WO2016186126A1 - 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
- WO2016186126A1 WO2016186126A1 PCT/JP2016/064707 JP2016064707W WO2016186126A1 WO 2016186126 A1 WO2016186126 A1 WO 2016186126A1 JP 2016064707 W JP2016064707 W JP 2016064707W WO 2016186126 A1 WO2016186126 A1 WO 2016186126A1
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- WO
- WIPO (PCT)
- Prior art keywords
- piston
- oil chamber
- front cover
- plate
- turbine
- 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
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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
- F16H41/00—Rotary fluid gearing of the hydrokinetic type
- F16H41/24—Details
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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
- F16H2045/0205—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
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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
- F16H2045/021—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
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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
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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 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 disclosed in Patent Document 1 includes a clutch portion disposed between the front cover and the turbine, and a damper disposed between the clutch portion and the turbine.
- the clutch part has a clutch disc pressed against a friction surface formed on the front cover, a piston, and a clutch output member.
- a lockup oil chamber and a cancel oil chamber are formed on both sides of the piston. Then, by supplying hydraulic oil to these oil chambers or by draining the hydraulic oil in these oil chambers, the piston moves in the axial direction, and lock-up on (power transmission state) or lock-up off ( The power transmission is released.
- a boss and an oil chamber plate are provided in order to form an oil chamber for lockup.
- the boss is fixed to the inner peripheral portion of the front cover, and the oil chamber plate is fixed to the outer peripheral surface of the boss.
- the piston is slidably supported on the outer peripheral surface of the boss, and a seal member is disposed between the inner peripheral end surface of the piston and the outer peripheral surface of the boss.
- a torque converter lockup device is a device for transmitting torque from a front cover to a member on a transmission side through a turbine of the torque converter.
- This lock-up device includes a clutch disk, a piston, an annular oil chamber plate, an annular support boss, and a first seal member.
- the clutch disk is disposed between the front cover and the turbine.
- the piston is disposed between the front cover and the turbine and is movable in the axial direction.
- the oil chamber plate is disposed between the piston and the turbine, and forms a first oil chamber to which hydraulic oil is supplied between the oil chamber plate.
- the support boss is fixed to the inner peripheral portion of the front cover, and has a piston support portion, a welded portion, and an intermediate portion.
- the piston support portion has a first diameter and slidably supports the inner peripheral end surface of the piston.
- the welded portion has a second diameter different from the first diameter, and the inner peripheral portion of the oil chamber plate is welded.
- the intermediate portion is formed with an intermediate diameter between the first diameter and the second diameter between the piston support portion and the welded portion, and an opening for supplying hydraulic oil to the first oil chamber is formed.
- the first seal member is attached to the piston support portion.
- it further includes a second seal member that is attached to the outer peripheral portion of the piston and forms a first oil chamber with the oil chamber plate.
- the piston is quickly operated to improve the responsiveness of the lockup. be able to.
- annular pressure plate is further provided between the piston and the clutch disc so as to be movable in the axial direction and press-contacting the clutch disc by the pressing force of the piston.
- the entire clutch disc can be pressed uniformly. For this reason, local wear of the clutch disk can be suppressed.
- the torque from the front cover is transmitted from the oil chamber plate to the pressure plate, and from the pressure plate to the clutch disc.
- route between the engaging part for torque transmission and a front cover becomes still longer, and the rattling sound in an engaging part becomes difficult to be transmitted with respect to a front cover. Therefore, the rattling noise that leaks to the outside can be further suppressed.
- this device further includes a damper mechanism that transmits torque from the clutch disk to the turbine and absorbs and attenuates torsional vibration.
- FIG. 6 is a plan sectional view showing a return mechanism.
- the torque converter 1 mainly includes a front cover 2, a torque converter main body 6 including three kinds of impellers (impeller 3, turbine 4, and stator 5), and a lockup device 7.
- 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.
- 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 in the fluid chamber.
- 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 stator 5 is a mechanism for rectifying the flow of hydraulic oil that is disposed between the inner peripheral portion of 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 integrally formed by casting with resin, aluminum alloy or the like.
- the stator 5 mainly has a disk-shaped stator shell 20 and a plurality of stator blades 21 formed integrally with the stator shell 20 on the outer peripheral side of the stator shell 20.
- the stator shell 20 is connected to a fixed shaft (not shown) via a one-way clutch 22.
- Thrust bearings 23 and 24 are disposed 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 7 is disposed between the front cover 2 and the turbine 4 and directly transmits power from the front cover 2 to the turbine 4. As shown in an enlarged view in FIG. 2, the lockup device 7 includes a clutch disk 28, a pressure plate 29, a piston 30, a piston operating mechanism 31, and a damper mechanism 34.
- the clutch disk 28 is formed in an annular shape and can be pressed against the friction surface 2 b of the front cover 2.
- the clutch disk 28 includes an annular core plate 36 and annular friction members 37 fixed to both side surfaces of the core plate 36.
- the outer peripheral portion of the core plate 36 is larger than the outer diameter of the friction member 37, and a portion protruding from the friction member 37 to the outer peripheral side is bent at a predetermined angle toward the turbine side.
- a plurality of engaging protrusions 36a are formed at the bent portion.
- the clutch disk 28 is formed so as to be inclined in a free state of lock-up off (release of power transmission). Specifically, the inner peripheral side of the clutch disk 28 is inclined so as to be positioned on the front cover 2 side as compared with the outer peripheral side. For this reason, in the lock-up-off state, the inner peripheral end of the clutch disc 28 makes an annular line contact with the friction surface 2 b of the front cover 2, and the outer peripheral end of the clutch disc 28 makes an annular line with the pressure plate 29. Contact. With such a configuration, the drag torque is reduced in the lock-up off state.
- the pressure plate 29 is disposed between the clutch disk 28 and the piston 30 so as to be movable in the axial direction.
- the pressure plate 29 is pressed by the piston 30 to press the clutch disk 28 toward the front cover 2.
- the pressure plate 29 is formed in an annular shape, and has an outer diameter larger than the outer diameter of the friction member 37 of the clutch disk 28 and an inner diameter smaller than the inner diameter of the friction member 37.
- a plurality of grooves 29 a are formed at predetermined intervals in the circumferential direction at the inner peripheral end of the pressure plate 29.
- Each groove 29a has a predetermined depth in the radial direction and is open on the inner peripheral side.
- FIG. 4 is a view of the pressure plate 29 as viewed from the front cover 2 side.
- the piston 30 is disposed between the front cover 2 and the turbine 4 and is movable in the axial direction.
- the piston 30 has a disk-shaped pressure receiving portion 30a, a first protruding portion 30b, a second protruding portion 30c, and an outer peripheral disk portion 30d.
- the main body is formed by the pressure receiving portion 30a and the outer peripheral disc portion 30d.
- the pressure receiving part 30a is a part that receives the pressure of the hydraulic oil, and the first protruding part 30b is formed on the outer periphery of the pressure receiving part 30a so as to protrude toward the turbine 4 side.
- the outer peripheral end portion of the pressure receiving portion 30a is inclined and extends toward the front cover 2, and the second protruding portion 30c is formed to protrude further toward the front cover 2 at the tip of the inclined and extended portion. .
- the outer peripheral disc portion 30d is integrated with the pressure receiving portion 30a and is offset to the front cover side with respect to the pressure receiving portion 30a. As shown in FIG. 5, a plurality of openings 30e are formed at predetermined intervals in the circumferential direction on the inner peripheral portion of the outer peripheral disc portion 30d. The plurality of openings 30e penetrates in the axial direction.
- FIG. 5 is a view of the piston 30 as viewed from the front cover 2 side.
- annular pressing portion 30f is formed at the outer peripheral end of the outer peripheral disc portion 30d.
- the pressing portion 30f is formed at the outer peripheral end portion of the outer peripheral disc portion 30d so as to protrude toward the front cover 2 side.
- the pressing portion 30f is formed so as to abut on a substantially central portion of the pressure plate 29 in the radial direction.
- the pressing portion 30f preferably presses a region between 20% on the inner peripheral side and 10% on the outer peripheral side from the central position of the radial width of the friction member 37 via the pressure plate 29.
- ⁇ Rigidity of core plate 36, pressure plate 29, and piston 30> The bending rigidity of the core plate 36, the pressure plate 29, and the piston 30 is set to be the highest for the piston 30, the pressure plate 29 is lower than the piston 30, and the core plate 36 is set to the lowest.
- the core plate 36, the pressure plate 29, and the piston 30 have the specifications as described above, when the front cover 2 (particularly the portion where the friction surface 2b is formed) is deformed, the pressure plate 29 and the clutch disk are moved by the piston 30. When the pressure 28 is pressed, the pressure plate 29 and the clutch disk 28 are deformed following the deformation of the front cover 2.
- the supporting boss 40 is fixed to the inner peripheral portion of the front cover 2 as shown in FIGS. 2 and 6.
- the support boss 40 is a part of the center boss 8 and is formed in a cylindrical shape extending in the axial direction from the end of the center boss 8 on the turbine 4 side.
- the support boss 40 includes a first fixing portion 40a, a piston support portion 40b, a second fixing portion 40c, a first intermediate portion 40d, and a second intermediate portion 40e.
- FIG. 6 is an enlarged partial view of FIG.
- the piston support part 40b is formed with an outer diameter larger than the outer diameter of the first fixed part 40a.
- the inner peripheral end surface of the piston 30 is slidably supported on the outer peripheral surface of the piston support portion 40b.
- a seal member 45 is attached to the outer peripheral surface of the piston support portion 40b. The seal member 45 seals between the outer peripheral surface of the piston support portion 40 b and the inner peripheral end surface of the piston 30.
- the side surface on the front cover 2 side of the piston support portion 40b is inclined so as to be separated from the front cover 2 as it goes to the inner peripheral side.
- the outer diameter of the second fixing portion 40c is smaller than the outer diameter of the piston support portion 40b. That is, the piston support portion 40b and the second fixing portion 40c are stepped.
- the inner peripheral end surface of the cover plate 41 is fixed to the outer peripheral surface of the second fixing portion 40c by welding. Even when the cover plate 41 is welded to the second fixed portion 40c by making the outer diameter of the second fixed portion 40c smaller than the outer diameter of the piston support portion 40b to which the seal member 45 is attached, the piston by welding is also used.
- the distortion of the support part 40b can be suppressed. Therefore, the sealing performance between the piston support portion 40b and the piston 30 is improved.
- the first intermediate portion 40d is formed between the first fixed portion 40a and the piston support portion 40b.
- the outer peripheral surface of the first intermediate portion 40d is inclined so that its diameter increases from the front cover 2 side toward the turbine 4 side.
- the minimum diameter of the outer peripheral surface of the first intermediate portion 40d is larger than the diameter of the first fixed portion 40a, and the maximum diameter is smaller than the diameter of the piston support portion 40b.
- the second intermediate portion 40e is formed between the piston support portion 40b and the second fixing portion 40c.
- the outer peripheral surface of the second intermediate portion 40e is inclined so that the diameter decreases from the front cover 2 side toward the turbine 4 side.
- the maximum diameter of the outer peripheral surface of the second intermediate portion 40e is smaller than the diameter of the piston support portion 40b, and the minimum diameter is larger than the diameter of the second fixed portion 40c.
- a thrust washer 46 is arranged between the end face of the supporting boss 40 on the turbine 4 side and the turbine hub 16. A groove in the radial direction is formed on the surface of the thrust washer 46.
- the torque transmission part 41c is formed further on the outer peripheral side of the seal part 41b.
- the torque transmission part 41c is a plurality of engagement protrusions (hereinafter referred to as “engagement protrusions 41c”) extending from the outer periphery of the seal part 41b to the front cover side.
- engagement protrusions 41c As shown in FIGS. 4 and 5, the engagement protrusion 41 c passes through an opening 30 e formed in the piston 30 and engages with a groove 29 a formed in the inner peripheral end portion of the pressure plate 29.
- FIG. 7 shows a perspective view of the cover plate 41 and the piston 30 as viewed from the turbine 4 side.
- the torque transmitted to the cover plate 41 can be transmitted to the pressure plate 29. Further, the relative rotation of the piston 30 with respect to the cover plate 41 is restricted by appropriately setting the circumferential dimension of the engagement protrusion 41c as the torque transmitting portion and the circumferential dimension of the opening 30e of the piston 30. be able to.
- FIGS. 2 and 8 the return mechanism 42 is disposed between the front cover 2 and the piston 30.
- FIG. 8 is a plan cross-sectional view of a portion where the front cover 2 and the return mechanism 42 of the piston 30 are disposed, as viewed from the outer peripheral side.
- the return mechanism 42 is disposed between a recess 2g formed on the side surface of the front cover 2 on the piston 30 side and a recess 30g formed on the side surface of the piston 30 on the front cover 2 side.
- the return mechanism 42 is a mechanism that urges the piston 30 in a direction away from the friction surface of the front cover 2.
- the return mechanism 42 urges the piston 30 in a direction away from the front cover 2, and the friction surface 2 b of the front cover 2 and the piston 30.
- the gap with the pressing portion 30f is adjusted.
- the return mechanism 42 includes a bimetal return spring 50 and a cam mechanism 51.
- the return spring 50 is disposed so as to extend in the left-right direction between the support member 52 fixed to the front cover 2 and one end of the cam mechanism 51.
- the return spring 50 is deformed so that the spring length becomes short as shown in FIG.
- the return spring 50 is deformed so that the spring length becomes longer as shown in FIG.
- the cam mechanism 51 includes a first cam member 55 fixed to the concave portion 2g of the front cover 2 and a second cam member 56 fixed to the concave portion 30g of the piston 30.
- the first cam member 55 is a block-like member extending in the left-right direction, and includes a first inclined surface 55a, a groove 55b, and a second inclined surface 55c.
- the first inclined surface 55a is formed on the outer peripheral surface of one end portion of the first cam member 55, and is inclined so that the thickness decreases from one end to the other end.
- the groove 55b is formed with a predetermined width on the other end side of the first inclined surface 55a and penetrates in the radial direction.
- the second inclined surface 55c is formed on the inner peripheral surface of the protrusion formed so as to cover a part of the other end side of the groove 55b.
- the second inclined surface 55c is inclined in the same direction as the first inclined surface 55a.
- One end of the return spring 50 is fixed to the other end surface of the first cam member 55.
- the second cam member 56 is a block-like member extending in the left-right direction, and includes a first inclined surface 56a, an engaging portion 56b, and a second inclined surface 56c.
- the engaging portion 56 b is a portion of the second cam member 56 that protrudes toward the first cam member 55, and can be inserted into the groove 55 b of the first cam member 55.
- the first inclined surface 56a is formed on the first cam member 55 side of the engaging portion 56b, and is inclined at the same angle in the same direction as the first inclined surface 55a of the first cam member 55.
- the first inclined surfaces 55a and 56a of the cam members 55 and 56 are slidable while being in contact with each other.
- the second inclined surface 56c is formed on the opposite side to the first inclined surface 56a of the engaging portion 56b, and is inclined at the same angle in the same direction as the second inclined surface 55c of the first cam member 55. Yes. And the 2nd inclined surfaces 55c and 56c of both the cam members 55 and 56 contact
- a lockup oil chamber C ⁇ b> 1 is formed between the pressure receiving portion 30 a of the piston 30 and the main body portion 41 a of the cover plate 41, as shown in FIG. 2.
- a cylindrical stepped portion 2c extending in the axial direction is formed between the radial intermediate portion and the inner peripheral portion of the front cover 2, and a seal member is provided on the outer peripheral surface of the stepped portion 2c. 57 is attached. The seal member 57 is in contact with the inner peripheral surface of the second protrusion 30c of the piston 30. Therefore, a canceling oil chamber C2 is formed between the pressure receiving portion 30a of the piston 30 and the front cover 2 for canceling the hydraulic pressure generated in the lockup oil chamber C1 when the lockup is turned off.
- the damper mechanism 34 is disposed between the clutch disk 28 and the turbine 4 and transmits torque from the clutch disk 28 to the turbine 4. As shown in FIG. 9, the damper mechanism 34 includes an engaging member 60, a drive plate 61, a driven plate 62, and a plurality of torsion springs 63.
- the engaging member 60 includes a fixed portion 60a and a plurality of first engaging portions 60b and second engaging portions 60c.
- the fixing portion 60 a is formed in an annular shape and is fixed to the drive plate 61 by rivets 65.
- the plurality of first engaging portions 60 b are formed by bending the outer peripheral end of the fixed portion 60 a toward the front cover 2, and mesh with engaging protrusions 36 a formed on the outer periphery of the core plate 36 of the clutch disk 28. .
- the clutch disk 28 is movable in the axial direction with respect to the first engagement portion 60b, and relative rotation is prohibited.
- the plurality of second engaging portions 60c are formed by bending the outer peripheral end of the fixed portion 60a to the turbine 4 side.
- the inner peripheral end surface of the disc part 61a is bent toward the turbine 4 to form a positioning part 61d.
- the positioning portion 61d is supported by a support portion 16c formed on the outer peripheral end portion of the turbine hub 16, and is positioned in the radial direction and the axial direction.
- a hole 61e penetrating in the axial direction is formed in the outer peripheral portion of the disc portion 61a.
- the second engagement portion 60c of the engagement member 60 passes through the hole 61e and extends toward the turbine 4 side.
- the support portion 61b is formed on the outer peripheral portion of the disc portion 61a and has a C-shaped cross section.
- a plurality of torsion springs 63 are accommodated in the support part 61b, and the movement of the torsion springs 63 in the radial direction and the front cover 2 side is restricted by the support part 61b.
- the engaging portion 61c is formed between the adjacent support portions 61b on the outer peripheral portion of the disc portion 61a. Part of the engaging part 61c is engaged with both end faces of the torsion spring 63 accommodated in the support part 61b.
- the driven plate 62 is formed in a substantially disc shape and is disposed between the drive plate 61 and the turbine 4.
- the driven plate 62 transmits the torque transmitted to the torsion spring 63 to the turbine hub 16.
- An inner peripheral end of the driven plate 62 is fixed to the turbine shell 14 and the turbine hub 16 by a rivet 17.
- the driven plate 62 extends to the outer peripheral side along the side surface of the turbine shell 14, and engaging portions 62 a formed on the outer peripheral portion are engaged with both end surfaces of the torsion spring 63.
- the leakage amount from the seal member 57 is set to be larger than the normal leakage amount. For this reason, the hydraulic oil leaking from the seal member 57 enters the canceling oil chamber C2, and the movement of the piston 30 toward the front cover 2 is suppressed. That is, the pressing force applied to the piston 30 due to the centrifugal force of the working oil in the lockup oil chamber C1 is canceled by the working oil leaking from the seal member 57 to the canceling oil chamber C2.
- the torque from the front cover 2 is a damper through the path of the supporting boss 40 ⁇ the cover plate 41 ⁇ the pressure plate 29 ⁇ the clutch disk 28 and from the front cover 2 through the clutch disk 28. It is transmitted to the mechanism 34.
- the torque input to the engagement member 60 is transmitted to the turbine 4 via the torsion spring 63 and the driven plate 62, and further transmitted to the input shaft of the transmission via the turbine hub 16.
- the inner peripheral side of the front cover 2 may be deformed so as to expand compared to the outer peripheral side due to the pressure of hydraulic oil or centrifugal force.
- the clutch disk 28 is pressed in a state where the front cover 2 (particularly the friction surface 2b) is deformed, the entire surface of the clutch disk 28 does not contact but locally contacts, and the clutch disk 28 may be abnormally worn.
- the clutch portion is configured by the clutch disk 28.
- a friction member may be fixed to the side surface of the pressure plate, and the friction member may be pressed against the friction surface 2b of the front cover 2.
- the clutch disk can be omitted.
- a return mechanism for separating the piston from the front cover may be disposed between the piston and the cover plate.
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- Engineering & Computer Science (AREA)
- General Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- Hydraulic Clutches, Magnetic Clutches, Fluid Clutches, And Fluid Joints (AREA)
- Mechanical Operated Clutches (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、内周端にはセンタボス8が溶接により固定されている。センタボス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、インペラシェル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が形成されている。
タービン4は流体室内でインペラ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、円板状のステータシェル20と、ステータシェル20の外周側にステータシェル20と一体で形成さ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(図示せず)に連結されている。
ロックアップ装置7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7は、図2に拡大して示すように、クラッチディスク28と、プレッシャプレート29と、ピストン30と、ピストン作動機構31と、ダンパ機構34と、を有している。
クラッチディスク28は、環状に形成されており、フロントカバー2の摩擦面2bに圧接可能である。クラッチディスク28は、環状のコアプレート36と、コアプレート36の両側面に固定された環状の摩擦部材37と、を有している。コアプレート36の外周部は、摩擦部材37の外径よりも大きく、摩擦部材37から外周側に突出した部分がタービン側に所定の角度で折り曲げられている。そして、この折曲げ部分に、複数の係合突起36aが形成されている。
プレッシャプレート29は、クラッチディスク28とピストン30との間に軸方向に移動自在に配置されている。プレッシャプレート29は、ピストン30により押圧されて、クラッチディスク28をフロントカバー2側に押圧する。また、プレッシャプレート29は、環状に形成されており、外径はクラッチディスク28の摩擦部材37の外径よりも大きく、内径は摩擦部材37の内径より小さい。プレッシャプレート29の内周端部には、図4に拡大して示すように、円周方向に所定の間隔で複数の溝29aが形成されている。各溝29aは、径方向に所定の深さを有し、内周側が開口している。なお、図4はプレッシャプレート29をフロントカバー2側から視た図である。
ピストン30は、図1及び図2に示すように、フロントカバー2とタービン4との間に配置され、軸方向に移動自在である。ピストン30は、円板状の受圧部30aと、第1突出部30bと、第2突出部30cと、外周円板部30dと、を有している。なお、受圧部30aと外周円板部30dによって本体部が形成されている。
コアプレート36、プレッシャプレート29、及びピストン30の曲げ剛性は、ピストン30が最も高く、プレッシャプレート29はピストン30より低く、コアプレート36は最も低く設定されている。
ピストン30は、ピストン作動機構31によって軸方向に作動する。図2に示すように、ピストン作動機構31は、支持用ボス40と、カバープレート(油室プレート)41と、リターン機構42と、を有している。
支持用ボス40は、図2及び図6に示すように、フロントカバー2の内周部に固定されている。具体的には、支持用ボス40は、センタボス8の一部であり、センタボス8のタービン4側端部から軸方向に延びる筒状に形成されている。支持用ボス40は、第1固定部40aと、ピストン支持部40bと、第2固定部40cと、第1中間部40dと、第2中間部40eと、を有している。なお、図6は図1の拡大部分図である。
カバープレート41は、フロントカバー2との間にピストン30の受圧部30aを挟むように配置されている。カバープレート41は、図2に示すように、本体部41aと、シール部41bと、トルク伝達部41cと、を有している。
リターン機構42は、図2及び図8に示すように、フロントカバー2とピストン30との間に配置されている。図8は、フロントカバー2及びピストン30のリターン機構42が配置された部分の平面断面図であり、外周側から視た図である。具体的には、リターン機構42は、フロントカバー2のピストン30側の側面に形成された凹部2gと、ピストン30のフロントカバー2側の側面に形成された凹部30gとの間に配置されている。リターン機構42は、ピストン30をフロントカバー2の摩擦面から離れる方向に付勢する機構であり、ピストン30をフロントカバー2から離れる方向に付勢するとともに、フロントカバー2の摩擦面2bとピストン30の押圧部30fとの間の隙間を調整する。リターン機構42は、図8に示すように、バイメタル製のリターンスプリング50と、カム機構51と、によって構成されている。
このようなリターン機構42では、雰囲気温度が低温の場合は、リターンスプリング50が図8(a)に示すように収縮する。このため、図8(a)において、第1カム部材55が第2カム部材56に対して右方向に移動する。すると、第1及び第2カム部材55,56の第1傾斜面55a,56aのスライドによって、ピストン30がフロントカバー2から離れるように移動する。このため、ピストン30とフロントカバー2との間の隙間、すなわち、クラッチディスク28が設けられた部分の隙間(クラッチディスク28の切れ代)が大きくなる。したがって、クラッチディスク28部分におけるドラグトルクを小さく抑えることができる。
ピストン作動機構31の構成によって、図2に示すように、ピストン30の受圧部30aとカバープレート41の本体部41aとの間には、ロックアップ用油室C1が形成されている。また、フロントカバー2の径方向中間部と内周部との間には、軸方向に延びる筒状の段付き部2cが形成されており、この段付き部2cの外周面には、シール部材57が装着されている。シール部材57は、ピストン30の第2突出部30cの内周面に当接している。したがって、ピストン30の受圧部30aとフロントカバー2との間には、ロックアップオフ時にロックアップ用油室C1で発生する油圧をキャンセルするためのキャンセル用油室C2が形成されている。
ダンパ機構34は、クラッチディスク28とタービン4との間に配置され、クラッチディスク28からのトルクをタービン4に伝達するものである。図9に示すように、ダンパ機構34は、係合部材60と、ドライブプレート61と、ドリブンプレート62と、複数のトーションスプリング63と、を有している。
ロックアップ装置7において、ロックアップを解除(ロックアップオフ)する場合には、ロックアップ用油室C1はドレンに接続される。したがって、ロックアップ用油室C1内の作動油は、第1油路P1を介してタンク側に戻される。このような状態では、ピストン30の押圧部30fによるプレッシャプレート29への押圧力が解除される。したがって、ロックアップオフ(動力伝達が解除された状態)であり、フロントカバー2からのトルクは、作動油を介してインペラ3からタービン4に伝達され、タービンハブ16を介してトランスミッションの入力シャフトに伝達される。
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。
また、ピストンをフロントカバーから離すためのリターン機構は、ピストンとカバープレートとの間に配置してもよい。
4 タービン
28 クラッチディスク
29 プレッシャプレート
29a 溝
30 ピストン
30e 開口
40 支持用ボス
40b ピストン支持部
40c 溶接部
40d 第1中間部
40e 第2中間部
41 カバープレート(油室プレート)
41c 係合突起(トルク伝達部)
45 シール部材(第1シール部材)
47 シール部材(第2シール部材)
C1 ロックアップ用油室
C2 キャンセル用油室
P1 第1油路
P2 第2油路
Claims (8)
- 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たクラッチディスクと、
前記フロントカバーと前記タービンとの間に配置され、軸方向に移動自在なピストンと、
前記ピストンと前記タービンとの間に配置され、前記ピストンとの間に作動油が供給される第1油室を形成する環状の油室プレートと、
前記フロントカバーの内周部に固定され、第1直径を有し前記ピストンの内周端面を摺動自在に支持するピストン支持部と、前記第1直径と異なる第2直径を有し前記油室プレートの内周部が溶接された溶接部と、前記ピストン支持部と前記溶接部との軸方向間に前記第1直径と前記第2直径の中間の直径で形成され前記第1油室に作動油を供給するための開口が形成された中間部と、を有する環状の支持用ボスと、
前記ピストン支持部に装着された第1シール部材と、
を備えたトルクコンバータのロックアップ装置。 - 前記ピストンの外周部に装着され、前記油室プレートとの間に前記第1油室を形成するための第2シール部材をさらに備えた、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。
- 前記フロントカバーと前記ピストンとの間には、前記第1油室と独立して形成された第2油室が形成されており、
前記支持用ボスには、前記第1油室及び前記第2油室に連通する第1油路及び第2油路が形成されている、
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。 - 前記ピストンと前記クラッチディスクとの間に軸方向に移動自在に配置され、前記ピストンの押圧力によって前記クラッチディスクを圧接する環状のプレッシャプレートをさらに備えた、請求項1から3のいずれかに記載のトルクコンバータのロックアップ装置。
- 前記プレッシャプレートは前記フロントカバーからのトルクが入力され、
前記クラッチディスクは前記プレッシャプレートからのトルクを前記タービン側に伝達する、
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。 - 前記油室プレートは、前記フロントカバーからのトルクを前記プレッシャプレートに伝達するトルク伝達部を有している、請求項5に記載のトルクコンバータのロックアップ装置。
- 前記ピストンは、円周方向に所定の間隔で形成された軸方向に貫通する複数の開口を有し、
前記トルク伝達部は、前記油室プレートの外周部に前記油室プレートと一体で形成され、前記ピストンの開口を貫通して前記プレッシャプレートに係合している、
請求項6に記載のトルクコンバータのロックアップ装置。 - 前記クラッチディスク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をさらに備えた、請求項1から7のいずれか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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DE112016001592.5T DE112016001592T5 (de) | 2015-05-20 | 2016-05-18 | Überbrückungsvorrichtung für Drehmomentwandler |
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JP2015102487A JP6639807B2 (ja) | 2015-05-20 | 2015-05-20 | トルクコンバータのロックアップ装置 |
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US11592091B1 (en) * | 2022-02-09 | 2023-02-28 | Schaeffler Technologies AG & Co. KG | Torque converter assembly including thrust washer |
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- 2016-05-18 US US15/567,672 patent/US20180112758A1/en not_active Abandoned
- 2016-05-18 KR KR1020177032497A patent/KR20180011088A/ko unknown
- 2016-05-18 WO PCT/JP2016/064794 patent/WO2016186146A1/ja active Application Filing
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WO2016186125A1 (ja) | 2016-11-24 |
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US20180163836A1 (en) | 2018-06-14 |
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US20180112758A1 (en) | 2018-04-26 |
KR20180011088A (ko) | 2018-01-31 |
US10571005B2 (en) | 2020-02-25 |
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US10408322B2 (en) | 2019-09-10 |
US20180094713A1 (en) | 2018-04-05 |
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