WO2011070852A1 - トルクコンバータ - Google Patents

トルクコンバータ Download PDF

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Publication number
WO2011070852A1
WO2011070852A1 PCT/JP2010/068125 JP2010068125W WO2011070852A1 WO 2011070852 A1 WO2011070852 A1 WO 2011070852A1 JP 2010068125 W JP2010068125 W JP 2010068125W WO 2011070852 A1 WO2011070852 A1 WO 2011070852A1
Authority
WO
WIPO (PCT)
Prior art keywords
outer peripheral
peripheral side
torque converter
torsion spring
torsion springs
Prior art date
Application number
PCT/JP2010/068125
Other languages
English (en)
French (fr)
Japanese (ja)
Inventor
裕樹 河原
Original Assignee
株式会社エクセディ
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 株式会社エクセディ filed Critical 株式会社エクセディ
Priority to US13/514,722 priority Critical patent/US9702445B2/en
Priority to CN2010800549822A priority patent/CN102639904A/zh
Priority to KR1020127014577A priority patent/KR20120085889A/ko
Priority to DE112010004737T priority patent/DE112010004737T5/de
Publication of WO2011070852A1 publication Critical patent/WO2011070852A1/ja

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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
    • 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
    • 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
    • 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
    • F16H2045/0205—Combinations of fluid gearings for conveying rotary motion with couplings or clutches with mechanical clutches for bridging a fluid gearing of the hydrokinetic type two chamber system, i.e. without a separated, closed chamber specially adapted for actuating a lock-up clutch
    • 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
    • F16H2045/0221—Combinations of fluid gearings for conveying rotary motion with couplings or clutches with mechanical clutches for bridging a fluid gearing of the hydrokinetic type with damping means
    • F16H2045/0226—Combinations of fluid gearings for conveying rotary motion with couplings or clutches with mechanical clutches for bridging a fluid gearing of the hydrokinetic type with damping means comprising two or more vibration dampers
    • 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
    • F16H2045/0221—Combinations of fluid gearings for conveying rotary motion with couplings or clutches with mechanical clutches for bridging a fluid gearing of the hydrokinetic type with damping means
    • F16H2045/0226—Combinations of fluid gearings for conveying rotary motion with couplings or clutches with mechanical clutches for bridging a fluid gearing of the hydrokinetic type with damping means comprising two or more vibration dampers
    • F16H2045/0231—Combinations of fluid gearings for conveying rotary motion with couplings or clutches with mechanical clutches for bridging a fluid gearing of the hydrokinetic type with damping means comprising two or more vibration dampers arranged in series
    • 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
    • F16H2045/0273—Combinations of fluid gearings for conveying rotary motion with couplings or clutches with mechanical clutches for bridging a fluid gearing of the hydrokinetic type characterised by the type of the friction surface of the lock-up clutch
    • F16H2045/0294—Single disk type lock-up clutch, i.e. using a single disc engaged between friction members

Definitions

  • the present invention relates to a torque converter, and more particularly to a torque converter including a lockup device having a plurality of torsion springs on the outer periphery and the inner periphery.
  • the torque converter is often provided with a lock-up device for transmitting torque directly from the front cover to the turbine.
  • the lock-up device includes a piston that can be frictionally connected to the front cover, a drive plate fixed to the piston, a plurality of torsion springs supported by the drive plate, and a plurality of torsion springs that elastically rotate the piston in the rotational direction. And a driven plate to be connected. The driven plate is fixed to the turbine.
  • the piston divides the space between the front cover and the turbine in the axial direction, and can move in the axial direction due to the hydraulic pressure difference on both sides in the axial direction.
  • Patent Document 1 a device has already been proposed in which a torsion spring is disposed on each of an outer peripheral portion and an inner peripheral portion, and an outer peripheral side torsion spring and an inner peripheral side torsion spring are connected by an intermediate member. Yes.
  • Patent Document 2 a configuration as shown in Patent Document 2 has been proposed in order to reduce the dimension in the axial direction.
  • the torus is reduced in size and flattened to shorten the axial direction.
  • Patent Document 1 has a long axial dimension in order to avoid interference between the inner torsion spring and the turbine, and cannot be made compact. Further, in order to shorten the axial dimension with the configuration shown in Patent Document 1, the coil diameter of the torsion spring becomes small, and good damper characteristics cannot be obtained.
  • An object of the present invention is to make the axial space compact and to further widen the damper twisting angle in the lock-up device to further improve the damper characteristics.
  • a torque converter is a torque converter that transmits torque input from a front cover to a member on a transmission side, and includes a torque converter body having an impeller, a turbine, and a stator, and a lockup device.
  • the lockup device is a device for mechanically connecting the front cover and the turbine, and includes a plurality of outer peripheral torsion springs and a plurality of inner peripheral torsion springs. The plurality of outer peripheral torsion springs are arranged side by side in the circumferential direction with a first mounting diameter.
  • the plurality of inner peripheral torsion springs are arranged in the circumferential direction with the second mounting diameter on the inner peripheral side of the plurality of outer peripheral torsion springs, and act in series with the outer peripheral torsion springs.
  • the first mounting diameter is equal to or larger than the outer diameter of the torus formed by each blade of the torque converter body, and the second mounting diameter is equal to or smaller than the inner diameter of the torus.
  • the outer peripheral side torsion spring is arranged on the outer peripheral side of the torus and the inner peripheral side torsion spring is arranged on the inner peripheral side of the torus, the torsion spring and the torque converter main body hardly interfere with each other, and the shaft of the entire apparatus The direction space can be made compact. Further, for the same reason, a torsion spring having a coil diameter larger than that of the conventional one can be used, so that a damper characteristic effective for vehicle vibration can be set.
  • the torsion angle can be widened, and a damper characteristic effective for vehicle vibration can be obtained.
  • the torque converter according to the second invention is the torque converter according to the first invention, wherein the portion of the turbine closest to the front cover is located closer to the front cover than the portion of the outer peripheral torsion spring and the inner peripheral torsion spring closest to the torque converter body. is doing.
  • the torsion spring and the torque converter main body are disposed so as to overlap in the axial direction, the axial dimension of the entire torque converter can be shortened.
  • the torque converter according to a third aspect of the present invention is the torque converter according to the first aspect of the present invention, further comprising a float member that is movable in the rotational direction and that causes at least two of the plurality of outer peripheral side torsion springs to act in series.
  • outer periphery side torsion spring and the inner periphery side torsion spring act in series, but also at least two of the plurality of outer periphery side torsion springs act in series by the float member, so that the twist angle is further widened. be able to.
  • a torque converter according to a fourth aspect of the invention is the torque converter of the third aspect, wherein the float member is provided so as to cover the outer peripheral portion of the outer peripheral side torsion spring.
  • the float member can prevent the outer periphery side torsion spring from protruding to the outer periphery side due to the centrifugal force. And when the outer peripheral side torsion spring expands and contracts, the outer peripheral part of the outer peripheral side torsion spring and the inner peripheral surface of the float member come into sliding contact with each other, but the float member is movable in the rotational direction. The sliding contact resistance is reduced, and the hysteresis torque can be reduced.
  • the axial space can be made compact, the damper twist angle in the lockup device can be made wider, and the damper characteristics can be improved.
  • FIG. 1 is a partial sectional view of a torque converter according to an embodiment of the present invention.
  • FIG. 1 is a partial sectional view of a torque converter 1 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.
  • FIG. 2 is a partial front view of the lockup device.
  • the torsion spring as an elastic member is omitted.
  • OO shown in FIG. 1 is a rotation axis of the torque converter and the lockup device.
  • the torque converter 1 is a device for transmitting torque from an engine-side crankshaft (not shown) to an input shaft of a transmission, and includes a front cover 2 fixed to an input-side member and three types of impellers ( A torque converter main body 6 including an impeller 3, a turbine 4, and a stator 5) and a lockup device 7 are included.
  • the front cover 2 is a disk-shaped member, and an outer peripheral cylindrical portion 10 protruding toward the axial transmission side is formed on the outer peripheral portion thereof.
  • the impeller 3 includes an impeller shell 12, a plurality of impeller blades 13, and a cylindrical impeller hub 14.
  • the impeller shell 12 is fixed to the outer peripheral cylindrical portion 10 of the front cover 2 by welding.
  • the plurality of impeller hubs 13 are fixed inside the impeller shell 12.
  • the impeller hub 14 is provided on the inner peripheral side of the impeller shell 12.
  • the turbine 4 is disposed to face the impeller 3 in the fluid chamber.
  • the turbine 4 includes a turbine shell 15, a plurality of turbine blades 16 fixed to the turbine shell 15, and a turbine hub 17 fixed to the inner peripheral side of the turbine shell 15.
  • the turbine hub 17 has a flange 17 a extending to the outer peripheral side, and an inner peripheral portion of the turbine shell 15 is fixed to the flange 17 a by a plurality of rivets 18.
  • An input shaft of a transmission (not shown) is splined to the inner peripheral portion of the turbine hub 17.
  • the stator 5 is a mechanism for rectifying the hydraulic oil that is disposed between the impeller 3 and the inner peripheral portion of the turbine 4 and returns from the turbine 4 to the impeller 3.
  • the stator 5 is mainly composed of a disk-shaped stator carrier 20 and a plurality of stator blades 21 provided on the outer peripheral surface thereof.
  • the stator carrier 20 is supported by a fixed shaft (not shown) via a one-way clutch 22.
  • a thrust washer 25 is provided between the front cover 2 and the turbine hub 16 in the axial direction, and a thrust washer is provided between the turbine hub 17 and the stator carrier 20 and between the stator carrier 20 and the impeller shell 12. Bearings 26 and 27 are provided.
  • the torus 6a filled with hydraulic oil is formed by the impeller blade 13, the turbine blade 16, and the stator blade 21.
  • the lockup device 7 is disposed in an annular space between the front cover 2 and the turbine 4.
  • the lock-up device 7 mainly includes a piston 30, a drive plate 31, a plurality of outer and inner torsion springs 32, 33, an outer torsion spring 32, and an inner torsion spring 33, respectively. And an intermediate plate 34 and a driven plate 35.
  • the piston 30 is a disk-shaped plate member, and is disposed so as to divide the space between the front cover 2 and the turbine 4 into two in the axial direction.
  • the outer peripheral portion of the piston 30 is a flat friction connecting portion 30a, and a friction facing 37 is provided on the axial direction engine side of the friction connecting portion 30a.
  • a flat friction surface is formed on the front cover 2 so as to face the friction facing 37.
  • an inner peripheral cylindrical portion 30 b extending toward the axial transmission side is provided on the inner peripheral edge of the piston 30.
  • the inner peripheral surface of the inner peripheral cylindrical portion 30 b is supported so as to be movable in the axial direction and the rotational direction with respect to the outer peripheral surface of the turbine hub 17.
  • the piston 30 is restricted from moving further toward the axial transmission side in a state where the tip of the inner peripheral cylindrical portion 30b is in contact with a part of the turbine hub 17.
  • a seal ring 38 is provided between the inner peripheral cylindrical portion 30 b and the outer peripheral surface of the turbine hub 17.
  • a space A is formed between the front cover 2 and the piston 30.
  • the outer peripheral portion of the space A is blocked with the friction facing 37 in contact with the front cover 2, and the inner peripheral portion of the space A is connected to an oil passage formed in the input shaft through a groove formed in the thrust washer 25. Communicate.
  • the drive plate 31 is an annular member made of sheet metal, and is disposed on the axial transmission side of the friction coupling portion 30 a in the piston 30.
  • An inner peripheral portion of the drive plate 31 is fixed to the piston 30 by a plurality of rivets 40.
  • a plurality of locking portions 31 a extending toward the axial transmission side are formed on the outer peripheral portion of the drive plate 31.
  • the plurality of locking portions 31 a are formed at predetermined intervals in the circumferential direction, and support the end surface of the outer peripheral side torsion spring 32.
  • a support portion 31 b extending toward the axial transmission side is formed above the piston mounting portion of the drive plate 31.
  • the inner peripheral side of the outer peripheral side torsion spring 32 is supported by the support portion 31b.
  • Each of the plurality of outer peripheral side torsion springs 32 includes a combination of a large coil spring and a small coil spring that is inserted into the large coil spring and shorter than the spring length of the large coil spring.
  • a total of eight outer peripheral side torsion springs 32 are arranged side by side in the rotation direction in two sets, and the float member 42 is arranged so that the two outer peripheral side torsion springs 32 of each set act in series.
  • the float member 42 is an annular member having a C-shaped cross section and is disposed above the support portion 31 b of the drive plate 31.
  • the float member 42 is disposed so as to be rotatable relative to the drive plate 31, and the outer peripheral portion supports the outer peripheral portion of the outer peripheral side torsion spring 32. That is, the float member 42 restricts the outer peripheral side torsion spring 32 from protruding to the outer peripheral side.
  • a front end portion 42 a of the float member 42 on the transmission side in the axial direction is bent on the inner peripheral side and the engine side. . That is, both end surfaces in the circumferential direction of the bent portion 42 a are in contact with the end surfaces of the corresponding torsion springs 32.
  • both ends in the circumferential direction of the pair of outer peripheral side torsion springs 32 are supported by the locking portions 31 a of the drive plate 31, and in the middle of the pair of outer peripheral side torsion springs 32.
  • the bent part 42a of the float member 42 is inserted into the part. Further, the outer peripheral portion of the outer peripheral side torsion spring 32 is supported by the outer peripheral portion of the float member 42.
  • the intermediate member 34 is an annular and disk-shaped plate member disposed between the piston 30 and the turbine shell 15.
  • the intermediate member 34 includes a first plate 44 and a second plate 45.
  • the first plate 44 and the second plate 45 are arranged with an interval in the axial direction.
  • the first plate 44 is disposed on the axial transmission side
  • the second plate 45 is disposed on the axial engine side.
  • the first plate 44 and the second plate 45 are connected to each other by a plurality of stopper pins 46 so that the outer peripheral portions thereof cannot rotate relative to each other and cannot move in the axial direction.
  • the first plate 44 and the second plate 45 are respectively formed with windows 44a and 45a penetrating in the axial direction.
  • the window portions 44 a and 45 a are formed to extend in the circumferential direction, and a cut-and-raised portion that is cut and raised in the axial direction is formed in the inner peripheral portion and the outer peripheral portion. .
  • a plurality of locking portions 44 b extending to the outer peripheral side torsion spring 32 are formed at the outer peripheral end of the first plate 44.
  • the plurality of locking portions 44b are formed by bending the tip of the first plate 44 toward the axial engine side.
  • the plurality of locking portions 44b are arranged at predetermined intervals in the circumferential direction, and a pair of outer peripheral side torsion springs 32 that act in series are arranged between the two locking portions 44b. Yes.
  • Each of the plurality of inner peripheral side torsion springs 33 includes a combination of a large coil spring and a small coil spring inserted into the large coil spring and having the same length as the spring length of the large coil spring.
  • the plurality of inner peripheral side torsion springs 33 are arranged side by side in the rotational direction on the inner peripheral side of the outer peripheral side torsion spring 32.
  • Each inner peripheral side torsion spring 33 is disposed in the windows 44 a and 45 a of both plates 44 and 45 of the intermediate member 34.
  • Each inner torsion spring 33 is supported at both ends in the circumferential direction and both sides in the radial direction by the windows 44a and 45a. Furthermore, each inner peripheral side torsion spring 33 is restricted from projecting in the axial direction by the cut and raised portions of the window portions 44 and 45.
  • the driven plate 35 is an annular and disk-shaped member, and an inner peripheral portion thereof is fixed to the flange 17 a of the turbine hub 17 by a rivet 18 together with the turbine shell 15.
  • the driven plate 35 is disposed between the first plate 44 and the second plate 45 so as to be rotatable relative to both the plates 44 and 45.
  • a window hole 35 a is formed in the outer peripheral portion of the driven plate 35 corresponding to the window portions 44 a and 45 a of the first and second plates 44 and 45.
  • the window hole 35a is a hole penetrating in the axial direction, and an inner peripheral torsion spring 33 is disposed in the window hole 35a.
  • a plurality of notches 35b that are long in the circumferential direction are formed on the outer peripheral portion of the driven plate 35, as indicated by broken lines in FIG. And the stopper pin 46 has penetrated this notch 35b to the axial direction. Therefore, the driven plate 35 and the plates 44 and 45 constituting the intermediate member 34 can be rotated relative to each other within an angle range where the notch 35b is formed.
  • the torus 6a of the torque converter main body 6 in this embodiment is formed in a relatively small size, and the plurality of outer peripheral side torsion springs 32 of the lockup device are arranged on the outer peripheral side of the torus 6a, and the plurality of inner peripheral sides are arranged.
  • the torsion spring 33 is disposed on the inner peripheral side of the torus 6a.
  • the plurality of outer peripheral side torsion springs 32 are arranged side by side in the rotational direction at the position of the mounting diameter Do.
  • the plurality of inner peripheral side torsion springs 33 are arranged side by side in the rotational direction at the position of the mounting diameter Di.
  • the mounting diameter Do of the outer peripheral side torsion spring 32 is larger than the outermost diameter To of the torus 6a, and the mounting diameter Di of the inner peripheral side torsion spring 33 is smaller than the innermost diameter Ti of the torus 6a.
  • the outer peripheral side torsion spring 32 is disposed closer to the transmission side than the inner peripheral side torsion spring 33 and is closer to the torque converter body 6 in the axial position.
  • a portion of the turbine 4 that is closest to the front cover 2 is closer to the front cover 2 than a portion of the outer peripheral side torsion spring 32 that is closest to the torque converter body 6. That is, the torque converter main body 6 and the outer peripheral side torsion spring 32 are arranged so as to overlap each other by a distance L in the axial direction.
  • Torque from the crankshaft on the engine side is input to the front cover 2.
  • the impeller 3 rotates and hydraulic oil flows from the impeller 3 to the turbine 4.
  • the turbine 4 is rotated by the flow of the hydraulic oil, and the torque of the turbine 4 is output to an input shaft (not shown).
  • the torque is transmitted in the order of the piston 30, the drive plate 31, the outer peripheral side torsion spring 32, the intermediate member 34, the inner peripheral side torsion spring 33, and the driven plate 35, and is output to the turbine hub 17.
  • the lockup device 7 transmits torque and absorbs and attenuates torque fluctuations input from the front cover 2. Specifically, when torsional vibration occurs in the lockup device 7, the outer peripheral side torsion spring 32 and the inner peripheral side torsion spring 33 are compressed in series between the drive plate 31 and the driven plate 35. Furthermore, also in the outer peripheral side torsion spring 32, one set of outer peripheral side torsion springs 32 is compressed in series.
  • the twist angle can be widened.
  • the outer peripheral side torsion spring 32 capable of increasing the circumferential distance can be operated in series, a wider twist angle can be secured. This means that the torsional characteristics can be further reduced in rigidity, and vibration absorption / damping performance can be further improved.
  • this lockup device 7 has a two-stage torsional characteristic.
  • the outer peripheral side torsion spring 32 tries to move to the outer peripheral side by centrifugal force. For this reason, the member which controls the movement to the outer peripheral side of the outer peripheral side torsion spring 32 is needed.
  • the movement of the outer peripheral side torsion spring 32 to the outer peripheral side is regulated by supporting the outer peripheral part of the outer peripheral side torsion spring 32 by the float member 42. At this time, since the float member 42 moves together with the outer peripheral side torsion spring 32, the sliding resistance can be reduced as compared with the case where the outer peripheral portion of the outer peripheral side torsion spring is supported by the drive plate as in the conventional device. it can.
  • the hysteresis torque as a whole is a combination of the hysteresis torque on the inner peripheral side and the outer peripheral side.
  • the hysteresis torque of the outer peripheral side torsion spring is small and the hysteresis torque of the inner peripheral side torsion spring is not different from that shown in the conventional patent document 1, and therefore the hysteresis torque as a whole. Becomes smaller. Therefore, vibration absorption / damping performance can be improved, and fuel consumption can be reduced by expanding the lock-up region.
  • the outer peripheral side and inner peripheral side torsion springs 32, 33 are arranged so that the mounting diameter Do of the outer peripheral side torsion spring 32 is larger than the outermost diameter To of the torus 6a and the mounting diameter Di of the inner peripheral side torsion spring 33. Is smaller than the innermost diameter Ti of the torus 6a. For this reason, the torque converter main body 6 and the lock-up device 7 can be brought closer to each other compared to the conventional torque converter. Further, the torque converter main body 6 and the outer peripheral side torsion spring 32 are arranged so as to overlap each other by a distance L in the axial direction. Therefore, the axial space of the entire torque converter can be made more compact.
  • the mounting diameter Do of the outer peripheral side torsion spring is larger than the outermost diameter To of the torus, but these may be the same diameter.
  • the mounting diameter Di of the inner periphery side torsion spring 33 and the innermost diameter Ti of the torus may be the same.
  • the number and length of coil springs constituting the outer peripheral side and inner peripheral side torsion springs are not limited to the above embodiment.
  • the axial space can be made compact, the damper twist angle in the lock-up device can be made wider, and the damper characteristics can be improved.
PCT/JP2010/068125 2009-12-09 2010-10-15 トルクコンバータ WO2011070852A1 (ja)

Priority Applications (4)

Application Number Priority Date Filing Date Title
US13/514,722 US9702445B2 (en) 2009-12-09 2010-10-15 Torque converter
CN2010800549822A CN102639904A (zh) 2009-12-09 2010-10-15 扭矩转换器
KR1020127014577A KR20120085889A (ko) 2009-12-09 2010-10-15 토크 컨버터
DE112010004737T DE112010004737T5 (de) 2009-12-09 2010-10-15 Drehmomentwandler

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
JP2009-279086 2009-12-09
JP2009279086A JP2011122622A (ja) 2009-12-09 2009-12-09 トルクコンバータ用ロックアップ装置

Publications (1)

Publication Number Publication Date
WO2011070852A1 true WO2011070852A1 (ja) 2011-06-16

Family

ID=44145405

Family Applications (1)

Application Number Title Priority Date Filing Date
PCT/JP2010/068125 WO2011070852A1 (ja) 2009-12-09 2010-10-15 トルクコンバータ

Country Status (6)

Country Link
US (1) US9702445B2 (de)
JP (1) JP2011122622A (de)
KR (1) KR20120085889A (de)
CN (1) CN102639904A (de)
DE (1) DE112010004737T5 (de)
WO (1) WO2011070852A1 (de)

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2014148467A1 (ja) * 2013-03-21 2014-09-25 株式会社エクセディ トルクコンバータのロックアップ装置

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WO2014053388A1 (en) * 2012-10-04 2014-04-10 Schaeffler Technologies AG & Co. KG Turbine piston thrust path
JP5805704B2 (ja) * 2013-05-16 2015-11-04 株式会社エクセディ トルクコンバータのロックアップ装置
US9611925B2 (en) * 2015-02-12 2017-04-04 Zhongtai Chen Torque converter having a reactor controlled by a jaw clutch
US9841060B2 (en) * 2015-10-20 2017-12-12 Valeo Embrayages Torsional vibration damper for hydrokinetic torque coupling device with inner and outer elastic damping members connected in series
JP6310442B2 (ja) * 2015-11-13 2018-04-11 古河電気工業株式会社 圧着端子、電線接続構造体、及びワイヤハーネス
JP6316261B2 (ja) * 2015-11-13 2018-04-25 古河電気工業株式会社 圧着端子、電線接続構造体、及びワイヤハーネス
JP6310441B2 (ja) * 2015-11-13 2018-04-11 古河電気工業株式会社 圧着端子、電線接続構造体、及びワイヤハーネス
US9927015B2 (en) * 2015-12-07 2018-03-27 Schaeffler Technologies AG & Co. KG Method of forming torque converter stator
KR101866035B1 (ko) * 2016-07-07 2018-06-08 현대자동차주식회사 차량용 토크 컨버터 댐퍼
KR101836728B1 (ko) * 2016-10-24 2018-03-08 현대자동차주식회사 차량용 토크컨버터
KR101878198B1 (ko) * 2017-05-23 2018-07-13 주식회사 카펙발레오 저강성 댐퍼가 채용된 3-웨이 방식의 토크 컨버터
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KR20120085889A (ko) 2012-08-01
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