WO2016136510A1 - Dispositif de verrouillage de convertisseur de couple - Google Patents

Dispositif de verrouillage de convertisseur de couple Download PDF

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Publication number
WO2016136510A1
WO2016136510A1 PCT/JP2016/054231 JP2016054231W WO2016136510A1 WO 2016136510 A1 WO2016136510 A1 WO 2016136510A1 JP 2016054231 W JP2016054231 W JP 2016054231W WO 2016136510 A1 WO2016136510 A1 WO 2016136510A1
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WO
WIPO (PCT)
Prior art keywords
clutch
hydraulic
front cover
torque
connecting member
Prior art date
Application number
PCT/JP2016/054231
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English (en)
Japanese (ja)
Inventor
亮太 中野
佐藤　佳司
Original Assignee
株式会社エクセディ
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Publication of WO2016136510A1 publication Critical patent/WO2016136510A1/fr

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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
    • F16H—GEARING
    • F16H61/00—Control functions within control units of change-speed- or reversing-gearings for conveying rotary motion ; Control of exclusively fluid gearing, friction gearing, gearings with endless flexible members or other particular types of gearing
    • F16H61/14—Control of torque converter lock-up clutches

Definitions

  • the present invention relates to a lockup device, and more particularly, to a torque converter lockup device disposed between a front cover and a turbine.
  • the torque converter is a device that transmits torque from the engine to the transmission side via an internal working fluid, and mainly includes a front cover to which torque from the engine is input, an impeller, a turbine, and a stator. I have. Torque input to the front cover is transmitted from the impeller to the turbine via hydraulic oil and output to the transmission side. The hydraulic fluid returning from the turbine to the impeller is rectified by the stator.
  • the lock-up device includes, for example, a piston that has a friction member and is pressed against the front cover, and a damper mechanism that is disposed between the piston and the turbine.
  • Patent Document 1 discloses an apparatus that eliminates the need for hydraulic pressure on the piston in the lock-up state.
  • the device disclosed in Patent Document 1 includes a first clutch portion and a second clutch portion.
  • the first clutch portion has a piston having a friction member.
  • the second clutch portion has a connecting member. The connecting member slides in the axial direction by the hydraulic oil, and can mechanically connect the front cover and the piston.
  • the front cover and the piston can be mechanically connected by the second clutch portion. For this reason, if the front cover and the piston are mechanically connected, it is not necessary to apply hydraulic pressure to the piston. For this reason, the loss by supply of hydraulic fluid can be suppressed.
  • a torque converter having a lock-up device is generally provided with two hydraulic ports. Therefore, in order to realize the device of Patent Document 1, it is necessary to significantly change the hydraulic circuit for supplying hydraulic oil to the torque converter.
  • An object of the present invention is to make it unnecessary to supply hydraulic oil in a lock-up state without significantly changing a hydraulic circuit for supplying hydraulic oil to the torque converter.
  • a lockup device for a torque converter is disposed between a front cover and a turbine, and includes a first clutch portion, a torque transmission member, a second clutch portion, and a first hydraulic port. And a drain port.
  • the first clutch portion is operated by hydraulic oil, and transmits torque or cancels torque transmission between the front cover and the turbine.
  • a torque transmission member is arrange
  • the second clutch portion includes a connecting member that is operated by hydraulic oil, and mechanically connects or disconnects the front cover and the torque transmission member.
  • the first hydraulic port supplies hydraulic oil that operates the first clutch unit and operates the connecting member of the second clutch unit.
  • the drain port is a port for releasing the connection of the second clutch portion by the connecting member.
  • torque is transmitted between the front cover and the turbine by operating the first clutch portion with hydraulic oil. Further, by operating the connecting member of the second clutch portion with the hydraulic oil, the connecting member mechanically connects the front cover and the torque transmitting member, and torque is transmitted between the front cover and the torque transmitting member. .
  • the front cover ⁇ the torque transmission member ⁇ the turbine is mechanically connected to the second clutch portion while reducing the relative rotation between the front cover and the torque transmission member by setting the first clutch portion to the torque transmission state. Torque can be transmitted along the path. For this reason, if torque is transmitted between the front cover and the torque transmission member via the connecting member, it is not necessary to apply hydraulic oil to the first clutch portion and the second clutch portion.
  • first clutch part and the connecting member are operated by hydraulic oil supplied from the first hydraulic port. Further, the connection by the connecting member is released by the drain port. That is, a special hydraulic port for operating the connecting member is not necessary. Therefore, this apparatus can be operated only by adding a drain port to two hydraulic ports similar to the conventional apparatus.
  • the first clutch portion is brought into a torque transmission release state, and the connection member of the second clutch portion is moved in a direction in which the connection is released.
  • a second hydraulic port for supplying oil is further provided.
  • the first clutch part and the connecting member are operated to release the torque transmission in the first clutch part, and the connection in the second clutch part is released. Can do.
  • the torque transmission member is a piston movable in the axial direction by hydraulic oil.
  • the first clutch portion has a friction member fixed to the piston, and the friction member is pressed by the front cover to transmit torque between the front cover and the piston.
  • the connecting member of the second clutch portion mechanically connects the front cover and the piston.
  • the second clutch portion includes a first ring gear and a second ring gear.
  • the first ring gear is provided on the front cover and has a plurality of teeth on the inner peripheral surface.
  • the second ring gear is provided on the piston and has a plurality of teeth on the inner peripheral surface.
  • the connecting member has a plurality of teeth on the outer peripheral surface that can mesh with the teeth of the first ring gear and the second ring gear.
  • torque is transmitted through the connecting member between the front cover and the piston by the teeth formed on the outer peripheral surface of the connecting member meshing with the teeth of the first ring gear and the second ring gear.
  • the torque converter lockup device further includes a first clutch portion, a second clutch portion, and an output member that outputs torque from the turbine, and the output member is a disc. And a cylindrical portion extending from the flange toward the axial front cover side.
  • the connecting member is supported on the outer peripheral surface of the cylindrical portion of the output member so as to be slidable in the axial direction.
  • an oil chamber is formed between the connecting member and the output member. This device is provided in the output member, and when the difference between the hydraulic oil pressure from the first hydraulic port and the hydraulic oil pressure from the second hydraulic port becomes a predetermined value or more, the oil chamber is connected to the first hydraulic port.
  • a differential pressure check valve for introducing the hydraulic oil is further provided.
  • the first clutch unit when hydraulic oil is supplied from the first hydraulic port, the first clutch unit is operated to enter a torque transmission state, and the rotational speed of the torque transmission member approaches the rotational speed of the front cover. Thereafter, hydraulic oil is supplied to the oil chamber via the first valve provided in the output member, and the connecting member is operated. By the operation of the connecting member, the front cover and the torque transmitting member are mechanically connected.
  • the operation of the connecting member can be delayed from the operation start of the first clutch portion by the operation of the first valve. Therefore, the front cover and the torque transmission member are smoothly connected by the connecting member.
  • the torque converter lockup device further includes a positioning mechanism for positioning the connecting member at the first position and the second position.
  • the first position is a position at which the second clutch portion is in a disconnected state.
  • the second position is a position where the second clutch portion is in a connected state.
  • the position of the connecting member can be fixed. Therefore, the connected state and the disconnected state can be reliably maintained in the second clutch portion.
  • supply of hydraulic oil can be made unnecessary in the lock-up state only by adding a drain port in addition to a generally used conventional hydraulic circuit for a torque converter. .
  • FIG. 1 is a cross-sectional view of a torque converter including a lockup device according to an embodiment of the present invention.
  • FIG. 2 is an enlarged partial view of FIG. 1 showing a positioning mechanism.
  • the figure which extracts and shows the damper mechanism of FIG. The figure for demonstrating a hydraulic circuit.
  • the cross-sectional block diagram which shows a main valve.
  • the cross-sectional block diagram which shows a drain port.
  • FIG. 1 is a partial cross-sectional view of a torque converter 1 having a lock-up device as one embodiment of the present invention.
  • An engine (not shown) is arranged on the left side of FIG. 1, and a transmission (not shown) is arranged on the right side of the figure.
  • OO shown in FIG. 1 is the rotation axis of the torque converter and the lockup device.
  • the torque converter 1 is a device for transmitting torque from a crankshaft (not shown) on the engine side to an input shaft of a transmission.
  • the torque converter 1 includes a front cover 2, a torque converter body 6 including three types of impellers (impeller 3, turbine 4, stator 5), and a lockup device 7.
  • the front cover 2 is fixed to a member on the engine side.
  • the front cover 2 has a disk-shaped main body 2a and an outer peripheral cylindrical portion 2b that is formed on the outer peripheral portion and protrudes toward the axial transmission side.
  • the impeller 3 includes an impeller shell 12 fixed to the outer peripheral cylindrical portion 2 b of the front cover 2 by welding, a plurality of impeller blades 13 fixed to the inside thereof, and a cylindrical shape welded to the inner peripheral portion of the impeller shell 12.
  • the turbine 4 is disposed opposite to the impeller 3 in the fluid chamber.
  • the turbine 4 includes a turbine shell 15, a plurality of turbine blades 16 fixed to the turbine shell 15, and a turbine hub (an example of an output member) 17 fixed to the inner peripheral side of the turbine shell 15. .
  • the turbine hub 17 includes a flange 17a, a first cylindrical portion 17b, a second cylindrical portion 17c, and a third cylindrical portion 17d.
  • the flange 17a is formed in a disk shape extending to the outer peripheral side.
  • the inner peripheral portion of the turbine shell 15 is fixed to the flange 17 a by a plurality of rivets 18.
  • the first cylindrical portion 17b is formed so as to protrude from the outer peripheral portion of the flange 17a to the front cover 2 side.
  • the second cylindrical portion 17c and the third cylindrical portion 17d are formed on the inner peripheral portion of the flange 17a.
  • the second cylindrical portion 17c is formed to protrude from the flange 17a to the front cover 2 side.
  • the third cylindrical portion 17d is formed so as to protrude further toward the front cover 2 from the inner peripheral portion at the tip of the second cylindrical portion 17c.
  • the third cylindrical portion 17d is smaller than the outer diameter of the second cylindrical portion 17c.
  • a spline hole is formed in the inner peripheral surface of the turbine hub 17.
  • the transmission input shaft can be engaged with the spline hole.
  • the stator 5 is a mechanism for rectifying the hydraulic oil that is disposed between the impeller 3 and the inner peripheral portion of the turbine 4 and returns from the turbine 4 to the impeller 3.
  • the stator 5 mainly includes an annular stator carrier 20 and a plurality of stator blades 21 provided on the outer peripheral surface thereof.
  • the stator carrier 20 is supported by a fixed shaft (not shown) via a one-way clutch 22.
  • Thrust bearings 24 and 25 are provided between the turbine hub 17 and the one-way clutch 22 and between the one-way clutch 22 and the impeller shell 12, respectively.
  • the lock-up device 7 is disposed in a space between the front cover 2 and the turbine 4, and transmits torque between them (hereinafter referred to as “lock-up state” or “lock-up on”) or cancels torque transmission. (Hereinafter referred to as “lock-up release” or “lock-up off”).
  • the lock-up device 7 includes a friction member 28 (an example of a first clutch part), a piston 30 (an example of a torque transmission member), a dog clutch (an example of a second clutch part) 32, and a damper mechanism 34. Yes. Further, the lockup device 7 is provided with a hydraulic circuit.
  • the friction member 28 is formed in an annular shape and is fixed to the outer peripheral side surface of the piston 30 on the front cover 2 side.
  • the friction member 28 is for transmitting torque between the front cover 2, the damper mechanism 34, and the turbine 4 or releasing torque transmission by the piston 30 that moves in the axial direction by the hydraulic oil.
  • the friction member 28 is referred to as a “first clutch portion 28”.
  • the piston 30 is a substantially disc-shaped member, and includes an outer peripheral disc portion 30a, an outer peripheral cylindrical portion 30b, an inner peripheral disc portion 30c, and an inner peripheral cylindrical portion 30d. ,have.
  • the piston 30 is disposed between the front cover 2 and the damper mechanism 34, and is movable in the axial direction by hydraulic oil. 2 shows an extracted portion of the lock-up device 7 in FIG.
  • the annular friction member 28 is fixed to the outer peripheral portion of the outer peripheral disc portion 30a.
  • the outer peripheral cylindrical portion 30b extends obliquely from the outer peripheral disc portion 30a toward the inner peripheral side, and further extends toward the axial turbine 4 side.
  • the inner peripheral disc part 30c extends from the outer cylindrical part 30b to the inner peripheral side.
  • the inner peripheral cylindrical portion 30d extends from the inner peripheral end of the inner peripheral disc portion 30c to the turbine 4 side.
  • the inner peripheral cylindrical portion 30 d is slidably supported on the outer peripheral surface of the first cylindrical portion 17 b of the turbine hub 17.
  • a seal member 36 is disposed on the outer peripheral surface of the first cylindrical portion 17b of the turbine hub 17, so that the space between the inner peripheral surface of the piston 30 and the first cylindrical portion 17b of the turbine hub 17 is sealed. Has been.
  • the dog clutch 32 includes a connecting member 40 that is operated by hydraulic oil, a first ring gear 41, and a second ring gear 42.
  • the dog clutch 32 is for mechanically connecting the front cover 2 and the piston 30 by the connecting member 40 and transmitting torque between the front cover 2 and the turbine 4 or releasing torque transmission.
  • the connecting member 40 is formed in an annular shape, and is disposed between the front cover 2 and the turbine hub 17 so as to be movable in the axial direction.
  • a plurality of teeth 40 a are formed on the outer peripheral surface of the connecting member 40.
  • a chamfer is formed at the front end of each tooth 40a on the front cover 2 side.
  • the inner peripheral surface of the connecting member 40 is slidably supported on the outer peripheral surface of the third cylindrical portion 17d of the turbine hub 17 and the outer peripheral surface of a thrust washer 46 (described later).
  • a seal member 47 is disposed on the outer peripheral surface of the third cylindrical portion 17d of the turbine hub, whereby the space between the inner peripheral surface of the connecting member 40 and the third cylindrical portion 17d is sealed.
  • annular projecting portion 40b projecting to the turbine 4 side is formed on the side surface on the turbine 4 side.
  • the annular projecting portion 40b is slidably supported on the outer peripheral surface of the second cylindrical portion 17c of the turbine hub 17.
  • a seal member 48 is disposed on the inner peripheral surface of the annular projecting portion 40b, thereby sealing between the inner peripheral surface of the annular projecting portion 40b and the second cylindrical portion 17c.
  • the first ring gear 41 is fixed to the intermediate portion in the radial direction on the side surface of the front cover 2 on the turbine 4 side.
  • a plurality of teeth 41 a are formed on the inner peripheral surface of the first ring gear 41.
  • the second ring gear 42 is formed integrally with the piston 30 on the inner peripheral surface of the outer peripheral cylindrical portion 30 b of the piston 30.
  • a plurality of teeth 42 a are formed on the inner peripheral surface of the second ring gear 42.
  • the teeth 40a of the connecting member 40 are always meshed with the teeth 42a of the second ring gear 42. Then, the connecting member 40 is moved to the front cover 2 side by the hydraulic oil, so that the teeth 40 a on the outer peripheral surface mesh with the teeth 41 a of the first ring gear 41. That is, the state in which the teeth 40a of the connecting member 40 mesh with the teeth 41a, 42a of both the first ring gear 41 and the second ring gear 42 is the torque transmission state (clutch on) of the dog clutch 32, and the second ring A state where only the teeth 42a of the gear 42 are engaged is a torque transmission release state (clutch off) of the dog clutch 32.
  • the lockup device 7 includes a positioning mechanism 49 for positioning the connecting member 40 in the axial direction.
  • the positioning mechanism 49 has a thrust washer 46. As shown in FIG. 2, the thrust washer 46 is disposed on the inner peripheral side of the connecting member 40 between the third cylindrical portion 17 d of the turbine hub 17 and the front cover 2.
  • the thrust washer 46 is formed with two through holes 46a at positions opposed to each other in the radial direction (only one hole is shown in FIG. 3).
  • a spring seat 50 is disposed in each of the two holes 46a.
  • the spring seat 50 includes a disc-shaped collar portion 50a and a positioning projection 50b that projects from the center of the collar portion 50a.
  • the positioning protrusion 50 b is inserted into the hole 46 a from the inner peripheral side of the thrust washer 46.
  • a spring 51 is provided between the flange portions 50a of the two spring seats 50 so as to bias the two spring seats 50 outward.
  • annular recesses 40c and 40d are formed on the inner peripheral surface of the connecting member 40 in the axial direction.
  • the tips of the positioning protrusions 50b of the two spring seats 50 can be fitted into the annular recesses 40c and 40d.
  • the damper mechanism 34 is disposed between the piston 30 and the turbine 4. As shown in FIG. 4, the damper mechanism 34 includes an input plate 54, a plurality of torsion springs 55, a float member 56, and an output plate 57.
  • the input plate 54 is an annular member, and the inner periphery is fixed to the piston 30 by a rivet 58.
  • the input plate 54 includes a support portion 54a, a plurality of engagement portions 54b, and a plurality of stopper claws 54c.
  • the support portion 54a is formed by bending the radial intermediate portion of the input plate 54 toward the turbine 4 and is formed in a cylindrical shape.
  • the plurality of engaging portions 54b are formed by bending a part of the support portion 54a to the outer peripheral side and further bending the tip thereof to the turbine 4 side.
  • the engaging portion 54 b is in contact with the circumferential end surface of the torsion spring 55.
  • the stopper claw 54c is formed by extending a part of the support portion 54a further to the turbine 4 side.
  • the plurality of torsion springs 55 are arranged at intervals in the circumferential direction, and movement is regulated by the float member 56.
  • the float member 56 is formed in an annular shape, and includes a side portion 56a, an outer peripheral portion 56b, and an intermediate engagement portion 56c.
  • the side portion 56a is disposed between the piston 30 and the torsion spring 55, and restricts the movement of the torsion spring 55 toward the front cover 2 side.
  • the inner peripheral surface of the side portion 56a is supported by the outer peripheral surface of the support portion 54a of the input plate 54, whereby the float member 56 is positioned in the radial direction.
  • the outer peripheral portion 56b is formed by extending the outer peripheral end of the side portion 56a toward the turbine 4 side.
  • the outer peripheral portion 56b restricts the torsion spring 55 from projecting to the outer peripheral side.
  • the movement of the torsion spring 55 toward the inner peripheral side is restricted by the stopper claw 54 c of the input plate 54.
  • the intermediate engaging part 56c is formed by cutting and raising a part of the side part 56a toward the turbine 4, and a part formed by bending a part of the outer peripheral part 56b toward the inner peripheral side and the front cover 2 side. ,have.
  • the intermediate engagement portion 56 c can contact the end surface of the torsion spring 55. Further, the movement of the torsion spring 55 toward the turbine 4 side is restricted by an intermediate engagement portion 56c formed by bending a part of the outer peripheral portion 56b toward the inner peripheral side.
  • the engaging portions 54b of the input plate 54 are engaged with both end faces in the circumferential direction of the set of two torsion springs 55 out of the plurality of torsion springs 55, and one set of two torsion springs.
  • An intermediate engagement portion 56 c is inserted between the springs 55 and is in contact with the end surface of the torsion spring 55. Thereby, one set of two torsion springs 55 acts in series.
  • the output plate 57 is a substantially disk-shaped member, and an inner peripheral portion thereof is fixed to the flange 17 a of the turbine hub 17 together with the turbine shell 15 by a rivet 18.
  • a cylindrical portion 57 a and a plurality of engaging portions 57 b are formed on the outer peripheral portion of the output plate 57.
  • the cylindrical part 57a is formed by bending the outer peripheral part to the front cover 2 side.
  • the plurality of engaging portions 57b are formed by bending a part of the tip of the cylindrical portion 57a to the outer peripheral side and the front cover 2 side.
  • the cylindrical portion 57a is formed with a notch extending in the circumferential direction at a portion where the plurality of engaging portions 57b are not formed.
  • the stopper claw 54c of the input plate 54 is inserted into this notch. Therefore, the input plate 54 and the output plate 57 can rotate relative to each other as long as the stopper claw 54c can move within the notch.
  • the plurality of engaging portions 57 b can be engaged with both circumferential end surfaces of one set of two torsion springs 55 of the plurality of torsion springs 55.
  • the hydraulic circuit includes a first hydraulic port P1, a second hydraulic port P2, a drain port Pd (see FIG. 7), a first oil chamber Q1, a second oil chamber Q2, and a third oil chamber Q3. And a pressure type check valve (hereinafter simply referred to as “check valve”) Vc.
  • check valve a pressure type check valve
  • the first hydraulic port P1 is formed between the turbine hub 17 and the one-way clutch 22.
  • the first hydraulic port P1 supplies hydraulic oil into the torque converter body 6 and supplies hydraulic oil to the first oil chamber Q1.
  • the second hydraulic port P2 is formed by a notch 46b formed at the end of the thrust washer 46 on the front cover 2 side.
  • the second hydraulic port P2 supplies hydraulic oil to the second oil chamber Q2. Further, when the second hydraulic port P2 is connected to the drain, the hydraulic oil in the second oil chamber Q2 is discharged through the second hydraulic port P2.
  • the first oil chamber Q1 is a space formed on the turbine 4 side of the piston 30.
  • the second oil chamber Q ⁇ b> 2 is a space formed between the front cover 2, the piston 30 and the connecting member 40.
  • the piston 30 moves to the front cover 2 side by increasing the hydraulic pressure of the hydraulic oil in the first oil chamber Q1 (hereinafter simply referred to as “hydraulic pressure”) above the hydraulic pressure of the second oil chamber Q2.
  • the third oil chamber Q3 is a space formed between the inner peripheral portion of the connecting member 40 and the turbine hub 17.
  • the check valve Vc is disposed inside the second cylindrical portion 17c of the turbine hub 17, as shown in FIG. 6 which is a partially enlarged view of FIGS. More specifically, a stepped hole penetrating in the axial direction is formed in the second cylindrical portion 17c, and a check valve Vc is disposed in this hole.
  • the check valve Vc opens when the pressure difference between the first oil chamber Q1 and the third oil chamber Q3 exceeds a predetermined value, and guides hydraulic oil from the first hydraulic port P1 to the third oil chamber Q3 side.
  • the check valve Vc includes a spool 61 that can move in the axial direction, a seat 62, and a spring 63.
  • the spool 61 has a body portion 61a and a seal portion 61b.
  • a horizontal hole 61c and a vertical hole 61d are formed in the body portion 61a.
  • the lateral hole 61c extends in the axial direction at the center of the body 61a.
  • the end of the horizontal hole 61c on the third oil chamber Q3 side is open, and the other end is closed.
  • the vertical hole 61d is formed in the end portion of the body portion 61a on the seal portion 61b side so as to penetrate in the radial direction.
  • the seal portion 61b is formed in a truncated cone shape, and an annular groove 61e is formed in a part thereof, and an O-ring 64 is attached to the groove 61e.
  • the sheet 62 has a tapered recess 62a into which the seal portion 61b of the spool 61 can be fitted.
  • a communication hole 62b communicating with the first hydraulic port P1 is formed at the bottom of the recess 62a.
  • the spring 63 is disposed on the outer periphery of the body portion 61 a of the spool 61 and acts to press the seal portion 61 b of the spool 61 against the concave portion 62 a of the sheet 62.
  • the drain port Pd is formed in the second cylindrical portion 17c of the turbine hub 17 at a location where the phase in the circumferential direction is different from that of the check valve Vc (for example, a position corresponding in the radial direction).
  • the drain port Pd has two first holes 71 in the axial direction (only one is shown in FIG. 7) and one second hole 72 in the radial direction.
  • the first hole 71 is formed at a predetermined depth from the end surface on the front cover 2 side of the second cylindrical portion 17c to the transmission side, and does not penetrate in the axial direction.
  • the second hole 72 is formed at a predetermined depth so as to communicate with the two first holes 71 from the outer peripheral surface opposite to the outer peripheral surface shown in FIG. 7 of the second cylindrical portion 17c. Yes. More specifically, the second hole 72 is formed to connect from the outer peripheral surface of the second cylindrical portion 17c to one first hole 71 (the hole not shown in FIG. 7), and penetrates the internal hole. Furthermore, it is formed so as to be connected to the other first hole 71 (hole shown in FIG. 7). The second hole 72 does not penetrate in the radial direction. And the part opened to the outer peripheral surface of the 2nd cylindrical part 17c of the 2nd hole 72 is obstruct
  • the drain port Pd as described above communicates with a control valve (not shown) provided on the transmission side through a clearance on the outer peripheral side of the transmission input shaft.
  • the hydraulic oil in the third oil chamber Q3 is drained through the drain port Pd by operating the control valve.
  • FIG. 8 shows the hydraulic control flow for the lockup device and the state of the lockup device at that time.
  • the upper part of the figure shows the oil pressure (left vertical axis) of each part with respect to the elapsed time (horizontal axis) and the displacement of the piston 30 and the connecting member 40 (right vertical axis). Note that “displacement” is not an absolute movement amount but a ratio (%) when the maximum displacement is 100%. In the lower part of the figure, the movement of the piston 30 and the connecting member 40 in each stage of hydraulic control is shown.
  • C1 indicates the hydraulic pressure of the first oil chamber Q1
  • C2 indicates the hydraulic pressure of the second oil chamber Q2
  • C3 indicates the hydraulic pressure of the third oil chamber Q3.
  • Dp represents the displacement of the piston 30 and Dd represents the displacement of the connecting member 40.
  • the first stage shows a torque transmission state by the torque converter body 6.
  • the hydraulic pressure C2 of the hydraulic oil supplied from the second hydraulic port P2 is relatively high, and the hydraulic pressure C2 of the second oil chamber Q2 is higher than the hydraulic pressures C1 and C3 of the first oil chamber Q1 and the dog oil chamber Qd. Is expensive. Therefore, both the first clutch portion 28 and the dog clutch 32 are off, and the torque input to the front cover 2 is transmitted to the turbine 4 via the torque converter body 6. That is, lock-up off.
  • the check valve Vc remains closed. Accordingly, the hydraulic pressure C3 of the third oil chamber Q3 is maintained as it is in the first stage, and the connecting member 40 does not move to the front cover 2 side. That is, the connecting member 40 meshes with the second ring gear 42, but does not mesh with the first ring gear 41, and the dog clutch 32 remains off.
  • FIG. 8 shows a state where the displacement Dd of the connecting member 40 is stopped in the middle.
  • the next stage IV is entered.
  • the hydraulic pressure C1 of the hydraulic oil supplied from the first hydraulic pressure port P1 is lowered to a predetermined hydraulic pressure.
  • This predetermined hydraulic pressure is such that the first clutch portion 28 slips.
  • the phase of the tooth 40a of the connection member 40 and the tooth 41a of the 1st ring gear 41 shifts, and mutual collision is avoided.
  • the connecting member 40 reliably meshes with the first ring gear 41.
  • the chamfer is formed in the end surface of the tooth
  • the first hydraulic port P1 and the second hydraulic port P2 are connected to the drain, and the hydraulic oil in the first oil chamber Q1 and the second oil chamber Q2 is discharged.
  • the hydraulic pressures C1 and C2 of the first and second oil chambers Q1 and Q2 become “0”.
  • the drain port Pd is closed by operating the control valve, and the hydraulic pressure in the third oil chamber Q3 is maintained at the third stage.
  • the torque input to the front cover 2 is transmitted to the piston 30 via the dog clutch 32 and then transmitted to the turbine 4 via the damper mechanism 34. That is, lock-up on by mechanical connection.
  • the first clutch portion 28 does not transmit torque. Further, since the hydraulic oil is not supplied also to the second oil chamber Q2, it is not necessary to drive a pump for supplying the hydraulic oil. That is, it is possible to transmit the torque input to the front cover 2 to the turbine 4 while maintaining the lock-up state without supplying hydraulic oil to the torque converter.
  • the fifth stage is a lock-up state in which torque from the front cover 2 is mechanically transmitted to the turbine 4 via the dog clutch 32.
  • the displacement of the piston 30 is the same as that of the fourth stage, but here, the pressing force by the hydraulic oil does not act on the piston 30. Therefore, in the fifth stage, the first clutch portion 28 is off.
  • the first hydraulic port P1 and the second hydraulic port P2 are connected to the drain, and the hydraulic pressures C1 and C2 of the first and second hydraulic chambers are “0”. That is, the lockup state can be maintained without supplying hydraulic oil to the lockup device.
  • the sixth stage and the seventh stage show the hydraulic control when releasing the lock-up state from the lock-up state.
  • the lock-up state is a state where torque is mechanically transmitted only by the dog clutch 32. If the dog clutch 32 is turned off from such a state, the clutch does not slip as a transition state, so that a shock may occur when the dog clutch 32 is turned off.
  • the dog clutch 32 when changing from the lock-up state to the lock-up release state, the dog clutch 32 is turned off after the first clutch portion 28 is turned on, and then the first clutch portion 28 is turned off.
  • the hydraulic oil is supplied from the second hydraulic port P2 with a delay from the increase in the hydraulic pressure C1 in the first oil chamber Q1, and the hydraulic pressure C2 in the second oil chamber Q2 is increased to a predetermined hydraulic pressure.
  • the check valve Vc is closed.
  • the drain port Pd is connected to the drain by operating the control valve.
  • the connecting member 40 moves to the second ring gear 42 side. For this reason, the meshing between the connecting member 40 and the first ring gear 41 is released, and the dog clutch 32 is turned off.
  • the first clutch portion 28 is once turned on and then the dog clutch 32 is turned off, so that the lock is turned on compared to the case where the dog clutch 32 is turned off without turning on the first clutch portion 28. Shock when releasing up can be suppressed.
  • the first clutch portion is a friction member fixed to the piston, but it may be a multi-plate clutch having a plurality of clutch plates.
  • the 2nd clutch part was made into the dog clutch, if the torque is transmitted mechanically other, the structure is not limited.
  • the front cover and the piston are mechanically connected by the second clutch portion, but the torque transmission path is not limited to this.
  • the front cover and the input member of the damper mechanism may be mechanically coupled by the second clutch portion.

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  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Control Of Fluid Gearings (AREA)

Abstract

Par simple ajout d'une structure simple à un circuit hydraulique utilisé dans un convertisseur de couple classique, la présente invention rend inutile l'alimentation en fluide hydraulique dans l'état de verrouillage. Le présent dispositif de verrouillage est pourvu d'une première section d'embrayage (28), d'un piston (30), d'un embrayage à griffes (32), d'un premier orifice hydraulique (P1), et d'un orifice de fuite (Pd). La première section d'embrayage (28) est actionnée par un fluide hydraulique. Le piston (30) est disposé entre la première section d'embrayage (28) et une turbine (4), et transmet le couple de la première section d'embrayage (28) à la turbine (4). L'embrayage à griffes (32) possède un élément de couplage (40) qui est actionné par le fluide hydraulique et est capable de coupler mécaniquement un couvercle avant (2) et le piston (30). Le premier orifice hydraulique (P1) actionne la première section d'embrayage (28) et fournit du fluide hydraulique pour faire fonctionner l'élément de couplage (40) de l'embrayage à griffes (32). L'orifice de fuite (Pd) libère le couplage par l'élément de couplage (40) de l'embrayage à griffes (32).
PCT/JP2016/054231 2015-02-25 2016-02-15 Dispositif de verrouillage de convertisseur de couple WO2016136510A1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
JP2015034736A JP2016156452A (ja) 2015-02-25 2015-02-25 トルクコンバータのロックアップ装置
JP2015-034736 2015-02-25

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WO2016136510A1 true WO2016136510A1 (fr) 2016-09-01

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Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US11351855B2 (en) * 2020-05-15 2022-06-07 Schaeffler Technologies AG & Co. KG Multi-mode hybrid module

Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPH0676761U (ja) * 1994-04-13 1994-10-28 株式会社大金製作所 ロックアップクラッチ付トルクコンバータ
JP2008144816A (ja) * 2006-12-07 2008-06-26 Exedy Corp ロックアップ装置およびそれを備えた流体式トルク伝達装置
JP2013256986A (ja) * 2012-06-12 2013-12-26 Exedy Corp トルクコンバータのロックアップ装置

Patent Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPH0676761U (ja) * 1994-04-13 1994-10-28 株式会社大金製作所 ロックアップクラッチ付トルクコンバータ
JP2008144816A (ja) * 2006-12-07 2008-06-26 Exedy Corp ロックアップ装置およびそれを備えた流体式トルク伝達装置
JP2013256986A (ja) * 2012-06-12 2013-12-26 Exedy Corp トルクコンバータのロックアップ装置

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US11351855B2 (en) * 2020-05-15 2022-06-07 Schaeffler Technologies AG & Co. KG Multi-mode hybrid module

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