • a power transmission device 1 shown in FIG. 1 is a device for transmitting torque from a housing 2 which is a member on the engine side (input side) to an input shaft 3 of a transmission which is a member on the transmission side (output side).
  • the housing 2 is configured to be rotatable around the rotation axis O, and is a first case 5 fixed to an engine-side member (not shown), and a second case 6 having an outer peripheral portion fixed to the outer peripheral portion of the first case 5. And have.
  • the housing 2 is filled with lubricating oil
  • the power transmission device 1 is a wet type (a type that operates in the lubricating oil).
  • the power transmission device 1 includes an input plate 10 (an example of an input-side rotating member), a damper device 11, and a plurality of torsion springs 12 (an example of an urging member).
  • the damper device 11 includes a flange 14 (an example of an output side rotating member), a plurality of outer peripheral side torsion springs 15 and inner peripheral side torsion springs 16, and an output plate 17.
  • the input plate 10 is fixed to the outer peripheral portion by welding on the inner side surface of the second case 6.
  • the input plate 10 includes an annular and disk-shaped fixing portion 10a, and a plurality of claws 10b (first engaging portions) formed by bending a part of the outer peripheral end of the fixing portion 10a toward the engine side. ing.
  • the inner peripheral end portion of the fixed portion 10a is fixed to the inner side surface of the second case 6 as described above.
  • a plurality of mounting holes 10c are formed in the fixed portion 10a at predetermined intervals in the circumferential direction.
  • FIG. 2 shows a view of the outer periphery of the input plate 10 and the flange 14 of FIG. 1 as viewed from the transmission side.
  • the flange 14 is a disk-shaped plate, and is arranged side by side with the input plate 10 (more precisely, the fixed portion 10a of the input plate 10) in the axial direction. That is, the flange 14 and the input plate 10 are arranged at different positions in the axial direction. As shown in FIG. 2, the flange 14 has a plurality of claw receiving portions 14 a and a plurality of outer peripheral side accommodating portions 14 b and inner peripheral side accommodating portions 14 c, respectively. A plurality of mounting holes 14d are formed between the circumferential directions of the plurality of claw receiving portions 14a.
  • the plurality of claw receiving portions 14 a protrude radially outward from the outer peripheral end and are formed at positions corresponding to the claw 10 b of the input plate 10.
  • the claw receiving portion 14a is formed with a groove 14e (second engaging portion) having a predetermined width in the circumferential direction and opened on the outer peripheral side.
  • the claw 10b of the input plate 10 is inserted into the groove 14e. When the claw 10b is located at the center in the groove 14e, a gap ⁇ is secured on both sides between the claw 10b and the groove 14e.
  • the torsion spring 12 has a coil portion 12a, a first arm 12b, and a second arm 12c.
  • the first arm 12b extends from one end of the coil portion 12a to the inner peripheral side, and the tip is bent toward the transmission side in the axial direction.
  • the bent portion is inserted into the mounting hole 10 c of the input plate 10.
  • the second arm 12c extends from the other end of the coil portion 12a to the inner peripheral side, and the tip is bent toward the engine side in the axial direction.
  • the bent portion is inserted into the mounting hole 14 d of the flange 14.
  • the torsion spring 12 and each member are designed so that a gap ⁇ is secured between both sides of the claw 10b and the groove 14e in a state where no torque is input to the apparatus.
  • the output plate 17 includes a first plate 21 and a second plate 22 that are arranged to face each other in the axial direction. Note that the inner periphery of the first plate 21 and the second plate 22 is fixed to the outer periphery of the hub 24 by rivets 23. Accordingly, the first plate 21 and the second plate 22 are not movable in the axial direction and are not relatively rotatable.
  • the first plate 21 and the second plate 22 are formed with a plurality of outer peripheral side openings 21a, 22a and inner peripheral side openings 21b, 22b arranged in the circumferential direction, respectively. Each opening part 21a, 22a, 21b, 22b is arrange
  • outer and inner torsion springs 15, 16 The outer peripheral side torsion spring 15 is accommodated in the outer peripheral side accommodating portion 14 b of the flange 14, and is supported in the axial direction and the radial direction by the outer peripheral side openings 21 a and 22 a of the output plate 17. Further, the inner peripheral side torsion spring 16 is accommodated in the inner peripheral side accommodating portion 14 c of the flange 14, and is supported axially and radially by the inner peripheral side openings 21 b and 22 b of the output plate 17. By these torsion springs 15 and 16, the flange 14 and the output plate 17 are elastically connected in the rotational direction.
  • the torsion spring 12 can obtain a low rigidity torsion characteristic. For this reason, in addition to the relatively high rigidity torsional characteristics by the outer peripheral side and inner peripheral side torsion springs 15, 16, low rigidity torsional characteristics can be obtained, and multi-stage torsional characteristics can be realized.
  • the arrangement of the torsion spring 12 is not limited to the above embodiment.
  • they may be arranged on the inner peripheral side of the input plate 10 ′ and the flange 14 ′.
  • the claw 10b 'of the input plate 10' is engaged with a groove 14a 'formed on the outer peripheral surface of the flange 14'.
  • the torsion spring 12 ′ has a first arm 12 b ′ and a second arm 12 c ′ extending from the coil portion 12 a ′ to the outer peripheral side, and tip ends thereof in attachment holes formed in the input plate 10 ′ and the flange 14 ′, respectively. It is attached.
  • FIG. 5 shows a second embodiment.
  • the second embodiment is the same as the first embodiment except for the configuration of the input plate 30, the flange 31, and the torsion spring 32. Therefore, in FIG. 3, only a different part is shown.
  • 5A and 5B are front partial views, FIG. 5A shows a portion where the torsion spring 32 is mounted, and FIG. 5B shows a claw 30b and a flange 31 of the input plate 30.
  • FIG. 2C is a side view of FIG.
  • the input plate 30 is fixed to the outer peripheral portion by welding on the inner side surface of the first case.
  • the input plate 30 is formed in an annular disk shape, and has a plurality of protrusions 30a and a plurality of claws 30b as shown in FIGS.
  • the plurality of protrusions 30a are formed to protrude radially outward from the outer peripheral surface of the input plate 30, and are arranged at predetermined intervals in the circumferential direction.
  • a pair of pins 34 are attached to the projecting portions 30a at both ends in the circumferential direction so as to extend along the axial direction.
  • the plurality of claws 30b are formed by bending a part of the outer peripheral end of the input plate 10 to the engine side, and extend in the axial direction.
  • the flange 31 is a disk-shaped plate, and is arranged side by side with the input plate 30 in the axial direction.
  • a plurality of grooves 31 a having a predetermined depth on the inner peripheral side and open to the outer peripheral side are formed at the outer peripheral end of the flange 31.
  • Claws 30b of the input plate 30 are inserted into the plurality of grooves 31a (see FIG. 5B).
  • a gap ⁇ is secured on both sides between the claw 30b and the groove 31a.
  • the torsion spring 32 is disposed at a position corresponding to, for example, four grooves among the plurality of grooves 31 a of the flange 31. And the nail
  • the torsion spring 32 includes a first coil portion 32a and a second coil portion 32b, a connecting portion 32c, and a first arm 32d and a second arm 32e.
  • the first coil portion 32 a is supported by one pin 34 attached to the protruding portion 30 a of the input plate 30.
  • the second coil portion 32b is supported by the other pin 34.
  • the connecting part 32c extends in the circumferential direction, and connects between one end of the first coil part 32a and one end of the second coil part 32b.
  • the first arm 32d extends from the other end of the first coil portion 32a to the inner peripheral side.
  • the distal end portion of the first arm 32 d is in contact with one side surface of the groove 31 a of the flange 31.
  • the second arm 32 e extends from the other end of the second coil portion 32 b to the inner peripheral side, and the tip end is in contact with the other side surface of the groove 31 a of the flange 31.
  • the torsion spring 32 and each member are designed so that a gap ⁇ is secured between both sides of the claw 30b and the groove 31a in a state where no torque is input to the apparatus.
  • the first arm 32d and the second arm 32e are set in the groove in a state where the torsion spring 32 is elastically deformed. That is, the torsion spring 32, the input plate 30, and the flange 31 are set with the pre-torque applied in both rotational directions between the input plate 30 and the flange 31 by the torsion spring 32.
  • the gap ⁇ is secured between both ends of the claw 30b and the groove 31a as in the first embodiment.
  • the amount of elastic deformation of the first arm 32d of the torsion spring 32 increases as shown in FIG. 7, and one end surface of the claw 30b comes into contact with the side surface of the groove 31a.
  • torque is directly input from the input plate 30 to the flange 31 via the claw 30b and the side surface of the groove 31a.
  • the torque input to the flange 31 is transmitted to the output plate 17 via the outer peripheral side torsion spring 15 and the inner peripheral side torsion spring 16, and is output to the transmission input shaft 3 via the hub.
  • the torsion spring 32 can obtain a low rigidity torsion characteristic. For this reason, in addition to the relatively high rigidity torsional characteristics by the outer peripheral side and inner peripheral side torsion springs 15, 16, low rigidity torsional characteristics can be obtained, and multi-stage torsional characteristics can be realized.
  • the pre-torque is applied to the torsion spring 32 so that the same gap ⁇ is secured between both sides of the claw 30b and the side surface of the groove 31a.
  • one end face of the claw 30b corresponds. You may set so that it may contact
  • FIG. 8 shows a third embodiment.
  • the input plate 40 is disposed on the outer peripheral side, and the flange 41 is disposed at the same position in the axial direction on the inner peripheral side.
  • the input plate 40 and the flange 41 are annular plate members and are capable of relative rotation.
  • a plurality of claws 40a projecting radially inward are formed on the inner peripheral surface of the input plate 40.
  • a groove 41a having a predetermined depth on the inner peripheral side and opening on the outer peripheral side is formed on the outer peripheral surface of the flange 41.
  • a claw 40a is inserted into the groove 41a.
  • the torsion spring 42 has a coil portion 42a, a first arm 42b, and a second arm 42c.
  • the coil portion 42 a is attached to and supported by a pin 43 fixed to the side surface of the flange 41.
  • the first arm 42b extends from one end of the coil portion 42a to the outer peripheral side, and the tip is bent toward the axial transmission side.
  • the bent portion is inserted into the mounting hole of the input plate 40.
  • the second arm 42c extends in the lateral direction from the other end of the coil portion 42a, and the tip is bent toward the engine side in the axial direction.
  • the bent portion is inserted into the mounting hole of the flange 41.
  • the torsion spring 42 and each of the torsion springs 42 and each of the grooves 41a are secured so that a gap is secured between both sides of the claw 40a and the groove 41a in a state where no torque is input to the apparatus.
  • the member is designed.
  • FIG. 9 shows a fourth embodiment.
  • the input plate 50 and the flange 51 are arranged in the radial direction at the same position in the axial direction. And the input plate 50 is arrange
  • the input plate 50 and the flange 51 are annular plate members and are capable of relative rotation.
  • a plurality of claws 50 a projecting radially inward are formed on the inner peripheral surface of the input plate 50.
  • a plurality of first grooves 51a and second grooves 51b having a predetermined depth on the inner peripheral side and opened to the outer peripheral side are formed on the outer peripheral surface of the flange 51.
  • claw 50a is inserted in the 1st groove
  • the second groove 51b is wider in the circumferential direction than the first groove 51a, and a first arm 52b and a second arm 52c of a torsion spring 52 described later are inserted therein.
  • the torsion spring 52 is disposed at a position corresponding to the second groove 51 b of the flange 51.
  • the torsion spring 52 has a main body 52a, a first arm 52b, and a second arm 52c.
  • the main body 52a is substantially V-shaped and is supported by three pins 53a, 53b, 53c. More specifically, the three pins 53a to 53c are arranged side by side in the circumferential direction at a predetermined interval. Both end portions of the main body portion 52a are supported on the outer peripheral side of the pins 53a and 53c, and the central portion of the main body portion 52a is supported on the inner peripheral side of the pin 53b.
  • the first arm 52b extends from one end of the main body 52a to the inner peripheral side.
  • the distal end portion of the first arm 52b is in contact with one side surface of the second groove 51b of the flange 51.
  • the second arm 52 c extends from the other end of the main body portion 52 a to the inner peripheral side, and the tip end is in contact with the other side surface of the second groove 51 b of the flange 51.
  • the torsion spring 52 and each member are designed such that a gap is secured between both sides of the claw 50a and the first groove 51a in a state where no torque is input to the apparatus. .
  • the torsion spring is used as the urging member, but another form of urging member may be used.
  • rattling noise during power transmission can be suppressed with a simple configuration.

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

Abstract

Provided is a power transmission device wherein tooth contact noise is suppressed using a simple configuration. This device comprises an input plate (10), a flange (11), and a torsion spring (12). The input plate (10) has a catch (10b) and is adapted such that torque is applied thereto. The flange (11) has a groove (14e) which can engage with the catch (10b) with a predetermined gap therebetween in the rotational direction. The flange (11) is disposed next to the input plate (10) in the axial direction and outputs torque. The torsion spring (12) is disposed between the input plate (10) and the flange (11), can elastically deform an amount greater than the gap between the catch (10b) and the groove (14e), and presses the input plate (10) and/or the flange (11) in the rotational direction.

Description

動力伝達装置Power transmission device
　本発明は、動力伝達装置、特に、入力側の部材から出力側の部材にトルクを伝達する動力伝達装置に関する。 The present invention relates to a power transmission device, and more particularly to a power transmission device that transmits torque from an input-side member to an output-side member.
　自動車等の車両においては、エンジンとトランスミッションとの間に、ロックアップ機構付きのトルクコンバータ等の動力伝達装置が設けられている。 In vehicles such as automobiles, a power transmission device such as a torque converter with a lock-up mechanism is provided between the engine and the transmission.
　例えば、動力伝達装置は、基本的に、入力プレートと、出力プレートと、それらの間に配置されたダンパ部と、を備えている。入力プレートはフライホイール等のエンジン側の部材からトルクが入力される。また、出力プレートはトランスミッション側の部材に連結される。ダンパ部は、フランジ及び複数のコイルスプリングを有している。フランジには入力プレートの一部が係合し、フランジに入力されたトルクはコイルスプリングを介して出力プレートに伝達される。 For example, the power transmission device basically includes an input plate, an output plate, and a damper portion disposed therebetween. Torque is input to the input plate from a member on the engine side such as a flywheel. The output plate is connected to a member on the transmission side. The damper part has a flange and a plurality of coil springs. A part of the input plate is engaged with the flange, and the torque input to the flange is transmitted to the output plate via the coil spring.
　以上のような動力伝達装置では、入力プレートとフランジとの間の係合部は、複数の爪と、爪が嵌合する溝と、から構成されている。このような係合部においては、爪と溝との間に隙間が存在するので、動力伝達時のトルク変動によって、歯打ち音が発生する。 In the power transmission device as described above, the engaging portion between the input plate and the flange is composed of a plurality of claws and a groove into which the claws are fitted. In such an engaging portion, since there is a gap between the claw and the groove, a rattling sound is generated due to torque fluctuation during power transmission.
　そこで、特許文献１に示されたロックアップ機構付きのトルクコンバータでは、摩擦係止機構を設け、ロックアップピストンとドライブプレートとの噛合部分の隙間に起因する歯打ち音を抑えるようにしている。 Therefore, in the torque converter with a lock-up mechanism shown in Patent Document 1, a friction locking mechanism is provided to suppress the rattling noise caused by the gap between the meshing portions of the lock-up piston and the drive plate.
　また、特許文献２の装置では、歯の噛合部分に波板形状の弾性部材を配置し、歯打ち音を抑えるようにしている。 Also, in the device of Patent Document 2, a corrugated elastic member is disposed at the meshing portion of the teeth so as to suppress rattling noise.
特開２００８－２９８１１３号公報JP 2008-298113 A 特開昭６０－１５９４２０号公報JP 60-159420 A
　特許文献１では、歯打ち音を抑制するために摩擦係止機構が設けられているが、そのための軸方向スペースが必要になり、また比較的多くの部品点数が必要になる。また、特許文献２の装置では、波板形状の弾性部材が設けられているが、この種の弾性部材は製造が困難であり、しかも比較的広い配置スペースが必要となる。また、特許文献２の構成は、入力プレートと出力プレートとが軸方向にずれた位置に配置されている装置には適用することが困難である。 In Patent Document 1, a friction locking mechanism is provided in order to suppress rattling noise, but an axial space for that is required, and a relatively large number of parts are required. Moreover, in the apparatus of Patent Document 2, a corrugated elastic member is provided. However, this type of elastic member is difficult to manufacture and requires a relatively large arrangement space. Further, the configuration of Patent Document 2 is difficult to apply to an apparatus in which the input plate and the output plate are arranged at positions shifted in the axial direction.
　本発明の課題は、動力伝達装置における歯打ち音を、簡単な構成で抑制できるようにすることにある。 An object of the present invention is to enable suppression of rattling noise in a power transmission device with a simple configuration.
　（１）本発明の一側面に係る動力伝達装置は、入力側の部材から出力側の部材にトルクを伝達する装置である。この動力伝達装置は、入力側回転部材と、出力側回転部材と、付勢部材と、を備えている。入力側回転部材は、第１係合部を有し、入力側の部材からトルクが入力される。出力側回転部材は、第１係合部に対して回転方向に所定の隙間を介して係合可能な第２係合部を有し、入力側回転部材と軸方向に並べて配置され、出力側の部材にトルクを出力する。付勢部材は、入力側回転部材と出力側回転部材との間に配置され、第１係合部と第２係合部との間の隙間以上の弾性変形が可能であり、入力側回転部材及び出力側回転部材の少なくとも一方を回転方向に付勢する。 (1) A power transmission device according to one aspect of the present invention is a device that transmits torque from an input-side member to an output-side member. The power transmission device includes an input side rotation member, an output side rotation member, and an urging member. The input side rotating member has a first engaging portion, and torque is input from the input side member. The output-side rotating member has a second engaging portion that can be engaged with the first engaging portion in the rotational direction via a predetermined gap, and is arranged side by side with the input-side rotating member in the axial direction. Torque is output to the member. The urging member is disposed between the input side rotation member and the output side rotation member, and can be elastically deformed more than the gap between the first engagement portion and the second engagement portion, and the input side rotation member And at least one of the output side rotation members is urged in the rotation direction.
　この装置では、入力側回転部材及び出力側回転部材の少なくとも一方が付勢部材によって回転方向に付勢されている。 In this device, at least one of the input side rotating member and the output side rotating member is biased in the rotational direction by the biasing member.
　ここで、例えば、トルクが入力されていない状態で、付勢部材によって両回転部材の第１係合部と第２係合部との間に隙間が確保されるように構成することができる。この場合は、入力側回転部材にトルクが入力されると、入力されたトルクは付勢部材を介して出力側回転部材に伝達され、出力側の部材に出力される。入力されたトルクが大きくなって付勢部材が弾性変形し、両係合部間の隙間がなくなると、トルクは第１係合部から第２係合部に直接伝達される。 Here, for example, it can be configured such that a gap is secured between the first engaging portion and the second engaging portion of both rotating members by the biasing member in a state where torque is not input. In this case, when torque is input to the input side rotating member, the input torque is transmitted to the output side rotating member via the biasing member and output to the output side member. When the input torque is increased and the urging member is elastically deformed and there is no gap between the two engaging portions, the torque is directly transmitted from the first engaging portion to the second engaging portion.
　また、トルクが入力されていない状態で、付勢部材によって両係合部が当接するように構成することができる。 Further, it can be configured such that both the engaging portions are brought into contact with each other by the biasing member in a state where no torque is inputted.
　いずれの場合も、微小なトルク変動による入力側回転部材及び出力側回転部材の回転が付勢部材によって規制されるので、軸方向に並べて配置された入力側回転部材及び出力側回転部材の係合部における歯打ち音を抑えることができる。 In any case, since the rotation of the input side rotation member and the output side rotation member due to minute torque fluctuation is restricted by the biasing member, the input side rotation member and the output side rotation member arranged in the axial direction are engaged. The rattling noise at the part can be suppressed.
　（２）好ましくは、付勢部材はねじりばねである。ねじりばねは、コイル部と、コイル部の一端から延びるとともに先端部が入力側回転部材に係合する第１アームと、コイル部の他端から延びるとともに先端部が出力側回転部材に係合する第２アームと、を有する。 (2) Preferably, the biasing member is a torsion spring. The torsion spring extends from one end of the coil portion, the first arm that engages with the input side rotating member, and extends from the other end of the coil portion, and the tip portion engages with the output side rotating member. And a second arm.
　ここでは、付勢部材がねじりばねによって構成されているので、簡単な構成で歯打ち音を抑制できる。また、付勢部材の組み付けが容易になる。さらに、ねじりばねの線径やアーム長さ等を変更することで、容易に仕様を変更することができる。 Here, since the biasing member is constituted by a torsion spring, the rattling noise can be suppressed with a simple configuration. Further, the urging member can be easily assembled. Furthermore, the specification can be easily changed by changing the wire diameter, arm length, etc. of the torsion spring.
　（３）好ましくは、入力側回転部材及び出力側回転部材の一方に円周方向に所定の間隔をあけて配置された第１支持部材及び第２支持部材をさらに備えている。そして、付勢部材はねじりばねであり、ねじりばねは、第１コイル部と、第２コイル部と、連結部と、第１アームと、第２アームと、を有する。第１コイル部は第１支持部材に支持されている。第２コイル部は第２支持部材に支持されている。連結部は第１コイル部の一端と第２コイル部の一端との間に延びている。第１アームは第１コイル部の他端から延びるとともに先端部が入力側回転部材及び出力側回転部材の他方に係合する。第２アームは第２コイル部の他端から延びるとともに先端部が入力側部材及び出力側回転部材の他方に係合する。 (3) Preferably, the apparatus further includes a first support member and a second support member arranged at a predetermined interval in the circumferential direction on one of the input side rotation member and the output side rotation member. The urging member is a torsion spring, and the torsion spring includes a first coil part, a second coil part, a connecting part, a first arm, and a second arm. The first coil portion is supported by the first support member. The second coil portion is supported by the second support member. The connecting portion extends between one end of the first coil portion and one end of the second coil portion. The first arm extends from the other end of the first coil portion, and the distal end engages with the other of the input side rotating member and the output side rotating member. The second arm extends from the other end of the second coil portion, and the distal end engages with the other of the input side member and the output side rotation member.
　（４）好ましくは、第１係合部及び第２係合部の一方は、軸方向に延び、円周方向に第１幅を有する係合爪である。また、第１係合部及び第２係合部の他方は、係合爪が挿入され、円周方向に第２幅を有する係合溝である。 (4) Preferably, one of the first engagement portion and the second engagement portion is an engagement claw extending in the axial direction and having a first width in the circumferential direction. The other of the first engaging portion and the second engaging portion is an engaging groove having an engaging claw inserted therein and having a second width in the circumferential direction.
　（５）本発明の別の側面に係る動力伝達装置は、入力側の部材から出力側の部材にトルクを伝達する装置である。この動力伝達装置は、入力側回転部材と、出力側回転部材と、ねじりばねと、を備えている。入力側回転部材は、第１係合部を有し、入力側の部材からトルクが入力される。出力側回転部材は、第１係合部に対して回転方向に所定の隙間を介して係合可能な第２係合部を有し、出力側の部材にトルクを出力する。ねじりばねは、入力側回転部材と出力側回転部材との間に配置され、第１係合部と第２係合部との間の隙間以上の弾性変形が可能であり、入力側回転部材及び出力側回転部材の少なくとも一方を回転方向に付勢する。 (5) A power transmission device according to another aspect of the present invention is a device that transmits torque from an input-side member to an output-side member. The power transmission device includes an input side rotating member, an output side rotating member, and a torsion spring. The input side rotating member has a first engaging portion, and torque is input from the input side member. The output side rotation member has a second engagement portion that can be engaged with the first engagement portion in the rotation direction via a predetermined gap, and outputs torque to the output side member. The torsion spring is disposed between the input side rotation member and the output side rotation member, and is capable of elastic deformation more than the gap between the first engagement portion and the second engagement portion, At least one of the output side rotating members is biased in the rotational direction.
　ここでは、前記同様に、簡単な構成で歯打ち音を抑制できる。また、ねじりばねの組み付けが容易になる。さらに、ねじりばねの線径やアーム長さ等を変更することで、容易に仕様を変更することができる。 Here, as described above, the rattling noise can be suppressed with a simple configuration. Further, the torsion spring can be easily assembled. Furthermore, the specification can be easily changed by changing the wire diameter, arm length, etc. of the torsion spring.
　以上のような本発明では、動力伝達装置における歯打ち音を、簡単な構成で抑制することができる。 In the present invention as described above, the rattling noise in the power transmission device can be suppressed with a simple configuration.
本発明の第１実施形態による動力伝達装置の断面構成図。The cross-sectional block diagram of the power transmission device by 1st Embodiment of this invention. 図１の正面部分図。The front fragmentary view of FIG. 第１実施形態の変形例の図２に相当する図。The figure equivalent to FIG. 2 of the modification of 1st Embodiment. 図３の側面図。FIG. 4 is a side view of FIG. 3. 本発明の第２実施形態の図２に相当する図。The figure equivalent to FIG. 2 of 2nd Embodiment of this invention. 第２実施形態の動作を説明するための図。The figure for demonstrating operation | movement of 2nd Embodiment. 第２実施形態の動作を説明するための図。The figure for demonstrating operation | movement of 2nd Embodiment. 第３実施形態の図２に相当する図。The figure equivalent to FIG. 2 of 3rd Embodiment. 第４実施形態の図２に相当する図。The figure equivalent to FIG. 2 of 4th Embodiment.
　図１は、本発明の一実施形態による動力伝達装置の断面図である。図１の左側にはエンジン（図示せず）が配置され、図の右側にトランスミッション（図示せず）が配置されている。なお、図１に示すＯ－Ｏが動力伝達の回転軸芯である。 FIG. 1 is a cross-sectional view of a power transmission device according to an embodiment of the present invention. An engine (not shown) is arranged on the left side of FIG. 1, and a transmission (not shown) is arranged on the right side of the figure. Note that OO shown in FIG. 1 is a rotational axis of power transmission.
　－第１実施形態－
　［動力伝達装置の全体構成］
　図１に示す動力伝達装置１は、エンジン側（入力側）の部材であるハウジング２からトランスミッション側（出力側）の部材であるトランスミッションの入力軸３にトルクを伝達するための装置である。ハウジング２は、回転軸芯Ｏまわりに回転可能に構成され、図示しないエンジン側の部材に固定される第１ケース５と、外周部が第１ケース５の外周部に固定された第２ケース６と、を有している。ハウジング２内には潤滑油が充填され、動力伝達装置１は湿式タイプ（潤滑油内で作動するタイプ）である。 -First embodiment-
[Overall configuration of power transmission device]
A power transmission device 1 shown in FIG. 1 is a device for transmitting torque from a housing 2 which is a member on the engine side (input side) to an input shaft 3 of a transmission which is a member on the transmission side (output side). The housing 2 is configured to be rotatable around the rotation axis O, and is a first case 5 fixed to an engine-side member (not shown), and a second case 6 having an outer peripheral portion fixed to the outer peripheral portion of the first case 5. And have. The housing 2 is filled with lubricating oil, and the power transmission device 1 is a wet type (a type that operates in the lubricating oil).
　動力伝達装置１は、入力プレート１０（入力側回転部材の一例）と、ダンパ装置１１と、複数のねじりばね１２（付勢部材の一例）と、を有している。ダンパ装置１１は、フランジ１４（出力側回転部材の一例）と、それぞれ複数の外周側トーションスプリング１５及び内周側トーションスプリング１６と、出力プレート１７と、を有している。 The power transmission device 1 includes an input plate 10 (an example of an input-side rotating member), a damper device 11, and a plurality of torsion springs 12 (an example of an urging member). The damper device 11 includes a flange 14 (an example of an output side rotating member), a plurality of outer peripheral side torsion springs 15 and inner peripheral side torsion springs 16, and an output plate 17.
　［入力プレート１０］
　入力プレート１０は、第２ケース６の内側の側面において、外周部に溶接により固定されている。入力プレート１０は、環状で円板状の固定部１０ａと、固定部１０ａの外周端の一部をエンジン側に折り曲げて形成された複数の爪１０ｂ（第１係合部）と、を有している。固定部１０ａの内周端部が、前述のように、第２ケース６の内側の側面に固定されている。固定部１０ａには、円周方向に所定の間隔で複数の取付孔１０ｃが形成されている。 [Input plate 10]
The input plate 10 is fixed to the outer peripheral portion by welding on the inner side surface of the second case 6. The input plate 10 includes an annular and disk-shaped fixing portion 10a, and a plurality of claws 10b (first engaging portions) formed by bending a part of the outer peripheral end of the fixing portion 10a toward the engine side. ing. The inner peripheral end portion of the fixed portion 10a is fixed to the inner side surface of the second case 6 as described above. A plurality of mounting holes 10c are formed in the fixed portion 10a at predetermined intervals in the circumferential direction.
　なお、図２に、図１の入力プレート１０及びフランジ１４の外周部を、トランスミッション側から視た図を示している。 FIG. 2 shows a view of the outer periphery of the input plate 10 and the flange 14 of FIG. 1 as viewed from the transmission side.
　［フランジ１４］
　フランジ１４は、円板状のプレートであり、入力プレート１０（正確には入力プレート１０の固定部１０ａ）と軸方向に並べて配置されている。すなわち、フランジ１４と入力プレート１０とは軸方向の異なる位置に配置されている。フランジ１４は、図２に示すように、複数の爪受け部１４ａと、それぞれ複数の外周側収容部１４ｂ及び内周側収容部１４ｃと、を有している。また、複数の爪受け部１４ａの円周方向間には、複数の取付孔１４ｄが形成されている。 [Flange 14]
The flange 14 is a disk-shaped plate, and is arranged side by side with the input plate 10 (more precisely, the fixed portion 10a of the input plate 10) in the axial direction. That is, the flange 14 and the input plate 10 are arranged at different positions in the axial direction. As shown in FIG. 2, the flange 14 has a plurality of claw receiving portions 14 a and a plurality of outer peripheral side accommodating portions 14 b and inner peripheral side accommodating portions 14 c, respectively. A plurality of mounting holes 14d are formed between the circumferential directions of the plurality of claw receiving portions 14a.
　複数の爪受け部１４ａは、外周端から径方向外方に突出し、入力プレート１０の爪１０ｂに対応する位置に形成されている。爪受け部１４ａには、円周方向に所定の幅を有し、外周側が開放する溝１４ｅ（第２係合部）が形成されている。この溝１４ｅに入力プレート１０の爪１０ｂが挿入されている。溝１４ｅ内の中央部に爪１０ｂが位置した場合、爪１０ｂと溝１４ｅとの間には両側に隙間δが確保される。 The plurality of claw receiving portions 14 a protrude radially outward from the outer peripheral end and are formed at positions corresponding to the claw 10 b of the input plate 10. The claw receiving portion 14a is formed with a groove 14e (second engaging portion) having a predetermined width in the circumferential direction and opened on the outer peripheral side. The claw 10b of the input plate 10 is inserted into the groove 14e. When the claw 10b is located at the center in the groove 14e, a gap δ is secured on both sides between the claw 10b and the groove 14e.
　［ねじりばね１２］
　ねじりばね１２は、コイル部１２ａと、第１アーム１２ｂと、第２アーム１２ｃと、を有している。第１アーム１２ｂは、コイル部１２ａの一端から内周側に延び、先端が軸方向のトランスミッション側に折り曲げられている。そして、その折り曲げ部が入力プレート１０の取付孔１０ｃに挿入されている。第２アーム１２ｃは、コイル部１２ａの他端から内周側に延び、先端が軸方向のエンジン側に折り曲げられている。そして、その折り曲げ部がフランジ１４の取付孔１４ｄに挿入されている。 [Torsion spring 12]
The torsion spring 12 has a coil portion 12a, a first arm 12b, and a second arm 12c. The first arm 12b extends from one end of the coil portion 12a to the inner peripheral side, and the tip is bent toward the transmission side in the axial direction. The bent portion is inserted into the mounting hole 10 c of the input plate 10. The second arm 12c extends from the other end of the coil portion 12a to the inner peripheral side, and the tip is bent toward the engine side in the axial direction. The bent portion is inserted into the mounting hole 14 d of the flange 14.
　この実施形態では、本装置にトルクが入力されていない状態において、爪１０ｂの両側と溝１４ｅとの間にそれぞれ隙間δが確保されるようにねじりばね１２及び各部材が設計されている。 In this embodiment, the torsion spring 12 and each member are designed so that a gap δ is secured between both sides of the claw 10b and the groove 14e in a state where no torque is input to the apparatus.
　［出力プレート１７］
　出力プレート１７は、軸方向に対向して配置された第１プレート２１及び第２プレート２２を有している。なお、第１プレート２１及び第２プレート２２は、内周部がリベット２３によってハブ２４の外周部に固定されている。したがって、第１プレート２１及び第２プレート２２は軸方向に移動不能であり、相対回転不能である。また、第１プレート２１及び第２プレート２２には、それぞれ複数の外周側開口部２１ａ，２２ａ及び内周側開口部２１ｂ，２２ｂが円周方向に並べて形成されている。各開口部２１ａ，２２ａ，２１ｂ，２２ｂはフランジ１４の外周側収容部１４ｂ及び内周側収容部１４ｃに対応する位置に配置されている。 [Output plate 17]
The output plate 17 includes a first plate 21 and a second plate 22 that are arranged to face each other in the axial direction. Note that the inner periphery of the first plate 21 and the second plate 22 is fixed to the outer periphery of the hub 24 by rivets 23. Accordingly, the first plate 21 and the second plate 22 are not movable in the axial direction and are not relatively rotatable. The first plate 21 and the second plate 22 are formed with a plurality of outer peripheral side openings 21a, 22a and inner peripheral side openings 21b, 22b arranged in the circumferential direction, respectively. Each opening part 21a, 22a, 21b, 22b is arrange | positioned in the position corresponding to the outer peripheral side accommodating part 14b of the flange 14, and the inner peripheral side accommodating part 14c.
　［外周側及び内周側トーションスプリング１５，１６］
　外周側トーションスプリング１５は、フランジ１４の外周側収容部１４ｂに収容され、出力プレート１７の外周側開口部２１ａ，２２ａによって軸方向及び径方向に支持されている。また、内周側トーションスプリング１６は、フランジ１４の内周側収容部１４ｃに収容され、出力プレート１７の内周側開口部２１ｂ，２２ｂによって軸方向及び径方向位支持されている。これらのトーションスプリング１５，１６によって、フランジ１４と出力プレート１７とは回転方向に弾性的に連結されている。 [Outer and inner torsion springs 15, 16]
The outer peripheral side torsion spring 15 is accommodated in the outer peripheral side accommodating portion 14 b of the flange 14, and is supported in the axial direction and the radial direction by the outer peripheral side openings 21 a and 22 a of the output plate 17. Further, the inner peripheral side torsion spring 16 is accommodated in the inner peripheral side accommodating portion 14 c of the flange 14, and is supported axially and radially by the inner peripheral side openings 21 b and 22 b of the output plate 17. By these torsion springs 15 and 16, the flange 14 and the output plate 17 are elastically connected in the rotational direction.
　［動作］
　入力プレート１０にトルクが入力されていない状況では、図２に示すように、爪１０ｂの両端と溝１４ｅとの間には、ねじりばね１２の付勢力によって、それぞれ隙間δが確保されている。このような状態で入力プレート１０にトルクが入力されると、入力プレート１０は図２の＋Ｒ方向に回転する。入力されたトルクが小さい場合は、ねじりばね１２が弾性変形し、爪１０ｂは溝１４ｅの側面に当接しない。 [Operation]
In a situation where no torque is input to the input plate 10, gaps δ are secured between the ends of the claw 10b and the groove 14e by the urging force of the torsion spring 12, as shown in FIG. When torque is input to the input plate 10 in such a state, the input plate 10 rotates in the + R direction in FIG. When the input torque is small, the torsion spring 12 is elastically deformed, and the claw 10b does not contact the side surface of the groove 14e.
　一方、所定の大きさ以上のトルクが入力されると、ねじりばね１２の弾性変形量が大きくなり、爪１０ｂが溝１４ｅの側面に当接して、入力プレート１０からフランジ１４に直接トルクが入力される。フランジ１４に入力されたトルクは、外周側トーションスプリング１５及び内周側トーションスプリング１６を介して出力プレート１７に伝達され、ハブ２４を介してトランスミッションの入力軸３に出力される。 On the other hand, when a torque of a predetermined magnitude or more is input, the amount of elastic deformation of the torsion spring 12 increases, the claw 10b comes into contact with the side surface of the groove 14e, and the torque is directly input from the input plate 10 to the flange 14. The Torque input to the flange 14 is transmitted to the output plate 17 via the outer peripheral side torsion spring 15 and the inner peripheral side torsion spring 16, and is output to the transmission input shaft 3 via the hub 24.
　ここでは、爪１０ｂと溝１４ｅの側面との間には隙間が存在するが、両者が接触するまでねじりばね１２の付勢力が抵抗になるので、両者が接触する際の衝撃が緩和される。このため、歯打ち音を抑えることができる。 Here, although there is a gap between the claw 10b and the side surface of the groove 14e, the urging force of the torsion spring 12 becomes resistance until they come into contact with each other, so that the impact when they come into contact is alleviated. For this reason, rattling noise can be suppressed.
　また、この装置では、爪１０ｂが溝１４ｅの側面に当接するまでは、ねじりばね１２によって低い剛性の捩り特性を得ることができる。このため、外周側及び内周側トーションスプリング１５，１６による比較的高い剛性の捩り特性に加えて、低い剛性の捩り特性を得ることができ、捩り特性の多段化を実現できる。 Moreover, in this apparatus, until the claw 10b comes into contact with the side surface of the groove 14e, the torsion spring 12 can obtain a low rigidity torsion characteristic. For this reason, in addition to the relatively high rigidity torsional characteristics by the outer peripheral side and inner peripheral side torsion springs 15, 16, low rigidity torsional characteristics can be obtained, and multi-stage torsional characteristics can be realized.
　［第１実施形態の変形例］
　（ａ）前記実施形態では、トルクが入力されていない状態で、爪１０ｂの両側と溝１４ｅの側面との間に同じ隙間δが確保されるように設定したが、例えば、爪１０ｂの一方の端面が対応する溝１４ｅの側面に当接するように設定してもよい。 [Modification of First Embodiment]
(A) In the above-described embodiment, the same gap δ is set between both sides of the claw 10b and the side surface of the groove 14e in a state where no torque is input. You may set so that an end surface may contact | abut to the side surface of the corresponding groove | channel 14e.
　（ｂ）ねじりばね１２の配置は前記実施形態に限定されない。例えば、図３及びその側面図である図４に示すように、入力プレート１０’及びフランジ１４’の内周側に配置してもよい。この例では、入力プレート１０’の爪１０ｂ’がフランジ１４’の外周面に形成された溝１４ａ’に係合している。そして、ねじりばね１２’は、コイル部１２ａ’から第１アーム１２ｂ’及び第２アーム１２ｃ’が外周側に延び、その先端が、それぞれ入力プレート１０’及びフランジ１４’に形成された取付孔に取り付けられている。 (B) The arrangement of the torsion spring 12 is not limited to the above embodiment. For example, as shown in FIG. 3 and FIG. 4 which is a side view thereof, they may be arranged on the inner peripheral side of the input plate 10 ′ and the flange 14 ′. In this example, the claw 10b 'of the input plate 10' is engaged with a groove 14a 'formed on the outer peripheral surface of the flange 14'. The torsion spring 12 ′ has a first arm 12 b ′ and a second arm 12 c ′ extending from the coil portion 12 a ′ to the outer peripheral side, and tip ends thereof in attachment holes formed in the input plate 10 ′ and the flange 14 ′, respectively. It is attached.
　－第２実施形態－
　［構成］
　図５に第２実施形態を示している。この第２実施形態は、入力プレート３０、フランジ３１及びねじりばね３２の構成が第１実施形態と異なるのみで、他の構成は同じである。したがって、図３では、異なる部分のみを示している。なお、図５（ａ）（ｂ）はともに正面部分図であり、同図（ａ）はねじりばね３２が装着されている部分を、同図（ｂ）は入力プレート３０の爪３０ｂとフランジ３１の溝３１ａとの係合部を示している。また、同図（ｃ）は同図（ａ）の側面図である。 -Second Embodiment-
[Constitution]
FIG. 5 shows a second embodiment. The second embodiment is the same as the first embodiment except for the configuration of the input plate 30, the flange 31, and the torsion spring 32. Therefore, in FIG. 3, only a different part is shown. 5A and 5B are front partial views, FIG. 5A shows a portion where the torsion spring 32 is mounted, and FIG. 5B shows a claw 30b and a flange 31 of the input plate 30. FIG. The engaging part with the groove | channel 31a is shown. FIG. 2C is a side view of FIG.
　入力プレート３０は、第１実施形態と同様に、第１ケースの内側の側面において、外周部に溶接により固定されている。入力プレート３０は、環状で円板状に形成されており、図５（ａ）（ｂ）に示すように、複数の突出部３０ａと、複数の爪３０ｂと、を有している。複数の突出部３０ａは、入力プレート３０の外周面から径方向外方に突出して形成されており、円周方向に所定の間隔で配置されている。この突出部３０ａには、円周方向の両端部に、１対のピン３４が軸方向に沿って延びるように装着されている。複数の爪３０ｂは、入力プレート１０の外周端の一部をエンジン側に折り曲げて形成され、軸方向に延びている。 As in the first embodiment, the input plate 30 is fixed to the outer peripheral portion by welding on the inner side surface of the first case. The input plate 30 is formed in an annular disk shape, and has a plurality of protrusions 30a and a plurality of claws 30b as shown in FIGS. The plurality of protrusions 30a are formed to protrude radially outward from the outer peripheral surface of the input plate 30, and are arranged at predetermined intervals in the circumferential direction. A pair of pins 34 are attached to the projecting portions 30a at both ends in the circumferential direction so as to extend along the axial direction. The plurality of claws 30b are formed by bending a part of the outer peripheral end of the input plate 10 to the engine side, and extend in the axial direction.
　フランジ３１は、円板状のプレートであり、入力プレート３０と軸方向に並べて配置されている。フランジ３１の外周端には、内周側に所定の深さを有し、外周側に開放する複数の溝３１ａが形成されている。この複数の溝３１ａには、入力プレート３０の爪３０ｂが挿入されている（図５（ｂ）参照）。溝３１ａ内の中央部に爪３０ｂが位置した場合、爪３０ｂと溝３１ａとの間には両側に隙間δが確保される。 The flange 31 is a disk-shaped plate, and is arranged side by side with the input plate 30 in the axial direction. A plurality of grooves 31 a having a predetermined depth on the inner peripheral side and open to the outer peripheral side are formed at the outer peripheral end of the flange 31. Claws 30b of the input plate 30 are inserted into the plurality of grooves 31a (see FIG. 5B). When the claw 30b is positioned at the center in the groove 31a, a gap δ is secured on both sides between the claw 30b and the groove 31a.
　ねじりばね３２は、フランジ３１の複数の溝３１ａのうちの例えば４個の溝に対応する位置に配置されている。そして、残りの溝に、入力プレート３０の爪３０ｂが挿入されている。ねじりばね３２は、第１コイル部３２ａ及び第２コイル部３２ｂと、連結部３２ｃと、第１アーム３２ｄ及び第２アーム３２ｅと、を有している。第１コイル部３２ａは入力プレート３０の突出部３０ａに装着された一方のピン３４に支持されている。また、第２コイル部３２ｂは他方のピン３４に支持されている。連結部３２ｃは、円周方向に延び、第１コイル部３２ａの一端と第２コイル部３２ｂの一端との間を連結している。第１アーム３２ｄは、第１コイル部３２ａの他端から内周側に延びている。そして、第１アーム３２ｄの先端部は、フランジ３１の溝３１ａの一方の側面に当接している。第２アーム３２ｅは、第２コイル部３２ｂの他端から内周側に延び、先端部は、フランジ３１の溝３１ａの他方の側面に当接している。 The torsion spring 32 is disposed at a position corresponding to, for example, four grooves among the plurality of grooves 31 a of the flange 31. And the nail | claw 30b of the input plate 30 is inserted in the remaining groove | channel. The torsion spring 32 includes a first coil portion 32a and a second coil portion 32b, a connecting portion 32c, and a first arm 32d and a second arm 32e. The first coil portion 32 a is supported by one pin 34 attached to the protruding portion 30 a of the input plate 30. The second coil portion 32b is supported by the other pin 34. The connecting part 32c extends in the circumferential direction, and connects between one end of the first coil part 32a and one end of the second coil part 32b. The first arm 32d extends from the other end of the first coil portion 32a to the inner peripheral side. The distal end portion of the first arm 32 d is in contact with one side surface of the groove 31 a of the flange 31. The second arm 32 e extends from the other end of the second coil portion 32 b to the inner peripheral side, and the tip end is in contact with the other side surface of the groove 31 a of the flange 31.
　この実施形態では、本装置にトルクが入力されていない状態において、爪３０ｂの両側と溝３１ａとの間にそれぞれ隙間δが確保されるようにねじりばね３２及び各部材が設計されている。 In this embodiment, the torsion spring 32 and each member are designed so that a gap δ is secured between both sides of the claw 30b and the groove 31a in a state where no torque is input to the apparatus.
　［動作］
　この第２実施形態では、図６に示すように、ねじりばね３２が弾性変形した状態で第１アーム３２ｄ及び第２アーム３２ｅが溝にセットされている。すなわち、ねじりばね３２によって、入力プレート３０とフランジ３１との間に、両回転方向にプリトルクを与えた状態で、ねじりばね３２、入力プレート３０、及びフランジ３１がセットされている。 [Operation]
In the second embodiment, as shown in FIG. 6, the first arm 32d and the second arm 32e are set in the groove in a state where the torsion spring 32 is elastically deformed. That is, the torsion spring 32, the input plate 30, and the flange 31 are set with the pre-torque applied in both rotational directions between the input plate 30 and the flange 31 by the torsion spring 32.
　ここでは、入力プレート３０に入力されるトルクがプリトルクを越えるまでは、第１実施形態と同様に、爪３０ｂの両端と溝３１ａとの間にそれぞれ隙間δが確保される。そして、プリトルクを越えるトルクが入力されると、図７に示すように、ねじりばね３２の第１アーム３２ｄの弾性変形量が大きくなり、爪３０ｂの一方の端面が溝３１ａの側面に当接する。ここでは、爪３０ｂ及び溝３１ａの側面を介して、入力プレート３０からフランジ３１に直接トルクが入力される。フランジ３１に入力されたトルクは、前記同様に、外周側トーションスプリング１５及び内周側トーションスプリング１６を介して出力プレート１７に伝達され、ハブを介してトランスミッションの入力軸３に出力される。 Here, until the torque input to the input plate 30 exceeds the pre-torque, the gap δ is secured between both ends of the claw 30b and the groove 31a as in the first embodiment. When a torque exceeding the pre-torque is input, the amount of elastic deformation of the first arm 32d of the torsion spring 32 increases as shown in FIG. 7, and one end surface of the claw 30b comes into contact with the side surface of the groove 31a. Here, torque is directly input from the input plate 30 to the flange 31 via the claw 30b and the side surface of the groove 31a. As described above, the torque input to the flange 31 is transmitted to the output plate 17 via the outer peripheral side torsion spring 15 and the inner peripheral side torsion spring 16, and is output to the transmission input shaft 3 via the hub.
　ここでは、第１実施形態と同様に、爪３０ｂと溝３１ａの側面との間には隙間が存在するが、両者が接触するまでねじりばね３２の付勢力が抵抗になるので、両者が接触する際の衝撃が緩和される。このため、歯打ち音を抑えることができる。 Here, as in the first embodiment, there is a gap between the claw 30b and the side surface of the groove 31a, but the biasing force of the torsion spring 32 becomes resistance until they come into contact with each other. The impact is mitigated. For this reason, rattling noise can be suppressed.
　また、この装置では、爪３０ｂが溝３１ａの側面に当接するまでは、ねじりばね３２によって低い剛性の捩り特性を得ることができる。このため、外周側及び内周側トーションスプリング１５，１６による比較的高い剛性の捩り特性に加えて、低い剛性の捩り特性を得ることができ、捩り特性の多段化を実現できる。 Moreover, in this apparatus, until the claw 30b comes into contact with the side surface of the groove 31a, the torsion spring 32 can obtain a low rigidity torsion characteristic. For this reason, in addition to the relatively high rigidity torsional characteristics by the outer peripheral side and inner peripheral side torsion springs 15, 16, low rigidity torsional characteristics can be obtained, and multi-stage torsional characteristics can be realized.
　［第２実施形態の変形例］
　前記実施形態では、ねじりばね３２にプリトルクを与えて爪３０ｂの両側と溝３１ａの側面との間に同じ隙間δが確保されるように設定したが、例えば、爪３０ｂの一方の端面が対応する溝３１ａの側面に当接するように設定してもよい。 [Modification of Second Embodiment]
In the embodiment, the pre-torque is applied to the torsion spring 32 so that the same gap δ is secured between both sides of the claw 30b and the side surface of the groove 31a. For example, one end face of the claw 30b corresponds. You may set so that it may contact | abut on the side surface of the groove | channel 31a.
　－第３実施形態－
　前記第１及び第２実施形態では、入力プレートとフランジとが軸方向に並べて配置された例を示したが、入力プレートとフランジとが軸方向の同じ位置で径方向に並べて配置されている場合の第３実施形態を図８に示す。 -Third embodiment-
In the first and second embodiments, the input plate and the flange are arranged side by side in the axial direction. However, the input plate and the flange are arranged in the radial direction at the same position in the axial direction. FIG. 8 shows a third embodiment.
　この例では、外周側に入力プレート４０が配置され、その内周側で軸方向の同じ位置にフランジ４１が配置されている。入力プレート４０とフランジ４１とは、環状のプレート部材であり、相対回転が可能である。 In this example, the input plate 40 is disposed on the outer peripheral side, and the flange 41 is disposed at the same position in the axial direction on the inner peripheral side. The input plate 40 and the flange 41 are annular plate members and are capable of relative rotation.
　入力プレート４０の内周面には、径方向内方に突出する複数の爪４０ａが形成されている。一方、フランジ４１の外周面には、内周側に所定の深さを有し、外周側に開放する溝４１ａが形成されている。この溝４１ａに爪４０ａが挿入されている。 A plurality of claws 40a projecting radially inward are formed on the inner peripheral surface of the input plate 40. On the other hand, on the outer peripheral surface of the flange 41, a groove 41a having a predetermined depth on the inner peripheral side and opening on the outer peripheral side is formed. A claw 40a is inserted into the groove 41a.
　ねじりばね４２は、コイル部４２ａと、第１アーム４２ｂと、第２アーム４２ｃと、を有している。コイル部４２ａは、フランジ４１の側面に固定されたピン４３に装着されて支持されている。第１アーム４２ｂは、コイル部４２ａの一端から外周側に延び、先端が軸方向トランスミッション側に折り曲げられている。そして、その折り曲げ部が入力プレート４０の取付孔に挿入されている。また、第２アーム４２ｃは、コイル部４２ａの他端から横方向に延び、先端が軸方向のエンジン側に折り曲げられている。そして、その折り曲げ部がフランジ４１の取付孔に挿入されている。 The torsion spring 42 has a coil portion 42a, a first arm 42b, and a second arm 42c. The coil portion 42 a is attached to and supported by a pin 43 fixed to the side surface of the flange 41. The first arm 42b extends from one end of the coil portion 42a to the outer peripheral side, and the tip is bent toward the axial transmission side. The bent portion is inserted into the mounting hole of the input plate 40. The second arm 42c extends in the lateral direction from the other end of the coil portion 42a, and the tip is bent toward the engine side in the axial direction. The bent portion is inserted into the mounting hole of the flange 41.
　第３実施形態では、第１実施形態と同様に、本装置にトルクが入力されていない状態において、爪４０ａの両側と溝４１ａとの間にそれぞれ隙間が確保されるようにねじりばね４２及び各部材が設計されている。 In the third embodiment, as in the first embodiment, the torsion spring 42 and each of the torsion springs 42 and each of the grooves 41a are secured so that a gap is secured between both sides of the claw 40a and the groove 41a in a state where no torque is input to the apparatus. The member is designed.
　この第３実施形態においても、第１及び第２実施形態と同様の作用効果を得ることができる。 In the third embodiment, the same effects as those of the first and second embodiments can be obtained.
　－第４実施形態－
　図９に第４実施形態を示す。この第４実施形態は、第３実施形態と同様に、入力プレート５０とフランジ５１とが軸方向の同じ位置で径方向に並べて配置されている。そして、外周側に入力プレート５０が配置され、その内周側で軸方向の同じ位置にフランジ５１が配置されている。入力プレート５０とフランジ５１とは、環状のプレート部材であり、相対回転が可能である。 -Fourth embodiment-
FIG. 9 shows a fourth embodiment. In the fourth embodiment, as in the third embodiment, the input plate 50 and the flange 51 are arranged in the radial direction at the same position in the axial direction. And the input plate 50 is arrange | positioned on the outer peripheral side, and the flange 51 is arrange | positioned in the same position of an axial direction on the inner peripheral side. The input plate 50 and the flange 51 are annular plate members and are capable of relative rotation.
　入力プレート５０の内周面には、径方向内方に突出する複数の爪５０ａが形成されている。一方、フランジ５１の外周面には、内周側に所定の深さを有し、外周側に開放するそれぞれ複数の第１溝５１ａと第２溝５１ｂとが形成されている。そして、第１溝５１ａに爪５０ａが挿入されている。また、第２溝５１ｂは第１溝５１ａよりも円周方向の幅が広く、後述するねじりばね５２の第１アーム５２ｂ及び第２アーム５２ｃが挿入されている。 A plurality of claws 50 a projecting radially inward are formed on the inner peripheral surface of the input plate 50. On the other hand, on the outer peripheral surface of the flange 51, a plurality of first grooves 51a and second grooves 51b having a predetermined depth on the inner peripheral side and opened to the outer peripheral side are formed. And the nail | claw 50a is inserted in the 1st groove | channel 51a. The second groove 51b is wider in the circumferential direction than the first groove 51a, and a first arm 52b and a second arm 52c of a torsion spring 52 described later are inserted therein.
　ねじりばね５２は、フランジ５１の第２溝５１ｂに対応する位置に配置されている。ねじりばね５２は、本体部５２ａと、第１アーム５２ｂと、第２アーム５２ｃと、を有している。本体部５２ａは概略Ｖ字状に形成されており、３つのピン５３ａ，５３ｂ，５３ｃに支持されている。より詳細には、３つのピン５３ａ～５３ｃは所定の間隔で円周方向に並べて配置されている。そして、本体部５２ａの両端部はピン５３ａ，５３ｃの外周側に支持され、本体部５２ａの中央部はピン５３ｂの内周側に支持されている。第１アーム５２ｂは、本体部５２ａの一端から内周側に延びている。そして、第１アーム５２ｂの先端部は、フランジ５１の第２溝５１ｂの一方の側面に当接している。第２アーム５２ｃは、本体部５２ａの他端から内周側に延び、先端部は、フランジ５１の第２溝５１ｂの他方の側面に当接している。 The torsion spring 52 is disposed at a position corresponding to the second groove 51 b of the flange 51. The torsion spring 52 has a main body 52a, a first arm 52b, and a second arm 52c. The main body 52a is substantially V-shaped and is supported by three pins 53a, 53b, 53c. More specifically, the three pins 53a to 53c are arranged side by side in the circumferential direction at a predetermined interval. Both end portions of the main body portion 52a are supported on the outer peripheral side of the pins 53a and 53c, and the central portion of the main body portion 52a is supported on the inner peripheral side of the pin 53b. The first arm 52b extends from one end of the main body 52a to the inner peripheral side. The distal end portion of the first arm 52b is in contact with one side surface of the second groove 51b of the flange 51. The second arm 52 c extends from the other end of the main body portion 52 a to the inner peripheral side, and the tip end is in contact with the other side surface of the second groove 51 b of the flange 51.
　第４実施形態では、本装置にトルクが入力されていない状態において、爪５０ａの両側と第１溝５１ａとの間にそれぞれ隙間が確保されるようにねじりばね５２及び各部材が設計されている。 In the fourth embodiment, the torsion spring 52 and each member are designed such that a gap is secured between both sides of the claw 50a and the first groove 51a in a state where no torque is input to the apparatus. .
　この第４実施形態においても、第１及び第２実施形態と同様の作用効果を得ることができる。 In the fourth embodiment, the same effects as those in the first and second embodiments can be obtained.
　［他の実施形態］
　本発明は以上のような実施形態に限定されるものではなく、本発明の範囲を逸脱することなく種々の変形又は修正が可能である。 [Other Embodiments]
The present invention is not limited to the above-described embodiments, and various changes or modifications can be made without departing from the scope of the present invention.
　第１及び第２実施形態では、付勢部材としてねじりばねを用いたが、他の形態の付勢部材を用いてもよい。 In the first and second embodiments, the torsion spring is used as the urging member, but another form of urging member may be used.
　本発明の動力伝達装置では、動力伝達時の歯打ち音を、簡単な構成で抑制することができる。 In the power transmission device of the present invention, rattling noise during power transmission can be suppressed with a simple configuration.
１　動力伝達装置
１０，３０，４０，５０　入力プレート１０（入力側回転部材）
１０ｂ，１０ｂ'，３０ｂ，４０ａ，５０ａ　爪（第１係合部）
１２，１２'，３２，４２，５２　ねじりばね（付勢部材）
１２ａ，１２ａ'，４２ａ　コイル部
１２ｂ，１２ｂ'，３２ｄ，４２ｂ，５２ｂ　第１アーム
１２ｃ、１２ｃ'，３２ｅ，４２ｃ，５２ｃ　第２アーム
１４，１４'，３１，４１，５１　フランジ（出力側回転部材）
１４ｅ，３１ａ，４１ａ　溝（第２係合部）
３２ａ　第１コイル部
３２ｂ　第２コイル部
３４，４３　ピン（支持部材）
５１ａ　第１溝（第２係合部） 1 Power transmission device 10, 30, 40, 50 Input plate 10 (input side rotating member)
10b, 10b ', 30b, 40a, 50a Claw (first engaging portion)
12, 12 ', 32, 42, 52 Torsion spring (biasing member)
12a, 12a ', 42a Coil portions 12b, 12b', 32d, 42b, 52b First arm 12c, 12c ', 32e, 42c, 52c Second arm 14, 14', 31, 41, 51 Flange (output side rotating member )
14e, 31a, 41a Groove (second engaging portion)
32a 1st coil part 32b 2nd coil part 34,43 pin (support member)
51a 1st groove | channel (2nd engaging part)

Claims (5)

  1. 　入力側の部材から出力側の部材にトルクを伝達する動力伝達装置であって、
    　第１係合部を有し、前記入力側の部材からトルクが入力される入力側回転部材と、
    　前記第１係合部に対して回転方向に所定の隙間を介して係合可能な第２係合部を有し、前記入力側回転部材と軸方向に並べて配置され、前記出力側の部材にトルクを出力する出力側回転部材と、
    　前記入力側回転部材と前記出力側回転部材との間に配置され、前記第１係合部と前記第２係合部との間の隙間以上の弾性変形が可能であり、前記入力側回転部材及び前記出力側回転部材の少なくとも一方を回転方向に付勢する付勢部材と、
    を備えた動力伝達装置。     A power transmission device that transmits torque from an input-side member to an output-side member,
    An input-side rotating member having a first engaging portion and receiving torque from the input-side member;
    A second engaging portion that can be engaged with the first engaging portion in a rotational direction through a predetermined gap, and is arranged side by side in the axial direction with the input-side rotating member; An output-side rotating member that outputs torque;
    The input-side rotation member is disposed between the input-side rotation member and the output-side rotation member, and can be elastically deformed more than a gap between the first engagement portion and the second engagement portion, And an urging member that urges at least one of the output side rotation members in the rotation direction;
    Power transmission device with
  2. 　前記付勢部材はねじりばねであり、
    　前記ねじりばねは、
    　コイル部と、
    　前記コイル部の一端から延びるとともに先端部が前記入力側回転部材に係合する第１アームと、
    　前記コイル部の他端から延びるとともに先端部が前記出力側回転部材に係合する第２アームと、
    を有する、
    請求項１に記載の動力伝達装置。     The biasing member is a torsion spring;
    The torsion spring is
    A coil section;
    A first arm extending from one end of the coil portion and having a tip portion engaged with the input side rotation member;
    A second arm extending from the other end of the coil portion and having a tip portion engaged with the output side rotation member;
    Having
    The power transmission device according to claim 1.
  3. 　前記入力側回転部材及び前記出力側回転部材の一方に円周方向に所定の間隔をあけて配置された第１支持部材及び第２支持部材をさらに備え、
    　前記付勢部材はねじりばねであり、
    　前記ねじりばねは、
    　前記第１支持部材に支持された第１コイル部と、
    　前記第２支持部材に支持された第２コイル部と、
    　前記第１コイル部の一端と前記第２コイル部の一端との間に延びる連結部と、
    　前記第１コイル部の他端から延びるとともに先端部が前記入力側回転部材及び前記出力側回転部材の他方に係合する第１アームと、
    　前記第２コイル部の他端から延びるとともに先端部が前記入力側部材及び前記出力側回転部材の他方に係合する第２アームと、
    を有する、
    請求項１に記載の動力伝達装置。     A first support member and a second support member disposed at a predetermined interval in the circumferential direction on one of the input side rotation member and the output side rotation member;
    The biasing member is a torsion spring;
    The torsion spring is
    A first coil portion supported by the first support member;
    A second coil portion supported by the second support member;
    A connecting portion extending between one end of the first coil portion and one end of the second coil portion;
    A first arm extending from the other end of the first coil portion and having a tip end engaged with the other of the input side rotating member and the output side rotating member;
    A second arm extending from the other end of the second coil portion and having a tip portion engaged with the other of the input side member and the output side rotation member;
    Having
    The power transmission device according to claim 1.
  4. 　前記第１係合部及び前記第２係合部の一方は、軸方向に延び、円周方向に第１幅を有する、係合爪であり、
    　前記第１係合部及び前記第２係合部の他方は、前記係合爪が挿入され、円周方向に第２幅を有する係合溝である、
    請求項１から３のいずれかに記載の動力伝達装置。     One of the first engagement portion and the second engagement portion is an engagement claw that extends in the axial direction and has a first width in the circumferential direction,
    The other of the first engaging portion and the second engaging portion is an engaging groove into which the engaging claw is inserted and having a second width in the circumferential direction.
    The power transmission device according to any one of claims 1 to 3.
  5. 　入力側の部材から出力側の部材にトルクを伝達する動力伝達装置であって、
    　第１係合部を有し、前記入力側の部材からトルクが入力される入力側回転部材と、
    　前記第１係合部に対して回転方向に所定の隙間を介して係合可能な第２係合部を有し、前記出力側の部材にトルクを出力する出力側回転部材と、
    　前記入力側回転部材と前記出力側回転部材との間に配置され、前記第１係合部と前記第２係合部との間の隙間以上の弾性変形が可能であり、前記入力側回転部材及び前記出力側回転部材の少なくとも一方を回転方向に付勢するねじりばねと、
    を備えた動力伝達装置。     A power transmission device that transmits torque from an input-side member to an output-side member,
    An input-side rotating member having a first engaging portion and receiving torque from the input-side member;
    An output-side rotation member that has a second engagement portion that can be engaged with the first engagement portion in a rotation direction through a predetermined gap, and that outputs torque to the output-side member;
    The input-side rotation member is disposed between the input-side rotation member and the output-side rotation member, and can be elastically deformed more than a gap between the first engagement portion and the second engagement portion, And a torsion spring that urges at least one of the output side rotation members in the rotation direction;
    Power transmission device with
PCT/JP2017/028363 2016-09-09 2017-08-04 Power transmission device WO2018047546A1 (en)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
JP2016-176629 2016-09-09
JP2016176629A JP6703920B2 (en) 2016-09-09 2016-09-09 Power transmission device

Publications (1)

Publication Number Publication Date
WO2018047546A1 true WO2018047546A1 (en) 2018-03-15

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WO (1) WO2018047546A1 (en)

Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS58193966A (en) * 1982-05-06 1983-11-11 Nissan Motor Co Ltd Lock-up torque converter
JPS61186842U (en) * 1985-05-14 1986-11-21
US20120102936A1 (en) * 2010-10-29 2012-05-03 Schaeffler Technologies Gmbh & Co. Kg Torsion spring damper
WO2016128260A1 (en) * 2015-02-10 2016-08-18 Federntechnik Knörzer GmbH Torsion spring and torsional vibration damper

Patent Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS58193966A (en) * 1982-05-06 1983-11-11 Nissan Motor Co Ltd Lock-up torque converter
JPS61186842U (en) * 1985-05-14 1986-11-21
US20120102936A1 (en) * 2010-10-29 2012-05-03 Schaeffler Technologies Gmbh & Co. Kg Torsion spring damper
WO2016128260A1 (en) * 2015-02-10 2016-08-18 Federntechnik Knörzer GmbH Torsion spring and torsional vibration damper

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JP2018040473A (en) 2018-03-15

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