WO2013154065A1 - トルクコンバータのロックアップ装置 - Google Patents
トルクコンバータのロックアップ装置 Download PDFInfo
- Publication number
- WO2013154065A1 WO2013154065A1 PCT/JP2013/060595 JP2013060595W WO2013154065A1 WO 2013154065 A1 WO2013154065 A1 WO 2013154065A1 JP 2013060595 W JP2013060595 W JP 2013060595W WO 2013154065 A1 WO2013154065 A1 WO 2013154065A1
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- WO
- WIPO (PCT)
- Prior art keywords
- clutch
- front cover
- turbine
- oil chamber
- torque converter
- Prior art date
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Classifications
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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
- F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
- F16D25/00—Fluid-actuated clutches
- F16D25/06—Fluid-actuated clutches in which the fluid actuates a piston incorporated in, i.e. rotating with the clutch
- F16D25/062—Fluid-actuated clutches in which the fluid actuates a piston incorporated in, i.e. rotating with the clutch the clutch having friction surfaces
- F16D25/063—Fluid-actuated clutches in which the fluid actuates a piston incorporated in, i.e. rotating with the clutch the clutch having friction surfaces with clutch members exclusively moving axially
- F16D25/0635—Fluid-actuated clutches in which the fluid actuates a piston incorporated in, i.e. rotating with the clutch the clutch having friction surfaces with clutch members exclusively moving axially with flat friction surfaces, e.g. discs
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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
- F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
- F16D25/00—Fluid-actuated clutches
- F16D25/12—Details not specific to one of the before-mentioned types
-
- 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
- F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
- F16D33/00—Rotary fluid couplings or clutches of the hydrokinetic type
- F16D33/18—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
- F16H2045/021—Combinations of fluid gearings for conveying rotary motion with couplings or clutches with mechanical clutches for bridging a fluid gearing of the hydrokinetic type three chamber system, i.e. comprising a separated, closed chamber specially adapted for actuating a lock-up clutch
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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
- F16H2045/0215—Details of oil circulation
-
- 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
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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
- 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
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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
- 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 lockup device, and more particularly to a torque converter lockup device for transmitting torque from a front cover to a member on the transmission side via a turbine of the torque converter.
- the torque converter is often provided with a lock-up device for transmitting torque directly from the front cover to the turbine.
- the lockup 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 in a rotational direction to the piston and the drive plate. And a driven plate that is elastically coupled. The driven plate is fixed to the turbine.
- Patent Document 1 a so-called multi-plate lockup device using a plurality of clutch plates has been proposed in order to increase the clutch capacity of the lockup device.
- the lock-up device disclosed in Patent Document 1 includes a clutch portion disposed between a front cover and a turbine, a power transmission plate connected to an output member of the clutch portion, a power transmission plate, and a turbine.
- the clutch part has a plurality of clutch plates, and a piston disposed between the front cover and the plurality of clutch plates.
- a lockup oil chamber is formed between the front cover and the piston, and a plurality of clutch plates and a back plate for supporting these are arranged between the piston and the turbine.
- An object of the present invention is to reduce the axial size of the lockup device by devising the arrangement of pistons and oil chambers.
- a torque converter lockup device is a device for transmitting torque from a front cover to a member on a transmission side via a turbine of the torque converter, and includes a clutch portion, a damper mechanism, It is equipped with.
- a clutch part is arrange
- the damper mechanism transmits torque from the clutch portion to the turbine and absorbs and attenuates torsional vibration.
- the clutch portion includes a clutch output member that outputs torque to the damper mechanism, a clutch plate for transmitting torque between the front cover and the clutch output member, a disk-like oil chamber plate, a piston, have.
- the oil chamber plate is provided between the front cover and the turbine inner periphery so as not to move in the axial direction with respect to the front cover.
- the piston is provided between the front cover and the oil chamber plate so as to be movable in the axial direction, and forms a first oil chamber for lockup between the oil chamber plate and the lockup release with the front cover.
- the second oil chamber is configured, and the clutch portion is engaged with the hydraulic oil supplied to the first oil chamber.
- the first oil chamber for lockup is formed between the front cover and the turbine, and the piston moves from the turbine side to the front cover side to be in the lockup state. Therefore, compared with the conventional lockup device. Thus, the axial dimension can be shortened.
- the responsiveness at the time of switching between lockup and unlocking is improved.
- the 2nd oil chamber is comprised by the piston and the front cover, the oil chamber for lockup cancellation
- release can be comprised with few components, and an axial direction dimension can be shortened more.
- the lock-up device for a torque converter according to the second aspect of the present invention is the device according to the first aspect, wherein the clutch portion further has an annular boss extending in the axial direction.
- the annular boss has an inner peripheral portion of the oil chamber plate fixed to an end portion on the transmission side, an end surface on the front cover side is fixed to the front cover, and a piston slides in the axial direction on the outer peripheral surface.
- An oil passage for supplying hydraulic oil to the first oil chamber is formed.
- a torque converter lockup device is the device according to the first or second aspect, wherein the turbine includes a plurality of turbine blades, a turbine shell that supports the plurality of turbine blades, and the turbine shell connected to each other.
- the turbine hub has a flange portion that extends in a radial direction and is connected to an inner peripheral portion of the turbine shell.
- the flange portion includes an axial support portion formed on the outer peripheral portion, and a front end from an outer peripheral end portion of the axial support portion.
- a radial support portion extending in the cover side and formed in a cylindrical shape.
- the clutch output member has a clutch engagement portion, a damper engagement portion, a radial contact portion, and an axial contact portion.
- the clutch engaging portion is formed at the radially intermediate portion so as to extend toward the front cover, and engages with the clutch plate so as to be movable in the axial direction but not relatively rotatable.
- the damper engaging portion is formed on the outer peripheral portion and engages with the damper mechanism.
- the radial contact portion is formed in a cylindrical shape extending in the axial direction at the inner peripheral portion, and is in contact with the radial support portion of the turbine hub.
- the axial contact portion projects inward from the radial contact portion and contacts the axial support portion of the turbine hub.
- the clutch output member is provided with the clutch engaging portion and the damper engaging portion, the power transmission path can be configured with a small number of parts. Further, the clutch output member can be easily positioned in the axial direction and the radial direction by causing a part of the clutch output member to abut against the axial support portion and the radial support portion of the turbine hub.
- the lock-up device for a torque converter according to the fourth aspect of the present invention is the device according to the third aspect, wherein the damper mechanism has a plurality of torsion springs and an intermediate member.
- the plurality of torsion springs engage with the clutch output member.
- the intermediate member is disposed so as to be rotatable relative to the clutch output member, and causes at least two of the plurality of torsion springs to act in series.
- the intermediate member includes a spring engaging portion that engages with an end surface of the torsion spring, a cover portion that covers the outer periphery of the torsion spring and the side portion on the front cover side, and a plurality of protrusions that extend from the cover portion to the inner peripheral side. ,have.
- the clutch output member has a positioning portion that contacts the plurality of protrusions of the intermediate member and positions the intermediate member above the clutch engaging portion and below the damper engaging portion.
- the intermediate member can be positioned by the clutch output member.
- the torque converter lock-up device is the fourth aspect of the device according to the fourth aspect, wherein the positioning portion of the clutch output member is in contact with the inner peripheral end surface of the intermediate member to position the intermediate member in the radial direction.
- a direction positioning portion, and an axial positioning portion that contacts the side surfaces of the plurality of protrusions of the intermediate member and positions the intermediate member in the axial direction.
- the annular boss is formed with an oil passage for supplying hydraulic oil to the second oil chamber for releasing the lockup. ing.
- the axial dimension of the clutch portion can be particularly shortened.
- FIG. 1 is a partial cross-sectional view of a torque converter including a lockup device according to an embodiment of the present invention.
- the figure which shows the lockup apparatus of the torque converter shown by FIG. The figure which expands and shows the piston of the lockup apparatus shown by FIG. 2, and the structure which supports it.
- FIG. 1 is a longitudinal sectional view of a torque converter 1 in which an embodiment of the present invention is adopted.
- the torque converter 1 is a device for transmitting torque from a crankshaft of an engine to an input shaft of a transmission.
- 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 FIG. OO shown in FIG. 1 is a rotating shaft of the torque converter 1.
- the torque converter 1 mainly includes a front cover 2, a torque converter body including three types of impellers (impeller 3, turbine 4, and stator 5), and a lockup device 6.
- the front cover 2 is a disk-shaped member, and a center boss 8 is fixed to the inner peripheral end by welding.
- the center boss 8 is a cylindrical member extending in the axial direction, and is inserted into a center hole of a crankshaft (not shown).
- the front cover 2 is connected to the crankshaft of the engine via a flexible plate. That is, a plurality of bolts 9 are fixed at equal intervals in the circumferential direction on the outer peripheral side and the engine side surface of the front cover 2, and the outer peripheral portion of the flexible plate is moved to the front by the nuts screwed into the bolts 9. It is fixed to the cover 2.
- An outer peripheral cylindrical portion 2 a extending toward the axial transmission side is formed on the outer peripheral portion of the front cover 2.
- An impeller 3 is fixed to the tip of the outer peripheral cylindrical portion 2a by welding. As a result, the front cover 2 and the impeller 3 form a fluid chamber that is filled with hydraulic oil.
- a friction surface 2b is formed on the side surface on the turbine 4 side in the radial intermediate portion of the front cover 2. Furthermore, a cylindrical seal portion 2c extending toward the axial turbine 4 is formed on the inner peripheral side of the friction surface 2b.
- the impeller 3 mainly includes an impeller shell 10 and a plurality of impeller blades 11 fixed inside thereof. And the front-end
- the turbine 4 is disposed to face the impeller 3 in the axial direction.
- the turbine 4 mainly includes a turbine shell 14, a plurality of turbine blades 15 fixed inside the turbine shell 14, and a turbine hub 16 fixed to the inner peripheral end of the turbine shell 14.
- the turbine shell 14 and the turbine hub 16 are fixed by a plurality of rivets 17.
- the turbine hub 16 has a disk-like flange portion 16a and a cylindrical portion 16b.
- the flange portion 16 a has an inner peripheral end portion of the turbine shell 14 fixed by a rivet 17.
- the cylindrical portion 16b is formed to extend from the inner peripheral end of the flange portion 16a to the transmission side.
- a spline hole 16c is formed in the inner peripheral portion of the cylindrical portion 16b and meshes with a spline shaft formed at the tip of the input shaft 18 of the transmission.
- the flange portion 16a has an axial support portion 16d and a radial support portion 16e on the outer peripheral portion.
- the axial support portion 16d is formed in a step difference in the axial direction at the outer peripheral end of the flange portion 16a.
- the radial support portion 16e is formed in a cylindrical shape and extends from the tip of the axial positioning portion 16d to the front cover 2 side in the axial direction.
- a through hole 16 f for supplying hydraulic oil for supplying hydraulic oil of the torque converter to the impeller 3 is formed in the inner peripheral portion of the flange portion 16 a of the turbine hub 16.
- the stator 5 is a mechanism for rectifying the flow of hydraulic oil that is disposed between the inner periphery of the impeller 3 and the inner periphery of the turbine 4 and returns from the turbine 4 to the impeller 3.
- the stator 5 is integrally formed by casting with resin, aluminum alloy or the like.
- the stator 5 mainly includes an annular stator shell 20 and a plurality of stator blades 21 provided on the outer peripheral surface of the stator shell 20.
- the stator shell 20 is connected to a fixed shaft 23 via a one-way clutch 22.
- An annular recess 20a is formed on the surface of the stator shell 20 on the front cover 2 side at a position facing the rivet 17.
- the recess 20a is formed to avoid interference with the head of the rivet 17.
- thrust bearings 23a and 23b are arranged between the stator shell 20 and the impeller shell 10 and between the stator shell 20 and the flange portion 16a of the turbine hub 16, respectively.
- the lockup device 6 is disposed between the front cover 2 and the turbine 4 and directly transmits power from the front cover 2 to the turbine 4.
- the lockup device 6 includes a clutch portion 24 disposed between the front cover 2 and the turbine 4, and a damper mechanism 25 that transmits torque from the clutch portion 24 to the turbine 4.
- the clutch unit 24 transmits torque from the front cover 2 to the damper mechanism 25 or blocks torque transmission between the front cover 2 and the damper mechanism 25.
- the clutch portion 24 includes a clutch output member 27, a clutch plate 28, an oil chamber plate 29, a piston 30, and a boss 31 as shown in an enlarged manner in FIG.
- the clutch output member 27 is disposed between the front cover 2 and the turbine 4.
- the clutch output member 27 is formed in an annular shape, and includes a disc portion 27a formed in a disc shape, a clutch engagement portion 27b, a plurality of damper engagement portions 27c, a radial contact portion 27d, It has an axial contact portion 27e, and a plurality of radial positioning portions 27f and axial positioning portions 27g, respectively. Each of these parts is formed by pressing one plate.
- the plurality of clutch engaging portions 27b are formed by bending a part of the intermediate portion in the radial direction of the disc portion 27a to the front cover 2 side.
- the plurality of damper engaging portions 27c are formed to extend further from the outer peripheral portion of the disc portion 27a to the outer peripheral side.
- Each damper engaging portion 27 c has a portion extending on the outer peripheral side and a portion extending in the axial direction, and can be engaged with an end surface of a torsion spring (described later) constituting the damper mechanism 25.
- the radial contact portion 27d is a portion formed by bending the inner peripheral end of the disc portion 27a toward the turbine 4, and is formed in a cylindrical shape and extends in the axial direction.
- the radial contact portion 27d is supported by being in contact with the radial support portion 16e of the turbine hub 16. With such a configuration, the clutch output member 27 is positioned in the radial direction.
- the axial contact portion 27e is a portion formed by bending the axial end portion of the radial contact portion 27d toward the inner peripheral side, and is formed in an annular shape.
- the axial contact portion 27e is sandwiched between the axial support portion 16d of the turbine hub 16 and an output plate 55 (described later) in the axial direction. With such a configuration, the clutch output member 27 is positioned in the axial direction.
- the plurality of radial positioning portions 27f are portions formed by bending a part of the outer peripheral portion of the disc portion 27a to the front cover 2 side, and extend in the axial direction.
- the axial positioning portion 27g is a portion formed by bending the axial end portion of the radial positioning portion 27f outward.
- the clutch plate 28 is formed in a disc shape and is disposed so as to face the friction surface 2b of the front cover 2.
- An annular friction member is fixed to both surfaces of the clutch plate 28.
- a plurality of teeth that engage with the clutch engaging portion 27 b of the clutch output member 27 are formed at the outer peripheral end of the clutch plate 28.
- the oil chamber plate 29 is disposed between the front cover 2 and the turbine hub 16.
- the oil chamber plate 29 has a disk part 29a and a cylindrical part 29b extending from the outer peripheral end of the disk part 29a to the axial front cover 2 side.
- the disc part 29 a is fixed to the outer peripheral surface of the boss 31.
- a plurality of embossed portions 29c that are formed so as to protrude toward the front cover 2 are formed at the radial intermediate portion of the disc portion 29a.
- the embossed portion 29 c can contact the side surface of the piston 30.
- a plurality of teeth 29d are formed at the tip of the cylindrical portion 29b.
- the piston 30 is disposed between the front cover 2 and the oil chamber plate 29.
- the piston 30 has a disk-shaped oil chamber constituting part 30a, a pressing part 30b, and a connecting part 30c for connecting them.
- the oil chamber component 30 a is disposed so as to face the inner peripheral portion of the front cover 2 and the disk portion 29 a of the oil chamber plate 29. Further, the inner peripheral end face of the oil chamber component 30 a is slidably supported on the outer periphery of the boss 31.
- a seal member 34 is provided on the outer peripheral surface of the connecting portion 30 c, and the seal member 34 is slidably in contact with the inner peripheral surface of the cylindrical portion 29 b of the oil chamber plate 29.
- a seal member 35 is provided on the outer peripheral surface of the seal portion 2 b of the front cover 2, and the seal member 35 is in contact with the inner peripheral surface of the coupling portion 30 c of the piston 30.
- the pressing portion 30b is opposed to the clutch plate 28.
- a plurality of notches 30d extending in the circumferential direction are formed on the inner peripheral side of the pressing portion 30b, and a plurality of teeth 29d of the oil chamber plate 29 are inserted into and engaged with the notches 30d.
- the boss 31 is formed in an annular shape.
- the end surface of the boss 31 on the front cover 2 side is fixed to the side surface of the front cover 2.
- the inner peripheral end of the oil chamber plate 29 is fixed to the outer peripheral surface at the end of the boss 31 on the turbine 4 side by welding.
- the inner peripheral end surface of the piston 30 is slidably supported on the outer peripheral surface of the boss 31.
- a seal member 36 is provided on the outer peripheral surface of the boss 31, and the seal member 36 is in contact with the inner peripheral end surface of the piston 30.
- the second oil chamber L2 is provided with a disc spring 40 as a return spring for separating the piston 30 from the clutch plate 28. Further, a resin stopper 41 is provided on the end surface of the boss 31 on the turbine 4 side. The turbine hub 16 can come into contact with the stopper 41.
- the oil chamber component 30a, the oil chamber plate 29, and the front cover 2 constitute the first oil chamber L1 for lockup on the turbine 4 side of the piston 30 and the front cover 2 side of the piston 30 on the front cover 2 side.
- a second oil chamber L2 for unlocking is configured.
- the boss 31 is formed with a plurality of first oil passages 51, a plurality of second oil passages 52, and a single third oil passage 53.
- the first oil passage 51 is formed so as to penetrate the boss 31 in the radial direction, and communicates the inner peripheral side of the boss 31 with the first oil chamber L1.
- the second oil passage 52 is formed so as to penetrate the boss 31 in the radial direction, and communicates the inner peripheral side of the boss 31 with the second oil chamber L2.
- the third oil passage 53 is formed so as to penetrate through the end surface on the front cover 2 side and the end surface on the turbine 4 side of the boss 31, and an oil passage for supplying hydraulic oil to the second oil chamber L ⁇ b> 2 and the torque converter. And communicate with.
- the damper mechanism 25 includes an output plate 55 fixed to the turbine shell 14, a plurality of torsion springs 56, and a plurality of intermediate members 57.
- FIG. 4 shows only the damper mechanism 25 of the lockup device 6 and the configuration related thereto extracted.
- the output plate 55 has a main body portion 55a, a plurality of engaging portions 55b, an axial contact portion 55c, and a fixing portion 55d.
- the main body portion 55 a has a shape along the outer periphery of the turbine shell 14.
- the plurality of engaging portions 55b are formed by bending the outer peripheral tip portion of the main body portion 55a to the front cover 2 side.
- the plurality of engaging portions 45b engage with both ends in the circumferential direction of one set (two in this embodiment) of torsion springs 46 acting in series.
- the axial contact portion 55c is formed on the inner peripheral portion of the main body portion 55a, and sandwiches the axial contact portion 27e of the clutch output member 27 together with the axial contact portion 16d of the turbine hub 16 as described above. It is out.
- the fixed portion 55d is formed on the further inner peripheral side of the axial contact portion 55c in a step difference from the axial contact portion 55c in the axial direction.
- the fixing portion 55 d is fixed to the turbine hub 16 and the turbine shell 14 by rivets 17.
- Each of the plurality of intermediate members 57 is a member for causing one set (two) of torsion springs of the plurality of torsion springs 56 to act in series.
- the intermediate member 57 is an annular member having a substantially C-shaped cross section, and includes an engaging portion 57a, a cover portion 57b, and a protruding portion 57c.
- the engaging portion 57a is disposed between two torsion springs acting in series, and is engaged with an end face of an adjacent torsion spring.
- the cover part 57b covers the outer periphery of the torsion spring 56 and the side part of the torsion spring 56 on the front cover 2 side.
- the protrusion 57c is formed at a part of the inner peripheral end of the intermediate member 57, and is disposed so as to be sandwiched between the disc portion 27a of the clutch output member 27 and the axial positioning portion 27g. . Further, the inner peripheral end surface of the protrusion 47 c can be brought into contact with the radial positioning portion 27 f of the clutch output member 27.
- the intermediate member 57 regulates the radial and axial movement of the torsion spring 56 by the cover portion 57b. Further, the intermediate member 57 is positioned in the axial direction and the radial direction by the plurality of protrusions 57c being supported by the radial positioning portion 27f and the axial positioning portion 27g of the clutch output member 27.
- the protrusion part 57c is formed in the width
- the intermediate member 57 is set at a position where the projection 57c passes between the plurality of axial positioning portions 27g of the clutch output member 27. Then, the projection 57c is passed between the plurality of axial positioning portions 27g, and then the intermediate member 57 is rotated by a predetermined angle. Thereby, the intermediate member 57 is fixed at a position as shown in the figure.
- the lockup first oil chamber L ⁇ b> 1 is connected to the drain via the first oil passage 51, and a second oil passage 52 is connected from a control valve (not shown).
- the hydraulic oil is supplied to the second oil chamber L2 for releasing the lockup between the piston 30 and the front cover 2 via the.
- the piston 30 moves toward the turbine 4, and the pressing portion 30 b of the piston 30 is separated from the clutch plate 28.
- oil for operating the torque converter is supplied from between the input shaft 18 and the fixed shaft 23 of the transmission.
- This hydraulic oil is supplied between the turbine hub 16 and the piston 30 through the through hole 16 f of the turbine hub 4.
- This hydraulic oil is guided to the outer peripheral end portion of the front cover 2 through a gap formed between the front cover 2 and the clutch output member 27 and the intermediate member 57.
- the torque converter body is supplied.
- the hydraulic oil in the torque converter body flows through a control valve (not shown) through an oil passage between the stator shell 20 and the impeller shell 10.
- the torque from the front cover 2 is transmitted from the impeller 2 to the turbine 4 via the hydraulic oil, and further transmitted to the input shaft 18 of the transmission.
- the second oil chamber L2 for releasing the lockup is connected to the drain via the second oil passage 52 and the first oil passage.
- the hydraulic oil is supplied to the first oil chamber L 1 between the piston 30 and the oil chamber plate 29 via 51.
- the piston 30 moves to the front cover 2 side, and the clutch plate 28 is pressed between the front cover 2 and the piston 30.
- the torque input from the clutch output member 27 is transmitted to the turbine 4 via the torsion spring 56 and the output plate 55, and further transmitted to the transmission input shaft 18 via the turbine hub 16.
- the hydraulic oil for the torque converter is supplied to the second oil chamber L2 via the third oil passage 53. Therefore, centrifugal force acts on this hydraulic oil, and the movement of the piston 30 toward the clutch plate 28 is cancelled.
- a first oil chamber L1 for lockup is formed between the front cover 2 and the turbine 4, and the piston 30 moves from the turbine 4 side to the front cover 2 side and enters a lockup state. Therefore, the axial dimension can be shortened as compared with the conventional lockup device.
- an oil chamber for unlocking can be configured with a small number of parts, and the axial dimension can be further shortened.
- the clutch output member 27 is provided with the clutch engaging portion 27b and the damper engaging portion 27c, the power transmission path can be configured with a small number of parts. Further, the axial output portion 27e and the radial direction contact portion 27d of the clutch output member 27 are brought into contact with the axial direction support portion 16d and the radial direction support portion 16e of the turbine hub 16, so that the clutch output member 27 can be easily formed. The positioning in the axial direction and the radial direction can be performed. For this reason, the configuration for positioning the clutch output member 27 can be simplified.
- the clutch output member 27 is provided with a radial positioning portion 27f and an axial positioning portion 27g to position the intermediate member 57 in the radial direction and the axial direction. Therefore, the configuration for positioning the intermediate member 57 can be simplified.
- the third oil passage 53 Since the third oil passage 53 is provided, even when the hydraulic oil is not supplied to the second oil chamber L2 for releasing the lockup when the lockup is released, the third oil passage 53 acts on the hydraulic oil in the first oil chamber L1. It is possible to suppress drag torque from being generated due to the centrifugal force.
- the axial dimension of the clutch portion can be particularly shortened.
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- Engineering & Computer Science (AREA)
- General Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- Mechanical Operated Clutches (AREA)
- Control Of Fluid Gearings (AREA)
Abstract
Description
図1は本発明の一実施形態が採用されたトルクコンバータ1の縦断面図である。トルクコンバータ1は、エンジンのクランクシャフトからトランスミッションの入力シャフトにトルクを伝達するための装置である。図1の左側に図示しないエンジンが配置され、図1の右側に図示しないトランスミッションが配置されている。図1に示すO-Oがトルクコンバータ1の回転軸である。
フロントカバー2は、円板状の部材であって、内周端にはセンターボス8が溶接により固定されている。センターボス8は、軸方向に延びる円筒形状の部材であり、クランクシャフト(図示せず)の中心孔内に挿入されるものである。
インペラ3は、主に、インペラシェル10と、その内側に固定された複数のインペラブレード11と、から構成されている。そして、インペラシェル10の外周側先端部が、前述のように、フロントカバー2に溶接されている。なお、インペラハブ10の内周端部には、トランスミッション側に延びる筒状部10aが形成されている。
タービン4はインペラ3に対して軸方向に対向して配置されている。タービン4は、主に、タービンシェル14と、その内部に固定された複数のタービンブレード15と、タービンシェル14の内周端部に固定されたタービンハブ16と、から構成されている。タービンシェル14とタービンハブ16とは複数のリベット17によって固定されている。
ステータ5は、インペラ3の内周部とタービン4の内周部との間に配置され、タービン4からインペラ3に戻る作動油の流れを整流するための機構である。ステータ5は樹脂やアルミ合金等で鋳造により一体に形成されている。ステータ5は、主に、環状のステータシェル20と、ステータシェル20の外周面に設けられた複数のステータブレード21と、を有している。ステータシェル20は、ワンウェイクラッチ22を介して固定シャフト23に連結されている。
ロックアップ装置6は、フロントカバー2とタービン4との間に配置され、フロントカバー2からタービン4に動力を直接伝達するものである。このロックアップ装置6は、フロントカバー2とタービン4との間に配置されたクラッチ部24と、クラッチ部24からのトルクをタービン4に伝達するダンパ機構25と、を備えている。
クラッチ部24は、フロントカバー2からのトルクをダンパ機構25に伝達し、あるいはフロントカバー2とダンパ機構25との間のトルク伝達を遮断する。このクラッチ部24は、図2に拡大して示すように、クラッチ出力部材27と、クラッチプレート28と、油室プレート29と、ピストン30と、ボス31と、を有している。
以上のように、油室構成部30aと油室プレート29及びフロントカバー2とによって、ピストン30のタービン4側にロックアップ用の第1油室L1が構成され、ピストン30のフロントカバー2側にロックアップ解除用の第2油室L2が構成されている。
ダンパ機構25は、図4に示すように、タービンシェル14に固定された出力プレート55と、複数のトーションスプリング56と、複数の中間部材57と、を有している。なお、図4は、ロックアップ装置6のうちのダンパ機構25及びそれに関連する構成のみを抽出して示したものである。
ロックアップ装置6において、ロックアップを解除する場合には、ロックアップ用の第1油室L1が第1油路51を介してドレンに接続されるとともに、図示しないコントロールバルブから第2油路52を介してピストン30とフロントカバー2との間のロックアップ解除用の第2油室L2に作動油が供給される。これにより、ピストン30はタービン4側に移動し、ピストン30の押圧部30bはクラッチプレート28から離れる。
(1)フロントカバー2とタービン4との間にロックアップ用の第1油室L1が形成され、ピストン30はタービン4側からフロントカバー2側に移動してロックアップ状態になる。したがって、従来のロックアップ装置に比較して、軸方向寸法を短縮することができる。
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。
2 フロントカバー
4 タービン
6 ロックアップ装置
14 タービンシェル
15 タービンハブ
16 タービンハブ
16a フランジ部
16d 軸方向支持部
16e 径方向支持部
24 クラッチ部
25 ダンパ機構
27 クラッチ出力部材
27b クラッチ係合部
27c ダンパ係合部
27d 径方向当接部
27e 軸方向当接部
27f 径方向位置決め部
27g 軸方向位置決め部
28 クラッチプレート
29 油室プレート
30 ピストン
31 ボス
51~53 油路
55 出力プレート
56 トーションスプリング
57 中間部材
57a スプリング係合部
57b カバー部
57c 突起部
L1 ロックアップ用第1油室
L2 ロックアップ解除用第2油室
Claims (6)
- フロントカバーからのトルクをトルクコンバータのタービンを介してトランスミッション側の部材に伝達するためのトルクコンバータのロックアップ装置であって、
前記フロントカバーと前記タービンとの間に配置され、トルクを伝達あるいは遮断するためのクラッチ部と、
前記クラッチ部からのトルクを前記タービンに伝達するとともに、捩り振動を吸収・減衰するダンパ機構と、
を備え、
前記クラッチ部は、
前記ダンパ機構にトルクを出力するクラッチ出力部材と、
前記フロントカバーと前記クラッチ出力部材との間でトルク伝達を行うためのクラッチプレートと、
前記フロントカバーと前記タービン内周部との間に前記フロントカバーに対して軸方向移動不能に設けられた円板状の油室プレートと、
前記フロントカバーと前記油室プレートとの間に軸方向移動自在に設けられ、前記油室プレートとの間にロックアップ用の第1油室を構成するとともに、前記フロントカバーとの間にロックアップ解除用の第2油室を構成し、前記第1油室に供給される作動油によって前記クラッチ部を係合状態にするピストンと、
を有する、
トルクコンバータのロックアップ装置。 - 前記クラッチ部は軸方向に延びる環状のボスをさらに有し、
前記環状のボスは、前記トランスミッション側の端部に前記油室プレートの内周部が固定されるとともに、前記フロントカバー側の端面が前記フロントカバーに固定され、外周面を前記ピストンが軸方向に摺動し、前記第1油室に作動油を供給するための油路が形成されている、
請求項1に記載のトルクコンバータのロックアップ装置。 - 前記タービンは、複数のタービンブレードと、前記複数のタービンブレードを支持するタービンシェルと、タービンシェルが連結されたタービンハブと、を有し、
前記タービンハブは、径方向に延び前記タービンシェルの内周部が連結されたフランジ部を有し、前記フランジ部は、外周部に形成された軸方向支持部と、前記軸方向支持部の外周端部から前記フロントカバー側に延び筒状に形成された径方向支持部と、を有し、
前記クラッチ出力部材は、
径方向中間部に前記フロントカバー側に延びて形成され、前記クラッチプレートに軸方向移動自在にかつ相対回転不能に係合するクラッチ係合部と、
外周部に形成され、前記ダンパ機構に係合するダンパ係合部と、
内周部において軸方向に延びる筒状に形成され、前記タービンハブの径方向支持部に当接する径方向当接部と、
前記径方向当接部から内周側に突出し、前記タービンハブの軸方向支持部に当接する軸方向当接部と、
を有する、
請求項1又は2に記載のトルクコンバータのロックアップ装置。 - 前記ダンパ機構は、
前記クラッチ出力部材と係合する複数のトーションスプリングと、
前記クラッチ出力部材と相対回転自在に配置され、前記複数のトーションスプリングのうちの少なくとも2つを直列に作用させるための中間部材と、
を有し、
前記中間部材は
前記トーションスプリングの端面に係合するスプリング係合部と、
前記トーションスプリングの外周及び前記フロントカバー側の側部を覆うカバー部と、
前記カバー部から内周側に延びる複数の突起部と、
を有し、
前記クラッチ出力部材は、前記クラッチ係合部の上方でかつ前記ダンパ係合部の下方において、前記中間部材の複数の突起部に当接して前記中間部材の位置決めを行う位置決め部を有している、
請求項3に記載のトルクコンバータのロックアップ装置。 - 前記クラッチ出力部材の位置決め部は、
前記中間部材の内周端面と当接して前記中間部材を径方向に位置決めする径方向位置決め部と、
前記中間部材の複数の突起部の側面に当接して前記中間部材を軸方向に位置決めする軸方向位置決め部と、
を有する、
請求項4に記載のトルクコンバータのロックアップ装置。 - 前記環状ボスには、前記ロックアップ解除用の第2油室に作動油を供給するための油路が形成されている、請求項2に記載のトルクコンバータのロックアップ装置。
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CN106461046B (zh) * | 2014-05-07 | 2019-09-24 | 舍弗勒技术股份两合公司 | 用于定位毂的定中柱 |
DE112015003280B4 (de) | 2014-07-16 | 2024-06-27 | Schaeffler Technologies AG & Co. KG | Drehmomentwandlerkupplung mit verringertem Gegendruck |
JP2016044778A (ja) * | 2014-08-25 | 2016-04-04 | マツダ株式会社 | 流体伝動装置 |
US20180106351A1 (en) * | 2015-05-20 | 2018-04-19 | Exedy Corporation | Lock-up device for torque converter |
US10408322B2 (en) | 2015-05-20 | 2019-09-10 | Exedy Corporation | Lock-up device for torque converter |
US10571005B2 (en) | 2015-05-20 | 2020-02-25 | Exedy Corporation | Lock-up device for torque converter |
CN107923505A (zh) * | 2015-08-19 | 2018-04-17 | 株式会社艾科赛迪 | 液力变矩器的锁定装置 |
US20180163837A1 (en) * | 2015-08-19 | 2018-06-14 | Exedy Corporation | Lock-up device for torque converter |
Also Published As
Publication number | Publication date |
---|---|
US9303747B2 (en) | 2016-04-05 |
CN104204616A (zh) | 2014-12-10 |
US20150008086A1 (en) | 2015-01-08 |
KR102017093B1 (ko) | 2019-10-21 |
JP2013217452A (ja) | 2013-10-24 |
DE112013002023T5 (de) | 2015-03-12 |
JP5584249B2 (ja) | 2014-09-03 |
CN104204616B (zh) | 2017-03-01 |
KR20140144678A (ko) | 2014-12-19 |
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