WO2010021243A1 - トルクコンバータ - Google Patents
トルクコンバータ Download PDFInfo
- Publication number
- WO2010021243A1 WO2010021243A1 PCT/JP2009/063871 JP2009063871W WO2010021243A1 WO 2010021243 A1 WO2010021243 A1 WO 2010021243A1 JP 2009063871 W JP2009063871 W JP 2009063871W WO 2010021243 A1 WO2010021243 A1 WO 2010021243A1
- Authority
- WO
- WIPO (PCT)
- Prior art keywords
- stator
- impeller
- brake
- side member
- 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
- 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
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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
- F16H2045/0273—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
- F16H2045/0284—Multiple disk type lock-up clutch
Definitions
- the present invention relates to a torque converter, and more particularly to a torque converter in which a stator brake is provided on the inner circumferential portion of a stator.
- the torque converter is a device having three types of impellers consisting of an impeller, a turbine and a stator, and transmitting power by the fluid inside the torus formed by these.
- the impeller together with the front cover to which power is input from the engine, forms a fluid chamber filled with hydraulic oil.
- the turbine is disposed axially opposite the impeller in the fluid chamber.
- the turbine hub that constitutes this turbine is connected to the transmission input shaft.
- the stator rectifies the flow of hydraulic oil from the turbine to the impeller and is disposed between the inner periphery of the impeller and the inner periphery of the turbine.
- the stator is connected to a fixed housing or the like via a one-way clutch.
- a torque converter provided with a brake for braking the rotation of the stator (see Patent Document 1).
- a stator brake is provided on the inner peripheral side of the stator, and a lockup clutch is provided between the front cover and the turbine.
- the lockup clutch and the stator brake are responsive to the differential pressure between the pressure of the hydraulic fluid for turning on (locking) the lockup clutch and the pressure of the hydraulic fluid for turning off (locking release) the lockup clutch. , Change the engagement force between the front cover and the impeller and the stator.
- the stator brake is disposed on the inner peripheral side of the stator. Therefore, if the diameter of the brake disk is increased in order to secure a large brake capacity, the torus of the torque converter is reduced, which adversely affects the performance of the torque converter. Conversely, if the torus is increased to ensure the performance of the torque converter, the space for the stator brake will be narrowed, and a sufficient brake capacity can not be secured.
- stator brake becomes axially long, which hinders the reduction of the axial dimension of the entire torque converter.
- An object of the present invention is to reduce the size of the stator brake while maintaining the performance of the torque converter. Another object of the present invention is to enable the stator brake to be disposed on the inner peripheral side of the stator without increasing the axial dimension.
- the torque converter according to the first aspect of the invention transmits torque from the engine to the input shaft of the transmission by fluid, and includes a front cover, an impeller, a turbine, a stator, a stator brake, and a first sliding member. And a second sliding member.
- the front cover receives torque from the engine.
- the impeller is connected to the front cover and constitutes a fluid chamber together with the front cover.
- a turbine is disposed opposite the impeller and capable of outputting torque to the transmission.
- the stator is disposed between the inner periphery of the impeller and the inner periphery of the turbine to rectify the flow of fluid flowing from the turbine to the impeller.
- the stator brake includes a stator side member connected to the stator, a stationary side member disposed on the inner peripheral side of the stator side member and coupled to a non-rotatable member, and between the stator side member and the stationary side member And a brake disc unit disposed to brake rotation of the stator.
- the first sliding member is disposed axially between the impeller and the stator side member, and rotatably supports the impeller and the stator side member.
- the second sliding member is disposed on the engine side in the axial direction with respect to the first sliding member between the impeller and the stationary side member in the axial direction, and rotatably supports the impeller and the stationary side member.
- the power input to the front cover and the impeller is transmitted to the turbine through the fluid and further transmitted to the transmission. Also, fluid flows from the impeller into the turbine and is returned to the impeller through the stator. Also, the stator brakes the rotation by the stator brake, thereby controlling the capacity of the torque converter.
- the stator brake includes a stator side member that can rotate with the stator, and a stationary side member that can not rotate. And these members are disposed close to the impeller and do not rotate in synchronization with the impeller. On the other hand, it is necessary to bring the stator brake and the impeller close to each other in order to shorten the axial dimension of the torque converter.
- the first and second sliding members are disposed between the stator side member and the stationary side member constituting the stator brake and the impeller, and the stator brake is supported relatively rotatably with respect to the impeller. Therefore, it is not necessary to provide an unnecessary space between the stator brake and the impeller, and the axial dimension can be shortened. Moreover, since the second sliding member disposed on the further inner circumferential side is disposed on the engine side in the axial direction relative to the first sliding member, the axial dimension of the torque converter can be further shortened.
- a torque converter according to a second aspect of the present invention is the torque converter of the first aspect, wherein the second sliding member is disposed on the inner peripheral side of the stator side member so as to axially overlap the stator side member.
- the second sliding member is disposed to overlap the stator side member in the axial direction, the axial dimension can be further shortened.
- a torque converter according to a third aspect of the present invention is the torque converter according to the first aspect, further including a lock-up clutch for directly transmitting power from the front cover to the turbine, having a piston pressed into contact with the front cover.
- the turbine also includes a turbine hub having a disk-shaped flange portion and a cylindrical portion. The tubular portion is formed to extend in the axial direction on the inner peripheral portion of the flange portion, and is connected to the input shaft of the transmission.
- the piston of the lockup clutch is axially movably supported at the outer peripheral portion of the flange portion, and the stator side member extends from the outer peripheral side of the disk-shaped vertical wall portion to the transmission side And an inner cylindrical portion extending from the inner circumferential side of the vertical wall portion to the transmission side, and the inner cylindrical portion of the stator side member is a cylindrical shape of the turbine hub It is rotatably supported on the outer peripheral surface of the part.
- the axial dimension can be further shortened.
- a torque converter according to a fourth aspect is the torque converter according to the third aspect, wherein the first sliding member is disposed between the inner wall surface of the impeller and the transmission side end face of the outer cylindrical portion of the stator side member.
- a torque converter according to a fifth aspect of the present invention is the torque converter according to the fourth aspect, wherein the third sliding member is disposed between the engine side surface of the vertical wall of the stator side member and the turbine, and rotatably supports the stator side member. Are further equipped.
- a torque converter according to a sixth aspect of the present invention is the torque converter according to the third aspect, wherein the impeller has a cylindrical portion extending in the axial direction along the input shaft of the transmission at the inner peripheral portion.
- the stationary side member of the stator brake has a disk-shaped vertical wall portion, and an inner cylindrical portion formed to extend in the axial direction on the transmission side on the inner peripheral portion of the vertical wall portion.
- the inner cylindrical portion of the fixed side member is arranged to overlap in the axial direction on the inner peripheral side of the cylindrical portion of the impeller.
- the axial dimension can be further shortened.
- a torque converter according to a seventh aspect of the invention is the torque converter according to the third aspect, wherein a plurality of teeth extending in the axial direction is formed on the outer peripheral portion of the outer cylindrical portion of the stator side member. A plurality of teeth are formed to mesh with the plurality of teeth.
- the dimension on the stator brake side can be secured larger in the radial direction, and the diameter of the disc constituting the stator brake can be increased. Therefore, the required brake capacity can be secured with a small number of discs.
- a torque converter according to an eighth aspect of the present invention is the torque converter according to the first aspect, wherein an inside / outside diameter ratio of a torus formed of an impeller, a turbine and a stator is 0.55 or more .
- the required performance of the torque converter can be maintained without increasing the number of disks of the stator brake.
- the size of the stator brake can be reduced while maintaining the performance of the torque converter. Further, the axial dimension of the torque converter can be shortened.
- FIG. 2 is a schematic longitudinal sectional view of a torque converter 1;
- FIG. 2 is an enlarged partial view of FIG. 1;
- FIG. 1 is a longitudinal sectional view of a torque converter 1 in which one embodiment of the present invention is adopted.
- the torque converter 1 is a device for transmitting torque from the crankshaft of the engine to the input shaft 2 of the transmission.
- An engine (not shown) is disposed on the left side of FIG. 1, and a transmission (not shown) is disposed on the right side of FIG. OO shown in FIG. 1 is the rotation shaft of the torque converter 1.
- the torque converter 1 mainly includes a front cover 4, three types of impellers (impellers 5, turbines 6 and stators 7), a stator brake 8, and a lockup clutch 10.
- the front cover 4 is a disk-shaped member, and a center boss 14 is fixed to the inner peripheral end by welding.
- the center boss 14 is an axially extending cylindrical member, and is inserted into a central hole of a crankshaft (not shown).
- the front cover 4 is connected to the crankshaft of the engine via a flexible plate. That is, a plurality of nuts 15 are fixed at equal intervals in the circumferential direction on the outer circumferential side and the engine side of the front cover 4, and bolts (not shown) screwed to the nuts 15 are flexible plates. The outer peripheral portion is fixed to the front cover 4.
- An outer peripheral side cylindrical portion 4 a extending to the transmission side in the axial direction is formed on an outer peripheral portion of the front cover 4.
- the impeller 5 is fixed to the tip of the outer peripheral side cylindrical portion 4a by welding. As a result, the front cover 4 and the impeller 5 form a fluid chamber in which the working oil is filled.
- the impeller 5 mainly includes an impeller shell 18, a plurality of impeller blades 19 fixed to the inner side thereof, and an impeller hub 20 fixed to the inner circumferential portion of the impeller shell 18. And the outer peripheral side front-end
- the turbine 6 is disposed axially opposite to the impeller 5 in the fluid chamber.
- the turbine 6 mainly includes a turbine shell 22, a plurality of turbine blades 23 fixed to a surface on the impeller side thereof, and a turbine hub 24 fixed to the inner peripheral edge of the turbine shell 22.
- the turbine shell 22 and the turbine hub 24 are fixed by a plurality of rivets (not shown).
- the turbine hub 24 has a disk-like flange portion 24a to which the inner peripheral portion of the turbine shell 22 is fixed, an outer cylindrical portion 24b extending toward the engine in the axial direction on the outer peripheral portion of the flange portion 24a, and a flange And an inner cylindrical portion 24c formed to extend in the axial direction at the inner peripheral portion of the portion 24a. Further, a spline hole is formed in the inner peripheral portion of the inner cylindrical portion 24c, and is engaged with a spline shaft formed at the tip of the input shaft 2 of the transmission.
- a thrust washer 25 is disposed between the end of the inner cylindrical portion 24 c of the turbine hub 24 and the front cover 4 for supporting the both rotatably relative to each other.
- the stator 7 is disposed between the inner peripheral portion of the impeller 5 and the inner peripheral portion of the turbine 6 and is a mechanism for rectifying the flow of hydraulic oil from the turbine 6 back to the impeller 5.
- the stator 7 is integrally formed of resin, aluminum alloy or the like by casting.
- the stator 7 mainly includes an annular stator shell 30 and a plurality of stator blades 31 provided on the outer peripheral surface of the stator shell 30.
- the stator shell 30 is supported by the cylindrical fixed shaft 33 via the stator brake 8.
- a plurality of axially extending teeth 30 a are formed on the inner peripheral surface of the stator shell 30.
- the fixed shaft 33 is disposed between the outer peripheral surface of the input shaft 2 and the inner peripheral surface of the cylindrical portion 20 a of the impeller hub 20.
- a torus-shaped fluid operating chamber is formed in the fluid chamber by the shells 18, 22 and 30 of the impellers 5, 6 and 7 described above.
- the inside and outside diameter ratio (D1 / D2) of the torus is 0.63, and the inside and outside diameter ratio of the torus in consideration of the performance of the torque converter and the brake capacity and axial dimension of the stator brake described later. Is preferably 0.55 or more.
- the outer diameter D2 of the torus is the outer diameter of the impeller blade 19
- the inner diameter D1 is the outer diameter of the stator shell 30 (the inner diameter of the stator blade 31).
- the stator brake 8 is disposed on the inner peripheral side of the stator 7 and is for braking the rotation of the stator 7.
- the stator brake 8 is a hydraulically operated clutch brake, and as shown in detail in FIG. 2, the brake case (stator side member) 35 and a multi-plate brake disc disposed inside the brake case 35 It has a portion 36, a piston 37 for pressing the brake disk portion 36, and a brake fixing member (fixed side member) 38 disposed on the inner peripheral side of the brake disk portion 36 and connected to the fixed shaft 33. .
- the brake case 35 includes a disk-shaped vertical wall 35a, an outer cylindrical portion 35b extending from an outer peripheral portion of the vertical wall 35a to the transmission side, and a vertical wall 35a. And an inner cylindrical portion 35c formed to extend from the inner peripheral portion to the transmission side.
- the vertical wall portion 35 a is disposed substantially in parallel with the flange portion 24 a of the turbine hub 24.
- a first thrust bearing 40 is disposed between the outer peripheral portion of the vertical wall portion 35 a and the inner peripheral portion of the turbine shell 22.
- the first thrust bearing 40 is a bearing (sliding member) for rotatably supporting the brake case 35 of the stator brake 8 with respect to the turbine hub 24 (turbine shell 22).
- a plurality of teeth 35d and 35e extending in the axial direction are formed on the outer peripheral surface and the inner peripheral surface of the outer cylindrical portion 35b, and the teeth 35d formed on the outer peripheral surface are formed on the inner peripheral surface of the stator shell 30. It meshes with the plurality of teeth 30a. Further, on the inner peripheral surface of the stator shell 30, a pair of snap rings 41 and 42 are attached to both axial ends of the teeth 30a. Thus, the brake case 35 and the stator shell 30 can not rotate relative to each other, and can not move relative to each other in the axial direction.
- a second thrust bearing 43 is disposed between an axial tip end surface of the outer cylindrical portion 35 b and the impeller shell 18.
- the second thrust bearing 43 is a bearing (sliding member) for rotatably supporting the brake case 35 of the stator brake 8 with respect to the impeller shell 18.
- the inner cylindrical portion 35 c is supported by the outer peripheral portion of the inner cylindrical portion 24 c of the turbine hub 24 relatively rotatably via the roller bearing 44. That is, the inner cylindrical portion 35 c of the brake case 35 is disposed so as to overlap the inner cylindrical portion 24 c of the turbine hub 24 in the axial direction.
- a thrust washer 45 is disposed between the axial forward end of the inner cylindrical portion 35 c and the brake fixing member 38.
- the brake disc portion 36 has a plurality of driven plates 48 (four in this example) and discs 49 (three in this example) alternately arranged in the axial direction.
- the driven plate 48 is a ring-shaped member in which a plurality of teeth are formed on the outer peripheral portion, and the plurality of teeth mesh with the teeth 35 e of the brake case 35 so as to be axially movable.
- the driven plate disposed closest to the transmission is thicker than the other three driven plates, and the other three plates have the same thickness. It is formed.
- the disc 49 is a ring-shaped member in which facings, which are friction members, are attached to both surfaces. A plurality of teeth are formed on the inner circumferential portion of the disc 49.
- the piston 37 has a pressing portion 37a on the outer peripheral portion for pressing the driven plate 48 of the brake disk portion 36 and the disk 49 to each other. A plurality of grooves are formed in the pressing portion 37a along the radial direction. Further, on the inner peripheral portion of the piston 37, a cylindrical support portion 37b extending toward the transmission in the axial direction is formed. The support portion 37 b is axially movably supported on the outer peripheral surface of the inner cylindrical portion 35 c of the brake case 35. The space between the piston 37 and the brake case 35 is sealed by two seal members 51 and 52 provided on the outer peripheral portion of the piston and the outer peripheral portion of the inner cylindrical portion 35 c of the brake case 35.
- the brake fixing member 38 includes a disk-shaped vertical wall 38a, an outer cylindrical portion 38b axially extending from the outer peripheral portion of the vertical wall 38a toward the engine, and a vertical wall 38a. And an inner cylindrical portion c extending in the axial direction from the inner peripheral portion to the transmission side.
- a plurality of teeth extending in the axial direction are formed on the outer peripheral surface of the outer cylindrical portion 38 b, and the teeth mesh with the teeth formed on the inner peripheral portion of the disc 49. Further, spline holes are formed on the inner peripheral surface of the inner cylindrical portion 38 c, and the spline holes are engaged with spline shafts formed on the outer peripheral surface of the fixed shaft 33.
- the inner cylindrical portion 38c is disposed on the inner peripheral side of the cylindrical portion 20a of the impeller hub 20, and both overlap in the axial direction.
- a third thrust bearing 50 is disposed between the outer peripheral portion of the vertical wall portion 38 a and the impeller shell 18.
- the third thrust bearing 50 is a bearing (sliding member) for rotatably supporting the brake fixing member 38 fixed in a non-rotatable manner relative to the rotating impeller hub 20.
- the third thrust bearing 50 is disposed closer to the engine in the axial direction than the second thrust bearing 43.
- the third thrust bearing 50 is disposed inward of the brake case 35 of the stator brake 8 and axially overlaps the outer cylindrical portion 35 b of the brake case 35.
- the lockup clutch 10 is disposed between the front cover 4 and the turbine 6 and directly transmits power from the front cover 4 to the turbine 6.
- the lockup clutch 10 includes a piston 55 and a damper portion 56 disposed between the piston 55 and the turbine 6 as shown in FIG.
- the piston 55 has a piston main body 55a to which the friction member 57 is fixed on the surface on the front cover 4 side, an outer cylindrical portion 55b formed on the outer peripheral side, and an inner cylindrical portion 55c formed on the inner peripheral side. ,have.
- the inner cylindrical portion 55 c is axially movably supported by the outer cylindrical portion 24 b of the turbine hub 24.
- a seal member 58 for sealing between the outer cylindrical portion 24 b of the turbine hub 24 and the piston 55 is provided.
- the damper portion 56 is disposed on the inner peripheral side of the outer cylindrical portion 55 b of the piston 55.
- the damper portion 56 is configured to elastically connect the input side member 60 fixed to the piston 55, the output side member 61 fixed to the turbine shell 22, and the input side member 60 and the output side member 61.
- the circuit for operating the stator brake 8 is, as shown in FIG. 2, a through hole 65 formed in the inner cylindrical portion 24 c of the turbine hub 24 and a through hole formed in the inner cylindrical portion 35 c of the brake case 35. It is formed by the hole 66. That is, in order to turn on the stator brake 8 (press the disc), hydraulic fluid is supplied between the brake case 35 and the piston 37 through the through holes 65 and 66, and the stator brake 8 is turned off (press the disc The hydraulic oil is drained through the same path (through holes 65 and 66) to release it.
- seal members 67 and 68 are provided on both sides in the axial direction of the through hole 65.
- the lockup clutch 10 When the lockup clutch 10 is turned on as described above, the power transmitted from the engine to the front cover 4 is input to the damper unit 56 through the lockup clutch 10. The power is transmitted to the turbine 6 through the damper portion 56 and is further transmitted to the input shaft 2 of the transmission through the turbine hub 24. Power is thus directly transmitted to the transmission side.
- the stator brake 8 is generally turned on at the time of idling of the engine, that is, at the time of stop.
- hydraulic oil is supplied to the back surface of the piston 37 through the through hole 65 of the turbine hub 24 and the through hole 66 of the brake case 35.
- the piston 37 is moved to the transmission side in the axial direction, and the driven plate 48 and the disc 49 are mutually pressed by the piston 37.
- the stator 7 is braked and is in a non-rotatable state.
- the capacity factor of the torque converter is a relatively small value, so the load on the engine is small. For this reason, fuel consumption can be suppressed.
- stator brake 8 when the vehicle starts traveling, the stator brake 8 is switched from on (braking state) to off (braking release state). Thereby, the capacity coefficient is increased, and it is possible to obtain the capacity of the torque converter sufficient for traveling.
- stator brake 8 When the stator brake 8 is turned off, the hydraulic oil supplied to the back surface of the piston 37 is discharged through the through holes 65 and 66.
- the thrust bearings 43 and 50 are respectively disposed between the brake case 35 and the brake fixing member 38 of the stator brake 8 and the impeller 5 to support the stator brake 8 relatively rotatably with respect to the impeller 5 . Therefore, it is not necessary to provide an unnecessary space between the stator brake 8 and the impeller 5, and the axial dimension can be shortened. Further, since the third thrust bearing 50 is disposed closer to the engine in the axial direction than the second thrust bearing 43 and accommodated in the brake case 35, the axial dimension of the torque converter can be further shortened.
- stator 7 and the stator brake 8 are connected by a plurality of teeth formed on the respective inner and outer peripheral portions, a larger dimension on the stator brake side can be secured compared to other connecting methods.
- the diameter of the disc constituting the stator brake can be increased. Therefore, the required brake capacity can be secured with a small number of discs.
- the inner and outer diameter ratio (D1 / D2) of the torus is 0.55 or more, and the stator brake 8 is disposed on the inner peripheral side of the torus. Therefore, similarly to the above, the dimension on the stator brake side can be secured larger to increase the diameter of the brake disc portion, and the required brake capacity can be secured with a small number of discs. Therefore, the required torque converter performance can be maintained without increasing the number of disks of the stator brake.
- stator brake is configured by a plurality of disks
- present invention can be similarly applied to a single plate type stator brake.
- each oil supply circuit is not limited to the above embodiment.
- the size of the stator brake can be reduced while maintaining the performance of the torque converter. Further, the axial dimension of the torque converter can be shortened.
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2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4は、円板状の部材であって、内周端にはセンターボス14が溶接により固定されている。センターボス14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。
インペラー5は、主に、インペラーシェル18と、その内側に固定された複数のインペラーブレード19と、インペラーシェル18の内周部に固定されたインペラーハブ20と、から構成されている。そして、インペラーシェル18の外周側先端部が、前述のように、フロントカバー4に溶接されている。また、インペラーハブ20の内周部には、トランスミッション側に延びる筒状部20aが形成されている。
タービン6は流体室内でインペラー5に対して軸方向に対向して配置されている。タービン6は、主に、タービンシェル22と、そのインペラー側の面に固定された複数のタービンブレード23と、タービンシェル22の内周縁に固定されたタービンハブ24と、から構成されている。タービンシェル22とタービンハブ24とは複数のリベット(図示せず)によって固定されている。
ステータ7は、インペラー5の内周部とタービン6の内周部との間に配置され、タービン6からインペラー5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7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7は、主に、環状のステータシェル30と、ステータシェル30の外周面に設けられた複数のステータブレード31と、を有している。ステータシェル30は、ステータブレーキ8を介して筒状の固定シャフト33に支持されている。ステータシェル30の内周面には、軸方向に延びる複数の歯30aが形成されている。固定シャフト33は入力シャフト2の外周面とインペラーハブ20の筒状部20aの内周面との間に配置されている。
ステータブレーキ8は、ステータ7の内周側に配置されており、ステータ7の回転を制動するためのものである。このステータブレーキ8は、油圧作動式のクラッチブレーキであって、図2に詳細に示すように、ブレーキケース(ステータ側部材)35と、ブレーキケース35の内部に配置された多板型のブレーキディスク部36と、ブレーキディスク部36を押圧するピストン37と、ブレーキディスク部36の内周側に配置されて固定シャフト33に連結されたブレーキ固定部材(固定側部材)38と、を有している。
ブレーキケース35は、図2に示すように、円板状の縦壁部35aと、縦壁部35aの外周部からトランスミッション側に延びて形成された外筒状部35bと、縦壁部35aの内周部からトランスミッション側に延びて形成された内筒状部35cと、を備えている。縦壁部35aはタービンハブ24のフランジ部24aとほぼ平行に配置されている。
ブレーキディスク部36は、軸方向に互いに交互に配置されたそれぞれ複数のドリブンプレート48(この例では4枚)及びディスク49(この例では3枚)を有している。
ピストン37はブレーキディスク部36のドリブンプレート48及びディスク49を互いに押圧するための押圧部37aを外周部に有している。この押圧部37aには複数の溝が半径方向に沿って形成されている。また、ピストン37の内周部には、軸方向においてトランスミッション側に延びる筒状の支持部37bが形成されている。この支持部37bはブレーキケース35の内筒状部35cの外周面に軸方向に移動自在に支持されている。なお、ピストン37とブレーキケース35との間の空間は、ピストンの外周部及びブレーキケース35の内筒状部35cの外周部に設けられた2つのシール部材51,52によりシールされている。
ブレーキ固定部材38は、図2に示すように、円板状の縦壁部38aと、縦壁部38aの外周部から軸方向においてエンジン側に延びる外筒状部38bと、縦壁部38aの内周部から軸方向においてトランスミッション側に延びる内筒状部38cと、を有している。
ロックアップクラッチ10は、フロントカバー4とタービン6との間に配置され、フロントカバー4からタービン6に動力を直接伝達するものである。このロックアップクラッチ10は、図1に示すように、ピストン55と、ピストン55とタービン6との間に配置されたダンパー部56と、を有している。
ステータブレーキ8を作動させるための回路は、図2に示すように、タービンハブ24の内筒状部24cに形成された貫通孔65と、ブレーキケース35の内筒状部35cに形成された貫通孔66と、によって形成されている。すなわち、ステータブレーキ8をオン(ディスクを押圧)させるために、貫通孔65,66を介してブレーキケース35とピストン37との間に作動油が供給され、またステータブレーキ8をオフ(ディスクの押圧解除)させるために、同じ経路(貫通孔65,66)を介して作動油が排出される。なお、タービンハブ24の内筒状部24cにおいて、貫通孔65の軸方向両側にはシール部材67,68が設けられている。
ロックアップクラッチ10がオフ(ロックアップ解除)されているときには、フロントカバー4とタービン6との間のトルク伝達は、インペラー5とタービン6との間の流体伝達によって行われている。インペラー5がエンジンによって回転させられると、作動油は遠心力によってインペラー5からタービン6へと流れる。インペラー5からタービン6へ流れてきた作動油はタービン6を回転させた後にステータ7を通過する。作動油がステータ7を通過する際には、作動油はステータブレード31に衝突し、ブレードによって向きを変えられ、インペラー5へと戻される。
(a) ステータブレーキ8のブレーキケース35及びブレーキ固定部材38とインペラー5との間にそれぞれスラスト軸受43,50を配置して、ステータブレーキ8をインペラー5に対して相対回転自在に支持している。したがって、ステータブレーキ8とインペラー5との間に無駄なスペースを設ける必要がなく、軸方向寸法の短縮化を図ることができる。また、第3スラスト軸受50を第2スラスト軸受43よりも軸方向においてエンジン側に配置し、ブレーキケース35の内部に収容しているので、トルクコンバータの軸方向寸法をより短縮することができる。
前記実施形態では、複数のディスクによりステータブレーキが構成されている場合を説明したが、単板型のステータブレーキであっても本発明を同様に適用することができる。
2 トランスミッションの入力シャフト
4 フロントカバー
5 インペラー
6 タービン
7 ステータ
8 ステータブレーキ
20 インペラーハブ
20a インペラーハブの筒状部
24 タービンハブ
24a フランジ部
24b 外筒状部
24c 内筒状部
35 ブレーキケース
35a 縦壁部
35b 外筒状部
35c 内筒状部
36 ブレーキディスク部
37 ピストン
38 ブレーキ固定部材
38c 内筒状部
40,43,50 スラスト軸受
55 ロックアップクラッチ
Claims (8)
- エンジンからのトルクを流体によってトランスミッションの入力シャフトに伝達するためのトルクコンバータであって、
エンジンからのトルクが入力されるフロントカバーと、
前記フロントカバーに接続され、前記フロントカバーとともに流体室を構成するインペラーと、
前記インペラーに対向して配置され、前記トランスミッションにトルクを出力可能なタービンと、
前記インペラーの内周部と前記タービンの内周部との間に配置され、前記タービンから前記インペラーに流れる流体の流れを整流するためのステータと、
前記ステータに連結されたステータ側部材と、前記ステータ側部材の内周側に配置されるとともに回転不能な部材に連結された固定側部材と、前記ステータ側部材と前記固定側部材との間に配置されたブレーキディスク部、とからなり、前記ステータの回転を制動するステータブレーキと、
前記インペラーと前記ステータ側部材との軸方向間に配置され、前記インペラーと前記ステータ側部材とを回転自在に支持する第1摺動部材と、
前記インペラーと前記固定側部材との軸方向間で前記第1摺動部材より軸方向においてエンジン側に配置され、前記インペラーと前記固定側部材とを回転自在に支持する第2摺動部材と、
を備えたトルクコンバータ。 - 前記第2摺動部材は、前記ステータ側部材の内周側に、前記ステータ側部材と軸方向において重なるように配置されている、請求項1に記載のトルクコンバータ。
- 前記フロントカバーに圧接されるピストンを有し、前記フロントカバーから前記タービンに動力を直接伝達するためのロックアップクラッチをさらに備え、
前記タービンは、円板状のフランジ部と、前記フランジ部の内周部に軸方向に延びて形成されトランスミッションの入力シャフトに連結される筒状部と、を有するタービンハブを含み、
前記ロックアップクラッチのピストンは前記フランジ部の外周部において軸方向に移動自在に支持されており、
前記ステータ側部材は、円板状の縦壁部と、前記縦壁部の外周側からトランスミッション側に延びて形成された外筒状部と、前記縦壁部の内周側からトランスミッション側に延びて形成された内筒状部と、を有し、
前記ステータ側部材の内筒状部は前記タービンハブの筒状部の外周面に回転自在に支持されている、
請求項1に記載のトルクコンバータ。 - 前記第1摺動部材は、前記インペラーの内壁面と前記ステータ側部材の外筒状部のトランスミッション側端面との間に配置されている、請求項3に記載のトルクコンバータ。
- 前記ステータ側部材の縦壁部のエンジン側の面と前記タービンとの間に配置され、前記ステータ側部材を回転自在に支持する第3摺動部材をさらに備えた、請求項4に記載のトルクコンバータ。
- 前記インペラーは、内周部に前記トランスミッションの入力シャフトに沿って軸方向に延びる筒状部を有し、
前記ステータブレーキの固定側部材は、円板状の縦壁部と、前記縦壁部の内周部にトランスミッション側に軸方向に延びて形成された内筒状部と、を有し、
前記固定側部材の内筒状部は、前記インペラーの筒状部の内周側において軸方向において重なるように配置されている、
請求項3に記載のトルクコンバータ。 - 前記ステータ側部材の外筒状部の外周部には軸方向の沿って延びる複数の歯が形成されており、
前記ステータの内周部には、前記複数の歯に噛み合う複数の歯が形成されている、
請求項3に記載のトルクコンバータ。 - 前記インペラー、タービン及びステータによって構成されるトーラスの内外径比は0.55以上であり、
前記ステータブレーキは前記トーラスの内周側に配置されている、
請求項1に記載のトルクコンバータ。
Priority Applications (4)
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DE112009001985T DE112009001985T5 (de) | 2008-08-21 | 2009-08-05 | Drehmomentwandler |
US13/056,879 US20110132709A1 (en) | 2008-08-21 | 2009-08-05 | Torque converter |
CN200980131994.8A CN102124252A (zh) | 2008-08-21 | 2009-08-05 | 扭矩转换器 |
KR1020117003023A KR101317747B1 (ko) | 2008-08-21 | 2009-08-05 | 토크 컨버터 |
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JP2008212311A JP4684321B2 (ja) | 2008-08-21 | 2008-08-21 | トルクコンバータ |
JP2008-212311 | 2008-08-21 |
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WO2010021243A1 true WO2010021243A1 (ja) | 2010-02-25 |
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US (1) | US20110132709A1 (ja) |
JP (1) | JP4684321B2 (ja) |
KR (1) | KR101317747B1 (ja) |
CN (1) | CN102124252A (ja) |
DE (1) | DE112009001985T5 (ja) |
WO (1) | WO2010021243A1 (ja) |
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WO2012132740A1 (ja) | 2011-03-31 | 2012-10-04 | アイシン・エィ・ダブリュ株式会社 | 発進装置 |
KR101326819B1 (ko) * | 2011-07-29 | 2013-11-11 | 현대자동차주식회사 | 자동차의 토크 컨버터 |
WO2015100017A1 (en) * | 2013-12-13 | 2015-07-02 | Schaeffler Technologies Gmbh & Co. Kg | Torque converter including stator thrust bearing |
US10260608B2 (en) | 2014-04-17 | 2019-04-16 | Schaeffler Technologies AG & Co. KG | Hub assembly for a torque converter and related method |
CN106536989B (zh) | 2014-07-16 | 2019-04-05 | 舍弗勒技术股份两合公司 | 具有减小的背压的变矩器离合器 |
US9611925B2 (en) * | 2015-02-12 | 2017-04-04 | Zhongtai Chen | Torque converter having a reactor controlled by a jaw clutch |
US9739358B2 (en) * | 2015-04-15 | 2017-08-22 | Valeo Embrayages | Hydrokinetic torque coupling device having damper-piston lockup clutch, and related method |
US9677654B2 (en) * | 2015-07-24 | 2017-06-13 | Schaeffler Technologies AG & Co. KG | Torque converter with a selective pressure activated seal system |
JP6656967B2 (ja) * | 2016-03-18 | 2020-03-04 | 株式会社エクセディ | トルクコンバータのロックアップ装置 |
KR102440528B1 (ko) * | 2018-04-23 | 2022-09-06 | 현대자동차주식회사 | 별실 적용 토크컨버터 |
US10975960B2 (en) * | 2018-04-24 | 2021-04-13 | Allison Transmission, Inc. | Dual clutch control system for integral torque converter and retarder and method thereof |
US10895311B2 (en) * | 2018-05-15 | 2021-01-19 | Schaeffler Technologies AG & Co. KG | Four-pass torque converter with variable-pitch stator and bypass clutch |
US10571004B2 (en) | 2018-05-15 | 2020-02-25 | Schaeffler Technologies AG & Co. KG | Variable-pitch stator for torque converter |
US10520072B2 (en) | 2018-05-15 | 2019-12-31 | Schaeffler Technologies AG & Co. KG | Passive variable-pitch stator for torque converter |
US20200040975A1 (en) * | 2018-07-31 | 2020-02-06 | Schaeffler Technologies AG & Co. KG | Hydraulically actuated stator clutch |
US10792991B2 (en) * | 2018-12-05 | 2020-10-06 | Schaeffler Technologies AG & Co. KG | Hybrid module including torque converter having a stator friction brake |
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- 2009-08-05 KR KR1020117003023A patent/KR101317747B1/ko not_active IP Right Cessation
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KR101317747B1 (ko) | 2013-10-15 |
CN102124252A (zh) | 2011-07-13 |
KR20110034663A (ko) | 2011-04-05 |
JP2010048316A (ja) | 2010-03-04 |
DE112009001985T5 (de) | 2013-03-28 |
JP4684321B2 (ja) | 2011-05-18 |
US20110132709A1 (en) | 2011-06-09 |
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