WO2006057135A1 - トルクコンバータ - Google Patents
トルクコンバータ Download PDFInfo
- Publication number
- WO2006057135A1 WO2006057135A1 PCT/JP2005/019885 JP2005019885W WO2006057135A1 WO 2006057135 A1 WO2006057135 A1 WO 2006057135A1 JP 2005019885 W JP2005019885 W JP 2005019885W WO 2006057135 A1 WO2006057135 A1 WO 2006057135A1
- Authority
- WO
- WIPO (PCT)
- Prior art keywords
- turbine
- torque converter
- torsion spring
- fixed
- inner peripheral
- Prior art date
Links
Classifications
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16H—GEARING
- F16H45/00—Combinations of fluid gearings for conveying rotary motion with couplings or clutches
- F16H45/02—Combinations of fluid gearings for conveying rotary motion with couplings or clutches with mechanical clutches for bridging a fluid gearing of the hydrokinetic type
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16H—GEARING
- F16H41/00—Rotary fluid gearing of the hydrokinetic type
- F16H41/24—Details
-
- 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
- F16H2045/0247—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 having a turbine with hydrodynamic damping means
-
- 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 in particular, to one having a lock-up device.
- a torque converter can smoothly accelerate and decelerate in order to transmit power by a fluid.
- energy loss occurs due to fluid sliding, resulting in poor fuel consumption.
- some conventional torque converters are provided with a lockup device that mechanically connects an input-side front cover and an output-side turbine.
- the lockup device is disposed in a space between the front cover and the turbine.
- the lock-up device mainly consists of a disk-shaped piston that is pressed against the front cover, a driven plate attached to the rear side of the turbine, and a torsion spring that inertiaally connects the piston and the driven plate in the rotational direction. And is composed.
- An annular friction member is bonded to the piston at a position facing the flat friction surface of the front cover.
- the operation of the piston is controlled by a change in hydraulic pressure in the fluid chamber. Specifically, external hydraulic circuit force hydraulic fluid is supplied between the piston and the front cover when the lockup connection is released. This hydraulic oil flows radially outward in the space between the front cover and the piston, and further flows into the torque converter body on the outer peripheral side.
- the hydraulic fluid in the space between the front cover and the piston is drained by the inner peripheral side.
- the piston moves to the front cover side due to the hydraulic pressure difference.
- the friction member provided on the piston is pressed against the friction surface of the front cover. In this way, the torque of the front cover is transmitted to the turbine side via the lockup device.
- Patent Document 1 EUROPEAN PATENT APPLICATION 0070662A1
- a conventional torque converter lockup device includes, for example, a pair of input side plate members fixed to a piston, an output side plate member disposed between the axial directions thereof and fixed to a turbine knob, and both plate members. And a torsion spring that connects the two in the rotational direction.
- the output side plate member is fixed to the turbine hub with rivets together with the turbine shell.
- An object of the present invention is to provide a torque converter in which the outer peripheral edge of the torsion spring of the lockup device is positioned on the inner peripheral side of the inner peripheral edge of the fluid working chamber. It is to simplify the construction.
- the torque converter according to claim 1 includes a front cover, an impeller, a turbine, a stator, and a lockup device.
- the impeller is connected to the front cover to form a fluid chamber.
- the turbine is disposed opposite to the impeller in the fluid chamber, a turbine shell, a turbine blade fixed to one side of the turbine shell impeller, A turbine knob fixed to the inner periphery of the turbine shell.
- the stator is disposed between the inner peripheral portion of the impeller and the inner peripheral portion of the turbine, and constitutes a fluid working chamber together with the impeller and the turbine.
- the lock-up device is a device that is disposed between the front cover and the turbine and mechanically connects the two, and has a torsion spring that absorbs and attenuates torsional vibration.
- the outer peripheral edge of the torsion spring is located on the inner peripheral side from the inner peripheral edge of the fluid working chamber.
- the lock-up device includes a piston connectable to the front cover, a torsion spring, a drive member fixed to the piston for driving the torsion spring, and a driven part fixed to the turbine shell and driven by the torsion spring. Material.
- the driven member is fixed to the inner peripheral side portion of the turbine shell, so that the structure of the lockup device is simplified.
- the stator in claim 3, includes an annular stator carrier and a stator blade provided on an outer peripheral surface of the stator carrier.
- the stator carrier has a recess at a position corresponding to the torsion spring on the surface of the torsion spring.
- the stator carrier since the stator carrier has a recess at a position corresponding to the torsion spring, the axial dimension of the inner peripheral portion of the torque converter can be sufficiently shortened.
- the fixed portion of the turbine shell has a shape along the vicinity of the recess.
- the fixing portion of the turbine shell is a recess on the surface of the torsion spring, the axial dimension of the inner peripheral portion of the torque converter can be sufficiently shortened.
- the fixed portion of the turbine shell is close to the axial center position of the impeller and the turbine.
- the fixed portion of the turbine shell is positioned closer to the impeller than the center position in the axial direction of the impeller and the turbine.
- the fixed portion of the turbine shell has a plane perpendicular to the rotation axis.
- the driven member can be fixed easily and reliably.
- the driven member in any one of claims 1 to 7, is disposed in an annular shape corresponding to the torsion spring.
- the driven member is arranged corresponding to the torsion spring, and therefore the damper mechanism is downsized in the radial direction.
- the driven member has a plurality of claw portions that extend toward the piston side and abut against the rotational direction end of the torsion spring. Yes.
- the driven member has a simple structure having a claw portion.
- the axial engine side edge of the torsion spring is positioned closer to the axial transmission side than the most axial engine side edge of the turbine shell. is doing.
- the torsion spring is sufficiently close to the axial transmission side, so that the axial dimension of the inner peripheral portion of the torque converter can be sufficiently shortened.
- FIG. 1 is a schematic vertical sectional view of a torque converter as one embodiment of the present invention.
- FIG. 2 is a partial plan view of the lockup device.
- FIG. 1 shows a torque converter 1 in which an embodiment of the present invention is adopted.
- the torque converter 1 is mainly a torus-shaped fluid consisting of a front cover 2 and three types of impellers (impeller 10, turbine 11, stator 12) arranged concentrically with the front cover 2.
- the working chamber 3 and the mouth-up device 4 arranged in the space between the front cover 2 and the turbine 11 in the axial direction are also configured.
- the outer periphery of the front cover 2 and the impeller shell 15 of the impeller 10 is fixed by welding, and both form a fluid chamber filled with hydraulic oil.
- the front cover 2 is a member to which engine crankshaft (not shown) force torque is input.
- the front cover 2 is mainly composed of a disk-shaped main body 5. Inside body 5 Center boss 6 is fixed to the heart. A plurality of nuts 7 are fixed to the outer peripheral engine side surface of the main body 5. An outer peripheral cylindrical portion 8 extending toward the axial transmission side is formed on the outer peripheral portion of the main body 5.
- An annular and flat friction surface 70 is formed inside the main body 5 of the front cover 2 on the outer peripheral portion.
- the friction surface 70 faces the axial transmission side.
- the fluid working chamber 3 is disposed on the axial transmission side in the fluid chamber. As a result, the fluid chamber is divided into a fluid working chamber 3 and a space formed between the main body 5 of the front cover 2 and the turbine 11.
- the impeller 10 also includes an impeller shell 15, a plurality of impeller blades 16 fixed to the inside of the impeller shell 15, and an impeller hub 18 fixed to the inner peripheral edge of the impeller shell 15. ing.
- the impeller blade 16 is fixed to the outer peripheral side portion of the impeller shell 15 whose radial dimension is significantly shorter than the conventional one.
- the turbine 11 is disposed to face the impeller 10 in the fluid chamber.
- the turbine 11 also includes a turbine shell 20, a plurality of turbine blades 21 fixed to the turbine shell 20, and a turbine knob 23 fixed to the inner peripheral edge of the turbine shell 20.
- the turbine bin blade 21 is fixed to the outer peripheral side portion of the turbine shell 20 whose radial dimension is significantly shorter than the conventional one.
- the turbine hub 23 has a cylindrical boss 23a and a flange 23b whose force also extends to the outer peripheral side.
- the flange 23 b is fixed to the inner peripheral portion of the turbine shell 20 by a plurality of rivets 24.
- a spline 23c is formed on the inner peripheral surface of the boss 23a. The spline 23c is engaged with a main drive shaft 71 that extends the transmission side force. As a result, the torque of the turbine hub 23 is output to the main drive shaft 71.
- the stator 12 is disposed between the inner peripheral portion of the impeller 10 and the inner peripheral portion of the turbine 11.
- the stator 12 is a mechanism for rectifying the hydraulic oil returning from the turbine 11 to the impeller 10 and realizing a torque amplifying function in the torque converter 1. This torque amplification action provides excellent acceleration performance when starting.
- the stator 12 includes a stator carrier 27 and a plurality of stator blades 28 provided on the outer peripheral surface thereof.
- the stator carrier 27 is supported by the stator shaft 72 via the one-way clutch 30. ing.
- the stator shaft 72 is a cylindrical member disposed around the main drive shaft 71.
- the stator carrier 27 extends longer in the radial direction than in the prior art, and the axial engine side surface 27a is recessed throughout. Specifically, the radially intermediate portion of the stator carrier 27 axially engine-side surface 27a is positioned closer to the axial transmission side than the inner peripheral portion as well as the outer peripheral portion of the stator blade 28 inlet side surface. Naturally, it is located closer to the axial transmission side than the axial center position C1 of the fluid working chamber 3.
- the inner peripheral portion 20a of the turbine shell 20 (the portion where the turbine blade 21 is not fixed) is curved in the axial direction along the stator carrier 27, and its radially intermediate portion is fluid-operated. It is located on the transmission side in the axial position from the axial center position C1 of chamber 3.
- the inner peripheral side portion 20a of the turbine shell 20 is close to the axial center position of the impeller 10 and the turbine 11, and is sufficiently close to the axial transmission side, so that the axial direction of the inner peripheral portion of the torque converter 1 Dimensions can be shortened sufficiently.
- the inner peripheral side portion 20a of the turbine shell 20 is located on the impeller 10 side from the axial center position C1 of the impeller 10 and the turbine 11, and is sufficiently close to the axial transmission side. Therefore, the axial dimension of the inner peripheral portion of the torque converter 1 can be sufficiently shortened.
- the stator carrier 27 and the turbine shell 20 are largely bent toward the axial transmission side to form a recess facing the axial engine side, thereby corresponding to the inner peripheral side of the fluid working chamber 3, particularly to the turbine 11. Space for a damper mechanism 42, which will be described later, is secured on the inner peripheral side of the portion to be operated.
- a first washer 32 is arranged between the main body 5 of the front cover 2 and the turbine hub 23 in the axial direction.
- the first washer 32 is formed with a plurality of grooves extending in the radial direction, and hydraulic oil can flow through both sides of the first washer 32 in the radial direction.
- a first port 66 is formed between the inner periphery of the front cover 2 and the turbine knob 23 so that hydraulic fluid can communicate in the radial direction.
- the first port 66 communicates an oil passage 61 provided in the main drive shaft 71 with a front chamber 81 between the front cover 2 and the piston 41.
- a second thrust bearing 33 is disposed between the turbine hub 23 and the one-way clutch 30. It is. In the second thrust bearing 33, hydraulic oil can flow through both sides in the radial direction. Between the turbine hub 23 and the inner peripheral portion of the stator 12 (specifically, the one-way clutch 30), a second port 67 capable of communicating hydraulic oil is formed on both sides in the radial direction. In other words, the second port 67 allows the fluid passage 62 between the main drive shaft 71 and the stator shaft 72 to communicate with the fluid working chamber 3.
- a third thrust bearing 34 is disposed between the stator carrier 27 and the inner peripheral portion of the impeller shell 15 in the axial direction.
- the working oil can circulate on both sides in the radial direction.
- a third port 68 capable of communicating hydraulic fluid is formed on both radial sides. That is, the third port 68 communicates the fluid passage 63 between the stator shaft 72 and the impeller hub 18 and the fluid working chamber 3.
- each of the oil passages 61 to 63 is connected to a hydraulic circuit (not shown) and can independently supply and discharge hydraulic fluid to the first to third ports 66 to 68.
- the lockup device 4 is disposed in an annular space formed between the main body 5 of the front cover 2 and the turbine 11 in the axial direction, and the front cover 2 and the turbine 11 It is a device for mechanically connecting and disconnecting.
- the lockup device 4 has a piston function that is activated by a change in hydraulic pressure in the space, and a damper function that absorbs and attenuates torsional vibration in the rotational direction.
- the lockup device 4 is mainly composed of a piston 41 and a damper mechanism 42!
- the piston 41 is a disc-shaped member disposed in the space near the main body 5 of the front cover 2.
- the piston 41 divides the space into a front chamber 81 on the front cover 2 side and a rear chamber 82 on the turbine 11 side.
- the outer periphery of the piston 41 is a friction coupling portion 49 disposed on the axial transmission side of the friction surface 70 of the front cover 2.
- the friction connecting portion 49 is an annular flat plate-like portion, and an annular friction facing 46 is attached to the axial engine side.
- An inner peripheral cylindrical portion 47 is formed on the inner peripheral edge of the piston 41.
- the inner peripheral cylindrical portion 47 extends from the inner peripheral edge of the piston 41 toward the axial transmission side.
- An inner peripheral surface of the inner peripheral cylindrical portion 47 is supported by an outer peripheral surface 26 of the turbine blade 23 so as to be movable in the axial direction and the rotational direction.
- the axial transmission side of the inner cylindrical part 47 is the flange 2 of the turbine hub 23. It can come into contact with 3b. This restricts the movement of the piston 41 toward the axial transmission side.
- An annular groove is formed on the outer peripheral surface 26, and a seal ring 48 is disposed in the groove.
- the seal ring 48 is in contact with the inner peripheral surface of the inner peripheral cylindrical portion 47.
- the seal ring 48 seals both axial sides of the inner periphery of the piston 41.
- the damper mechanism 42 is a mechanism for transmitting torque from the piston 41 to the turbine hub 23 and absorbing and damping torsional vibration.
- the damper mechanism 42 is disposed between the intermediate portion in the radial direction of the piston 41 and the inner peripheral portion of the turbine shell 20. More specifically, the damper mechanism 42 is arranged in an annular space corresponding to the recess of the inner peripheral side portion 20a of the turbine shell 20.
- the damper mechanism 42 is mainly composed of a drive member 50, a driven member 51, and a torsion spring 52.
- arrow R1 is the rotational direction drive side
- arrow R2 is the rotational direction reverse drive side.
- the drive member 50 is a drive member for inputting torque to the torsion spring 52, and further has a function of holding the torsion spring 52 to the piston 41.
- the drive member 50 is a plate member extending in an annular shape, and is fixed to the surface of the piston 41 on the axial transmission side.
- the drive member 50 is disposed so as to face the concave portion of the inner peripheral side portion 20a of the turbine shell 20 in the axial direction.
- the drive member 50 includes a disk-shaped portion 50a that contacts the piston 41, and an outer peripheral cylindrical portion 50b that extends from the outer periphery to the axial transmission side.
- the disc-like portion 50a is fixed to the piston 41 by rivets 55 arranged at a plurality of locations in the circumferential direction.
- the torsion spring 52 is an elastic member for absorbing torsional vibration, and also has a coil spring force, for example.
- a plurality of torsion springs 52 are arranged side by side in the circumferential direction.
- the torsion spring 52 is arranged on the engine side in the axial direction of the disk-like part 50a of the drive member 50 and on the inner peripheral side of the outer cylindrical part 50b.
- the torsion spring 52 is disposed between the rivets 55.
- the outer peripheral side cylindrical portion 50b is bent slightly inward in the radial direction on the tip end side, and thus restricts the axial movement of the torsion spring 52.
- the outer peripheral cylindrical portion 50b has a first support portion 50c deformed so as to protrude radially inwardly at a position corresponding to the rotation direction between the torsion springs 52. . Both ends of the first support portion 50c in the rotational direction are in contact with rotational ends (more precisely, spring seats) of the torsion spring 52.
- the drive member 50 extends from the inner peripheral edge of the disc-like portion 50a to the axial transmission side at a position corresponding to the rotational direction of the torsion springs 52, and further, the distal end is outward in the radial direction. It has a bent second support part 50e. Both ends of the second support portion 50e in the rotation direction are in contact with rotation direction ends of the torsion spring 52 (more precisely, a spring seat). Further, the drive member 50 has a third support portion 50d extending from the inner peripheral edge of the disc-like portion 50a toward the axial transmission side at a position corresponding to the torsion spring 52. The third support portion 50d restricts the movement of the torsion spring 52 inward in the radial direction.
- the driven member 51 is an annular plate member, and is fixed to the inner peripheral side portion of the turbine shell 20. More specifically, the driven member 51 has an annular portion 51a fixed to the recess 20a of the turbine shell 20 by fitting or welding (for example, TIG welding).
- the annular portion 51a has a plane perpendicular to the rotation axis, like the recess 20a.
- the inner peripheral portion of the annular portion 51a has an annular protrusion 5 lb extending on the axial engine side so as to extend along the cylindrical portion 20b constituting the inner peripheral side of the recess 20a.
- the driven member 51 has an engaging claw 51c cut and raised from the outer peripheral side of the annular portion 5la and extending toward the axial engine side.
- the engaging claws 51c extend correspondingly between the torsion springs 52, and both ends in the rotation direction are in contact with the rotation direction ends of the torsion springs 52 (more precisely, spring seats). Since the inner peripheral side portion 20a of the turbine shell 20 has a planar shape, the driven member 51 can be easily and reliably fixed.
- the torsion spring 52 is disposed on the inner peripheral side of the fluid working chamber 3. More precisely, the outer peripheral side edge of the torsion spring 52 is located closer to the inner peripheral side than the inner peripheral side edge of the fluid working chamber 3 (the outer peripheral surface of the stator carrier 27). In addition, the torsion spring 52 partially enters the inner peripheral side of the fluid working chamber 3, and the axial transmission side edge of the torsion spring 52 exceeds the axial transmission side edge of the turbine blade 21 of the turbine 11. It is close to the axial center CI of the lath. Further, since the driven member 51 is arranged in an annular shape corresponding to the torsion spring 52, the damper mechanism 42 is downsized in the radial direction.
- the torsion spring 52 has a coil diameter significantly larger than that of the conventional one without increasing the axial dimension of the entire torque converter 1. Since the coil diameter of the torsion spring 52 can be increased in this manner, the performance of the torsion spring 52 can be easily improved. As a result, it becomes possible to use the fluid torque transmission by the torus of the torque converter 1 only at the start of the vehicle, and thereafter use it in the mechanical torque transmission state in which the lockup device 4 is connected.
- Torque from the crankshaft on the engine side is input to the front cover 2 via the flexible plate.
- the impeller 10 rotates and hydraulic oil flows to the impeller 10 power turbine 11.
- the turbine 11 is rotated by the flow of the hydraulic oil, and the torque of the turbine 11 is output to the main drive shaft 71.
- the structure of the damper mechanism is simplified. Specifically, the structure of the present invention has fewer parts than a conventional structure in which a torsion spring is sandwiched between two plates and the hub flange disposed between them is fixed to the turbine hub with rivets. Further downsizing. As described above, the cost is reduced.
- the driven member 51 of the damper mechanism 42 is fixed to the inner peripheral portion 20a of the turbine shell 20, in other words, the damper mechanism 42 is disposed in the recess of the turbine shell 20, so that the torque converter 1
- the axial dimension of the inner periphery of the can is made sufficiently small.
- the torque converter 1 Since the axial engine side edge of the torsion spring 52 (also the drive member 50) is located closer to the axial transmission side than the most axial engine side portion of the turbine shell 20 of the turbine 11, the torque converter 1 The axial dimension of the inner periphery of the can is made sufficiently small.
- the driven member may include a plurality of member members divided in the circumferential direction.
- the driven member may be fixed to the turbine shell by caulking or rivets.
- the present invention can be used for a torque converter, particularly one having a lockup device.
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- Engineering & Computer Science (AREA)
- General Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- Mechanical Operated Clutches (AREA)
Abstract
Description
Claims
Priority Applications (2)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
US11/667,790 US20080041684A1 (en) | 2004-11-24 | 2005-10-28 | Torque Converter |
DE112005002860T DE112005002860T5 (de) | 2004-11-24 | 2005-10-28 | Drehmomentwandler |
Applications Claiming Priority (2)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
JP2004338792A JP4966492B2 (ja) | 2004-11-24 | 2004-11-24 | トルクコンバータ |
JP2004-338792 | 2004-11-24 |
Publications (1)
Publication Number | Publication Date |
---|---|
WO2006057135A1 true WO2006057135A1 (ja) | 2006-06-01 |
Family
ID=36497877
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
PCT/JP2005/019885 WO2006057135A1 (ja) | 2004-11-24 | 2005-10-28 | トルクコンバータ |
Country Status (5)
Country | Link |
---|---|
US (1) | US20080041684A1 (ja) |
JP (1) | JP4966492B2 (ja) |
KR (1) | KR20070086576A (ja) |
DE (1) | DE112005002860T5 (ja) |
WO (1) | WO2006057135A1 (ja) |
Families Citing this family (3)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
JP2011085236A (ja) * | 2009-10-19 | 2011-04-28 | Exedy Corp | トルクコンバータ用のロックアップ装置 |
JP4755277B2 (ja) * | 2009-12-10 | 2011-08-24 | 株式会社エクセディ | トルクコンバータ用ロックアップ装置 |
JP5684515B2 (ja) * | 2010-08-20 | 2015-03-11 | 株式会社エクセディ | トルクコンバータ |
Citations (5)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
JPH03104555U (ja) * | 1990-02-14 | 1991-10-30 | ||
JPH08338475A (ja) * | 1995-06-09 | 1996-12-24 | Unisia Jecs Corp | 捩り振動低減装置 |
JP2002048218A (ja) * | 2000-05-26 | 2002-02-15 | Exedy Corp | 弾性連結機構 |
JP2002147563A (ja) * | 2000-11-15 | 2002-05-22 | Exedy Corp | トルクコンバータ |
JP2004513304A (ja) * | 2000-11-02 | 2004-04-30 | ヴァレオ | 自動車用の流体動力学的結合装置 |
Family Cites Families (8)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US4240532A (en) * | 1978-09-21 | 1980-12-23 | Chrysler Corporation | Torsional isolator for torque converter lock-up mechanism |
DE3029860A1 (de) * | 1980-08-07 | 1982-03-04 | Fichtel & Sachs Ag, 8720 Schweinfurt | Hydrodynamischer drehmomentwandler |
JPH0253558U (ja) * | 1988-10-11 | 1990-04-18 | ||
JPH0483954A (ja) * | 1990-07-26 | 1992-03-17 | Toyota Motor Corp | ロックアップクラッチ付流体継手 |
US6016894A (en) * | 1998-02-06 | 2000-01-25 | Mannesmann Sachs Ag | Hydrodynamic coupling device with a lockup clutch |
US6264018B1 (en) * | 1999-02-09 | 2001-07-24 | Exedy Corporation | Lockup device of a torque converter |
JP2000266158A (ja) * | 1999-03-17 | 2000-09-26 | Exedy Corp | トルクコンバータのロックアップ装置 |
JP4883921B2 (ja) * | 2005-02-24 | 2012-02-22 | 株式会社エクセディ | トルクコンバータ |
-
2004
- 2004-11-24 JP JP2004338792A patent/JP4966492B2/ja active Active
-
2005
- 2005-10-28 WO PCT/JP2005/019885 patent/WO2006057135A1/ja active Application Filing
- 2005-10-28 DE DE112005002860T patent/DE112005002860T5/de not_active Withdrawn
- 2005-10-28 KR KR1020077014285A patent/KR20070086576A/ko not_active Application Discontinuation
- 2005-10-28 US US11/667,790 patent/US20080041684A1/en not_active Abandoned
Patent Citations (5)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
JPH03104555U (ja) * | 1990-02-14 | 1991-10-30 | ||
JPH08338475A (ja) * | 1995-06-09 | 1996-12-24 | Unisia Jecs Corp | 捩り振動低減装置 |
JP2002048218A (ja) * | 2000-05-26 | 2002-02-15 | Exedy Corp | 弾性連結機構 |
JP2004513304A (ja) * | 2000-11-02 | 2004-04-30 | ヴァレオ | 自動車用の流体動力学的結合装置 |
JP2002147563A (ja) * | 2000-11-15 | 2002-05-22 | Exedy Corp | トルクコンバータ |
Also Published As
Publication number | Publication date |
---|---|
KR20070086576A (ko) | 2007-08-27 |
DE112005002860T5 (de) | 2008-01-10 |
US20080041684A1 (en) | 2008-02-21 |
JP2006144997A (ja) | 2006-06-08 |
JP4966492B2 (ja) | 2012-07-04 |
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