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WO2014098353A1 - Convertisseur de couple pour véhicule - Google Patents

Convertisseur de couple pour véhicule Download PDF

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Publication number
WO2014098353A1
WO2014098353A1 PCT/KR2013/008611 KR2013008611W WO2014098353A1 WO 2014098353 A1 WO2014098353 A1 WO 2014098353A1 KR 2013008611 W KR2013008611 W KR 2013008611W WO 2014098353 A1 WO2014098353 A1 WO 2014098353A1
Authority
WO
WIPO (PCT)
Prior art keywords
impeller
torque converter
reactor
turbine
outer race
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Ceased
Application number
PCT/KR2013/008611
Other languages
English (en)
Korean (ko)
Inventor
권의섭
김진문
장재덕
주인식
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Korea Powertrain Co Ltd
Original Assignee
Korea Powertrain Co Ltd
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Korea Powertrain Co Ltd filed Critical Korea Powertrain Co Ltd
Publication of WO2014098353A1 publication Critical patent/WO2014098353A1/fr
Anticipated expiration legal-status Critical
Ceased legal-status Critical Current

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H41/00—Rotary fluid gearing of the hydrokinetic type
    • F16H41/24—Details
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H45/00—Combinations of fluid gearings for conveying rotary motion with couplings or clutches 
    • F16H45/02—Combinations of fluid gearings for conveying rotary motion with couplings or clutches  with mechanical clutches for bridging a fluid gearing of the hydrokinetic type
    • F16H2045/0205—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
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H45/00—Combinations of fluid gearings for conveying rotary motion with couplings or clutches 
    • F16H45/02—Combinations of fluid gearings for conveying rotary motion with couplings or clutches  with mechanical clutches for bridging a fluid gearing of the hydrokinetic type
    • F16H2045/0221—Combinations of fluid gearings for conveying rotary motion with couplings or clutches  with mechanical clutches for bridging a fluid gearing of the hydrokinetic type with damping means
    • F16H2045/0226—Combinations of fluid gearings for conveying rotary motion with couplings or clutches  with mechanical clutches for bridging a fluid gearing of the hydrokinetic type with damping means comprising two or more vibration dampers
    • 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
    • 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
    • F16H41/26—Shape of runner blades or channels with respect to function

Definitions

  • the present invention relates to a vehicle torque converter that can simply configure a one-way clutch structure for supporting the reactor to increase the cost reduction and design freedom.
  • the torque converter is installed between the engine of the vehicle and the transmission to transmit the driving force of the engine to the transmission using a fluid.
  • a torque converter receives a driving force of an engine, a turbine that rotates by an impeller that is rotated by oil discharged from an impeller, and a reactor that increases the rate of change of torque by directing the flow of oil flowing back to the impeller in a direction of rotation of the impeller ('stator' "Also".
  • torque converters are equipped with a lock-up clutch (also called a 'damper clutch'), which is a means of connecting directly between the engine and the transmission, as the load on the engine may decrease power transmission efficiency.
  • the lockup clutch is disposed between the turbine and the front cover that is connected to the engine so that the rotational power of the engine can be transmitted directly to the turbine.
  • This lockup clutch includes a piston that is movably coupled in the axial direction. And a torsional damper capable of absorbing shock and vibration acting in the rotational direction of the shaft when the lockup clutch is operated may be coupled to the lockup clutch.
  • the one-way clutch is disposed on the inner circumferential surface (the rotation center side).
  • Wenway clutches include inner races, multiple bearings and outer races from the center of rotation. That is, since the outer race of the one-way clutch is coupled to the inner circumferential surface of the reactor, the reactor is installed in a structure capable of rotating only in one direction.
  • the structure using the conventional one-way clutch has a problem in that the cost of expensive components is increased and the space required for securing the space due to the complicated structure is inferior in design freedom.
  • an object of the present invention is to provide a torque converter for a vehicle to reduce the cost and at the same time increase the design freedom through a simple structure that can omit and replace the one-way clutch It is.
  • the present invention is a front cover, the impeller coupled to the front cover to rotate, the turbine disposed in the position facing the impeller to rotate together in accordance with the rotation of the impeller, the impeller And a reactor positioned between the turbine and the turbine to change the flow of oil from the turbine to the impeller, a lockup clutch for directly transmitting a driving force of the front cover to a transmission, and springs coupled to the lockup clutch and disposed in the circumferential direction of the shaft. It includes a damper to absorb vibration and shock in the rotational direction,
  • the reactor includes an outer race coupled to the inner circumferential surface of the reactor and having an inner race provided with a first tapered portion on the inner circumferential surface, and an inner race having a second tapered portion contacting the inner circumferential surface of the outer race and corresponding to the first tapered portion.
  • an outer race coupled to the inner circumferential surface of the reactor and having an inner race provided with a first tapered portion on the inner circumferential surface, and an inner race having a second tapered portion contacting the inner circumferential surface of the outer race and corresponding to the first tapered portion.
  • the first tapered portion is provided at the inner diameter of the outer race
  • the second tapered portion is provided at the outer diameter of the inner race
  • first taper portion and the second taper portion are positioned at the center portions of the outer race and the inner race, and both side sides of the first taper portion and the second taper portion are horizontal portions.
  • the first taper portion and the second taper portion are preferably smaller in diameter toward the front cover side.
  • the said 1st taper part and the said 2nd taper part become the range of inclination of 0.5-2 degrees.
  • the reactor can remain locked or freely rotated due to the difference between the ratio of the impeller rotation speed and the turbine rotation speed, thereby reducing costs and increasing design freedom through a simple structure. It works.
  • FIG. 1 is a cross-sectional view of a torque converter for explaining an embodiment of the present invention.
  • FIG. 2 is an enlarged view of an inner race and an outer race which are main components of the present invention.
  • FIG 3 is a view showing the oil flow when the rotational speed of the turbine is relatively slow with respect to the rotational speed of the impeller.
  • FIG. 4 is a view showing the direction of the force acting on the outer race when the rotational speed of the turbine is relatively slow or close to the rotational speed of the impeller.
  • Fig. 5 is a diagram showing the oil flow when the rotational speed of the turbine approaches the rotational speed of the impeller.
  • FIG. 1 is a half sectional view of a vehicle torque converter cut in an axial direction to explain an embodiment of the present invention.
  • the torque converter according to the embodiment of the present invention is disposed at a position facing the impeller 6 and the impeller 6, which are connected to the crankshaft of the engine to rotate and the front cover 4, which is connected to the front cover 4 to rotate together.
  • Turbine (8) and a reactor located between the impeller (6) and the turbine (8) to divert the flow of oil from the turbine (8) to the impeller (6).
  • the reactor 10 delivering oil to the impeller 6 side has the same center of rotation as the front cover 4.
  • the torque converter of the embodiment of the present invention is provided with a lockup clutch 14 as a means of directly connecting the engine and the transmission. This lockup clutch 14 is arranged between the front cover 4 and the turbine 8.
  • the lockup clutch 14 is formed in a substantially disk shape and has a piston 16 that can move in the axial direction.
  • the torsional damper 20 transmits the driving force transmitted through the lockup clutch 14 to the turbine 8 to absorb the torsional force acting in the rotational direction of the shaft and to damp vibration.
  • the lockup clutch 14 described above comprises a friction plate 33 disposed between the front cover 4 and the piston 16.
  • the friction plate 33 is coupled to the friction material 35 on both sides. Therefore, when the piston 16 moves in the direction toward the front cover 4 by the hydraulic pressure, the lockup clutch 14 is brought into close contact with the front cover 4 and the piston 16 and the front cover 4.
  • the transmitted driving force may be transmitted to the friction plate 33.
  • the torsional damper 20 includes a drive plate 37, a cover plate 39, an outside spring 41, an inside spring 43, and a driven plate 45, as shown in FIG. 1. can do.
  • the drive plate 37 may be coupled to the friction plate 33 of the lockup clutch 14 to receive a driving force.
  • the drive plate 37 is coupled to the cover plate 39 can be integrally rotated.
  • the cover plate 39 may be disposed in plural in pairs, and the outside spring 41 and the inside spring 43 may be disposed in the circumferential direction.
  • the outside spring 41 is preferably disposed in the circumferential direction on the outer circumferential side of the inside spring 43. These outside springs 41 and inside springs 43 can absorb vibrations and shocks in the rotational direction by elastic force when the lock-up clutch 14 operates.
  • the driven plate 45 may elastically support one side of the outside spring 41 and the inside spring 43.
  • the driven plate 45 may be connected to the spline hub 47 that transmits the driving force to the transmission to transmit the driving force.
  • the driven plate 45 may receive the driving force through the outside spring 41 and the inside spring 43 and transmit the driving force to the spline hub 47.
  • the outer race 49 and the inner race 51 is disposed on the rotation center axis of the reactor 10.
  • the outer race 49 is disposed on the inner circumferential surface of the reactor 10.
  • the inner race 51 is disposed on the inner circumferential surface of the outer race 49.
  • the outer race 49 has a substantially cylindrical shape and is provided with a first taper portion 49a at the center of the inner circumferential surface. As shown in FIG. 2, the 1st taper part 49a is provided in the middle part a of the outer race 49, and is made into the shape which diameter becomes small toward the front cover 4 side. In addition, both side portions t1 and t2 of the first tapered portion 49a of the outer race 49 are made up of the horizontal portion 49b. That is, the inner diameter of the outer race 49 is circular in the horizontal portion 49b disposed on both sides of the first taper portion 49a. The horizontal portion 49b disposed on both sides of the first taper portion 49a may serve to maintain the center of the outer race 49 and the inner race 51.
  • the inner race 51 is disposed in the inner diameter of the outer race 49 in a structure corresponding to the outer race 49. That is, the inner race 51 is provided with the 2nd taper part 51a in the outer peripheral surface, and the other horizontal part 51b is provided in the both sides of the 2nd taper part 51a. Since the second tapered portion 51a and the other horizontal portion 51b of the inner race 51 correspond to the first tapered portion 49a and the horizontal portion 49b of the outer race 49 described above, a detailed description thereof will be provided. Will be omitted.
  • the angle which the 1st taper part 49a and the 2nd taper part 51a make is about 0.5-2 degrees.
  • the driving force of the engine is the front cover 4, the impeller 6, the turbine 8, the cover plate 39, the outside spring 41 and the inside spring 43.
  • the driving force is transmitted to the transmission through the driven plate 45 and the spline hub 47.
  • the outside spring 41 and the inside spring 43 may absorb vibration and shock in the rotational direction.
  • the piston 16 moves to the front cover 4 side by hydraulic pressure. Then, the friction materials 35 provided on both sides of the friction plate 33 are in close contact with one side of the front cover 4 and one side of the piston 16, and the driving force of the front cover 4 is transmitted to the friction plate 33. And the driving force transmitted to the friction plate 33 is transmitted to the drive plate 37. Since the drive plate 37 is integrally formed with the cover plate 39, the driving force is transmitted to the cover plate 39.
  • the cover plate 39 compresses the outside spring 41 and the inside spring 43. At this time, the outside spring 41 and the inside spring 43 absorbs vibration and shock in the rotational direction.
  • the driving force transmitted to the driven plate 45 is transmitted to the transmission through the spline hub 47.
  • the fluid enters the inner direction B of the blade b2 of the reactor 10 by the difference in rotational speeds of the impeller 6 and the turbine 8, and passes through the reactor 10. Due to the shape of the blade b2 of (10), this fluid also moves in the direction of the impeller 6 while moving in the A direction, so that the moving energy Fs of this fluid also acts in the direction of the impeller 6 (see Fig. 3). )
  • the moving energy of the fluid generated when the fluid moves from the turbine 8 side to the impeller 6 side and the moving energy generated while the fluid moves from the reactor 10 side to the impeller 6 side are added to the outer force. It acts to move the race 49 in the direction of the impeller 6.
  • the moving energy of the fluid from the turbine 8 side to the impeller 6 side is the same in the same direction as in the above case, the fluid flowing into the reactor 10 side as shown in FIG. Since it flows to the back side of the blade b2 of 10), the moving energy Fs according to the movement of the fluid acts in the left direction (turbine direction) as shown in FIG.
  • the embodiment of the present invention can perform the work performed by the conventional one-way clutch through a simple structure, and is particularly suitable for a system that does not use much of the lockup clutch function.
  • This embodiment of the present invention can replace the conventional one-way clutch with a simple structure can increase the cost reduction and design freedom.
  • the embodiment of the present invention can eliminate the thrust needle bearing disposed between the impeller (6) and the reactor (10) can reduce the number of parts, the structure is simpler, it is possible to improve the productivity.

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

Abstract

La présente invention concerne un convertisseur de couple destiné à un véhicule, qui peut réduire les coûts de fabrication et augmenter un degré de liberté dans la conception en simplifiant la structure d'embrayage unidirectionnel d'un réacteur. Le convertisseur de couple destiné à un véhicule selon la présente invention comprend un capot avant, un rotor, une turbine et un réacteur. Le réacteur comprend un chemin de roulement externe qui est accouplé le long d'une circonférence interne du réacteur et qui comporte une première partie conique prévue sur sa circonférence interne ; et un chemin de roulement interne qui vient en contact avec la circonférence interne du chemin de roulement externe et qui comporte une seconde partie conique correspondant à la première partie conique.
PCT/KR2013/008611 2012-12-17 2013-09-26 Convertisseur de couple pour véhicule Ceased WO2014098353A1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
KR20120147594 2012-12-17
KR10-2012-0147594 2012-12-17

Publications (1)

Publication Number Publication Date
WO2014098353A1 true WO2014098353A1 (fr) 2014-06-26

Family

ID=50978634

Family Applications (1)

Application Number Title Priority Date Filing Date
PCT/KR2013/008611 Ceased WO2014098353A1 (fr) 2012-12-17 2013-09-26 Convertisseur de couple pour véhicule

Country Status (1)

Country Link
WO (1) WO2014098353A1 (fr)

Cited By (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2016073043A1 (fr) * 2014-11-07 2016-05-12 Schaeffler Technologies AG & Co. KG Embrayage à cône de stator
US9897184B2 (en) 2014-11-07 2018-02-20 Schaeffler Technologies AG & Co. KG Stator cone clutch
DE102016219266A1 (de) 2016-10-05 2018-04-05 Zf Friedrichshafen Ag Hydrodynamischer Kreis eines Anfahrelementes

Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4280370A (en) * 1979-03-08 1981-07-28 Zahnradfabrik Friedrichshafen Ag Clutch assembly for gear-type transmission system
US20030115862A1 (en) * 2001-12-26 2003-06-26 Jatco Ltd. Torque converter
US20080072586A1 (en) * 2006-09-26 2008-03-27 Hammond Matthew D Drive unit for hybrid electric vehicle
JP2008175250A (ja) * 2007-01-17 2008-07-31 Nissan Motor Co Ltd 変速機の同期装置
KR20100132818A (ko) * 2009-06-10 2010-12-20 한국파워트레인 주식회사 차량용 토크 컨버터

Patent Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4280370A (en) * 1979-03-08 1981-07-28 Zahnradfabrik Friedrichshafen Ag Clutch assembly for gear-type transmission system
US20030115862A1 (en) * 2001-12-26 2003-06-26 Jatco Ltd. Torque converter
US20080072586A1 (en) * 2006-09-26 2008-03-27 Hammond Matthew D Drive unit for hybrid electric vehicle
JP2008175250A (ja) * 2007-01-17 2008-07-31 Nissan Motor Co Ltd 変速機の同期装置
KR20100132818A (ko) * 2009-06-10 2010-12-20 한국파워트레인 주식회사 차량용 토크 컨버터

Cited By (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2016073043A1 (fr) * 2014-11-07 2016-05-12 Schaeffler Technologies AG & Co. KG Embrayage à cône de stator
US9810303B2 (en) 2014-11-07 2017-11-07 Schaeffler Technologies Ag & Co. Stator cone clutch
US9897184B2 (en) 2014-11-07 2018-02-20 Schaeffler Technologies AG & Co. KG Stator cone clutch
DE102016219266A1 (de) 2016-10-05 2018-04-05 Zf Friedrichshafen Ag Hydrodynamischer Kreis eines Anfahrelementes

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