[go: up one dir, main page]

WO2011102220A1 - Dispositif de verrouillage - Google Patents

Dispositif de verrouillage Download PDF

Info

Publication number
WO2011102220A1
WO2011102220A1 PCT/JP2011/052112 JP2011052112W WO2011102220A1 WO 2011102220 A1 WO2011102220 A1 WO 2011102220A1 JP 2011052112 W JP2011052112 W JP 2011052112W WO 2011102220 A1 WO2011102220 A1 WO 2011102220A1
Authority
WO
WIPO (PCT)
Prior art keywords
piston
turbine
lockup device
claw
driven
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/JP2011/052112
Other languages
English (en)
Japanese (ja)
Inventor
裕樹 河原
直樹 富山
真次 藤本
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.)
Exedy Corp
Original Assignee
Exedy Corp
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 Exedy Corp filed Critical Exedy Corp
Priority to KR1020127022187A priority Critical patent/KR101457461B1/ko
Publication of WO2011102220A1 publication Critical patent/WO2011102220A1/fr
Anticipated expiration legal-status Critical
Ceased legal-status Critical Current

Links

Images

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
    • 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
    • F16F—SPRINGS; SHOCK-ABSORBERS; MEANS FOR DAMPING VIBRATION
    • F16F15/00—Suppression of vibrations in systems; Means or arrangements for avoiding or reducing out-of-balance forces, e.g. due to motion
    • F16F15/10—Suppression of vibrations in rotating systems by making use of members moving with the system
    • F16F15/12—Suppression of vibrations in rotating systems by making use of members moving with the system using elastic members or friction-damping members, e.g. between a rotating shaft and a gyratory mass mounted thereon
    • 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
    • F16F—SPRINGS; SHOCK-ABSORBERS; MEANS FOR DAMPING VIBRATION
    • F16F15/00—Suppression of vibrations in systems; Means or arrangements for avoiding or reducing out-of-balance forces, e.g. due to motion
    • F16F15/10—Suppression of vibrations in rotating systems by making use of members moving with the system
    • F16F15/12—Suppression of vibrations in rotating systems by making use of members moving with the system using elastic members or friction-damping members, e.g. between a rotating shaft and a gyratory mass mounted thereon
    • F16F15/131—Suppression of vibrations in rotating systems by making use of members moving with the system using elastic members or friction-damping members, e.g. between a rotating shaft and a gyratory mass mounted thereon the rotating system comprising two or more gyratory masses
    • F16F15/133—Suppression of vibrations in rotating systems by making use of members moving with the system using elastic members or friction-damping members, e.g. between a rotating shaft and a gyratory mass mounted thereon the rotating system comprising two or more gyratory masses using springs as elastic members, e.g. metallic springs
    • F16F15/134—Wound springs
    • 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
    • F16H2045/0273—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

Definitions

  • the fluid power transmission device is provided with a lockup device for directly transmitting torque from the front cover to the turbine.
  • This type of lock-up device includes, for example, a piston, a back plate, a friction coupling portion, a drive plate, a spring, and a driven plate.
  • the piston is supported by the front cover so as to be movable in the axial direction.
  • a hydraulic chamber is formed between the front cover and the piston. When the pressure in the hydraulic chamber changes, the piston moves in the axial direction.
  • the friction connecting portion is disposed between the piston and the back plate in the axial direction, and is sandwiched between the piston and the back plate when the piston moves to the turbine side.
  • power is transmitted from the front cover to the drive plate via the friction coupling portion.
  • the drive plate is rotatably provided with respect to the turbine, and supports the spring so as to be elastically deformable.
  • the driven plate is elastically connected in the rotational direction by a spring and is fixed to the turbine (see, for example, Patent Document 1).
  • a so-called drag torque may be generated when hydraulic oil flows in the friction portion.
  • An object of the present invention is to provide a lockup device capable of reducing drag torque.
  • the lockup device according to the present invention is a device for mechanically connecting the front cover and the turbine, which is disposed in a space between the front cover and the turbine of the fluid power transmission device.
  • This lockup device includes a piston, a driven member, an elastic member, and a connecting member.
  • the piston is supported by the turbine so as to be movable and rotatable in the axial direction, and moves in the axial direction in accordance with a change in pressure.
  • the driven member is fixed to the turbine.
  • the elastic member elastically connects the piston to the driven member in the rotational direction.
  • the connecting member connects the piston to the driven member.
  • the torque converter 1 is a device for transmitting power from a crankshaft (not shown) on the engine side to an input shaft (not shown) of a transmission, and includes a front cover 2 coupled to the crankshaft, an impeller 3, , A turbine 4, a stator 5, and a lockup device 7.
  • the front cover 2 includes an annular cover body 10, an annular support plate 2 a fixed to the cover body 10, and a disc-shaped back plate 2 b fixed to the cover body 10.
  • the support plate 2a supports a second friction plate 52 (described later) of the lockup device 7 so as to be movable in the axial direction and integrally rotatable, and is disposed on the inner side in the radial direction of the second friction plate 52.
  • the impeller 3 includes an impeller shell 12, a plurality of impeller blades 13, and an impeller hub 14.
  • the impeller shell 12 is fixed to the front cover 2.
  • the plurality of impeller blades 13 are fixed to the impeller shell 12.
  • the impeller hub 14 is fixed to the inner peripheral portion of the impeller shell 12.
  • a fluid chamber filled with hydraulic oil is formed by the front cover 2 and the impeller 3.
  • the turbine 4 is connected to the input shaft of the transmission, and is disposed to face the impeller 3 in the fluid chamber.
  • the turbine 4 includes a turbine shell 15, a plurality of turbine blades 16, and a turbine hub 17.
  • the turbine blade 16 is fixed to the turbine shell 15.
  • the turbine hub 17 is fixed to the inner periphery of the turbine shell 15.
  • the turbine hub 17 has a disk-shaped flange 17a and a turbine hub body 17b.
  • the turbine hub body 17b is connected to the input shaft of the transmission.
  • the flange 17a extends radially outward from the turbine hub body 17b.
  • An inner peripheral portion of the turbine shell 15 is fixed to the flange 17 a by a plurality of rivets 18.
  • the stator 5 is a mechanism for rectifying hydraulic oil returning from the turbine 4 to the impeller 3, and is disposed between the impeller 3 and the inner peripheral portion of the turbine 4.
  • the stator 5 includes a disk-shaped stator carrier 20, a plurality of stator blades 21 provided on the outer periphery of the stator carrier 20, and a one-way clutch 22.
  • the stator carrier 20 is supported by a fixed shaft (not shown) via a one-way clutch 22.
  • the lockup device 7 is a device for mechanically connecting the front cover 2 and the turbine 4, and is disposed in a space between the front cover 2 of the torque converter 1 and the turbine 4. ing. As shown in FIGS. 1 and 2, the lockup device 7 includes a piston 30, a plurality of springs 33 (an example of an elastic member), a first friction plate 51, a second friction plate 52, and a driven plate 35 ( An example of a driven member) and a connection ring 60 (an example of a connection member).
  • the spring is described as an example of the elastic member, but the elastic member may be another member as long as it is a member that can absorb torsional vibration.
  • the piston 30 has two members, ie, the piston main body 36 and the retaining plate 37, but the whole piston 30 may be integrally formed, and the piston 30 is composed of three or more members. Also good.
  • Piston 30 The piston 30 is arranged so as to divide the space between the front cover 2 and the turbine 4 into two in the axial direction. A space between the front cover 2 and the turbine 4 is roughly divided into a first space A and a second space B by the piston 30.
  • the piston 30 is supported by the turbine 4 so as to be movable and rotatable in the axial direction, and moves in the axial direction in accordance with a change in pressure. Specifically, when a pressure difference is generated between the first space A and the second space B, the piston 30 moves in the axial direction with respect to the front cover 2 and the turbine 4.
  • the piston 30 has a piston body 36, a retaining plate 37, and a plurality of rivets 40.
  • the piston body 36 is a member for pressing the first friction plate 51 and the second friction plate 52 toward the front cover 2, and is disposed on the turbine 4 side of the first friction plate 51 and the second friction plate 52. .
  • the piston body 36 is supported by the turbine hub body 17b of the turbine hub 17 so as to be movable and rotatable in the axial direction.
  • the piston main body 36 includes a sliding portion 30b disposed on the turbine 4 side of the second friction plate 52, a plurality of outer peripheral claw portions 30c disposed on the outer peripheral side of the sliding portion 30b, and a cylindrical portion 30d. Have.
  • the sliding portion 30 b is an annular portion that presses the first friction plate 51 and the second friction plate 52 toward the front cover 2.
  • the sliding portion 30 b is disposed in the vicinity of the second friction plate 52.
  • the outer peripheral claw portion 30c extends in the axial direction from the outer peripheral portion of the sliding portion 30b.
  • the outer peripheral claw portion 30c supports the first friction plate 51 so as to be movable in the axial direction and integrally rotatable.
  • the plurality of outer peripheral claw portions 30 c are arranged at equal intervals in the circumferential direction.
  • the cylindrical portion 30 d is a portion that slides with the turbine hub body 17 b of the turbine 4.
  • a seal ring 38 is embedded in the turbine hub body 17b, and the cylindrical portion 30d and the sliding portion of the turbine hub body 17b are sealed by the seal ring 38.
  • the retaining plate 37 is fixed to the piston main body 36 by a rivet 40, and supports the spring 33 so as to be elastically deformable.
  • the retaining plate 37 includes an annular fixing portion 37a fixed to the piston main body 36, and a support portion 37b disposed on the outer peripheral portion of the fixing portion 37a.
  • the fixed portion 37 a is disposed on the turbine 4 side of the piston main body 36.
  • An inner peripheral portion of the fixed portion 37 a is fixed to the piston body 36.
  • a plurality of openings 37c are formed in the fixing portion 37a.
  • the opening 37 c is disposed at the same circumferential position as the connection intermediate part 62 and the claw tip 63 of the connection ring 60.
  • the connecting intermediate part 62 is inserted into the opening 37c.
  • the opening 37c has a first opening 37e, a second opening 37f, and a third opening 37g.
  • the first opening 37e is disposed at a position corresponding to the connection intermediate portion 62 and the claw tip 63, and is formed slightly larger than the connection intermediate portion 62 and the claw tip 63.
  • the second opening 37f is formed on the outer side in the radial direction of the first opening 37e, and is connected to the first opening 37e.
  • the second opening 37f is formed to be longer in the circumferential direction than the first opening 37e, and is disposed at substantially the same radial position as the annular portion 61.
  • the annular part 61 can be elastically deformed in the axial direction, and when the claw part tip 63 is hooked on the driven plate 35, the connecting intermediate part 62 and the claw part tip 63 are pushed into the turbine 4 side. (See, for example, FIG. 5C).
  • the third opening 37g is formed on the outer side in the radial direction of the second opening 37f, and is connected to the second opening 37f.
  • the third opening 37g is formed longer in the circumferential direction than the second opening 37f. A part of the annular portion 61 overlaps the third opening 37g.
  • the spring 33 elastically connects the piston 30 and the turbine 4 in the rotational direction.
  • the spring 33 is accommodated in the support portion 37 b of the retaining plate 37.
  • the end portion of the spring 33 is supported in the rotation direction by the contact portion 37d.
  • the spring 33 is disposed between the adjacent contact portions 37d.
  • a protrusion 35 c of the driven plate 35 is inserted between the adjacent springs 33 in the axial direction.
  • the driven plate 35 is in contact with the end of the spring 33 in the rotational direction, and is fixed to the outer periphery of the turbine 4.
  • the driven plate 35 includes an annular fixed portion 35 a fixed to the turbine 4, a plurality of protrusions 35 c that can support the end of the spring 33, and an inner periphery of the fixed portion 35 a.
  • an annular claw portion 35b provided in the portion.
  • the protrusion 35 c protrudes from the outer peripheral portion of the fixed portion 35 a toward the piston 30 and is inserted into the support portion 37 b of the retaining plate 37.
  • the claw portion 35b protrudes from the inner peripheral portion of the fixed portion 35a to the piston 30 side.
  • a gap S is secured between the claw portion 35b and the turbine 4 in the axial direction.
  • the connection ring 60 is hooked on the claw portion 35b, and the claw portion tip 63 of the connection ring 60 is disposed in the gap S.
  • the driven plate 35 is provided with a first tapered surface 35d in consideration of the assembly of the connecting ring 60.
  • the first tapered surface 35d is formed at the end of the claw portion 35b.
  • the first tapered surface 35d is inclined with respect to the axial direction and faces the piston 30.
  • FIGS. 5A to 5C when the connecting ring 60 is assembled, the claw portion tip 63 of the connecting ring 60 slides on the first tapered surface 35d, and the radius is increased by the first tapered surface 35d. Guided inward direction. The assembly work will be described later.
  • the first friction plate 51 is disposed between the piston 30 and the front cover 2 in the axial direction.
  • the first friction plate 51 is disposed on the radially inner side of the spring 33, and is disposed so as to be movable in the axial direction and integrally rotatable with respect to the front cover 2.
  • the first friction plate 51 is supported by the outer peripheral claw portion 30c of the piston 30 so as to be movable in the axial direction and integrally rotatable.
  • Second friction plate 52 The second friction plate 52 is disposed between the piston 30 and the front cover 2 in the axial direction. More specifically, the second friction plate 52 is disposed between the first friction plate 51 and the sliding portion 30b. The second friction plate 52 is disposed on the radially inner side of the spring 33, and is disposed so as to be movable in the axial direction and rotatable integrally with the piston 30. The second friction plate 52 is supported by the support plate 2a of the front cover 2 so as to be movable in the axial direction and integrally rotatable.
  • the connecting ring 60 has an annular portion 61 disposed on the front cover 2 side of the piston 30 and a plurality of connecting claw portions 65 extending from the annular portion 61 on the turbine 4 side. is doing.
  • the connection ring 60 is integrally formed from a single plate.
  • the annular portion 61 is formed of an annular plate, and is disposed on the radially inner side of the support portion 37 b of the retaining plate 37 as shown in FIGS. 2 and 4.
  • the annular portion 61 is disposed on the radially outer side than the outer peripheral claw portion 30 c of the piston main body 36.
  • the annular portion 61 is thinner than the driven plate 35 and is elastically deformable in the axial direction with a relatively small force.
  • the annular portion 61 is slightly elastically deformed in the axial direction, and the driven plate 35 is pulled toward the piston 30 via the connecting claw portion 65.
  • the cylindrical portion 30 d of the piston 30 is in contact with the turbine hub 17. Therefore, the piston 30 is held in the axial direction at the position shown in FIG.
  • the claw portion tip 63 protrudes radially outward from the end portion of the connecting intermediate portion 62, and is in contact with the claw portion 35b in the axial direction.
  • the claw portion 35b and the claw portion tip 63 slide.
  • the claw portion tip 63 is provided with a second tapered surface 63a.
  • the second taper surface 63 a is inclined with respect to the axial direction and faces the turbine 4.
  • the first tapered surface 35d of the driven plate 35 guides the claw portion tip 63 radially inward.
  • the second tapered surface 63a slides with the first tapered surface 35d.
  • the first taper surface 35d and the second taper surface 63a are inclined by about 45 degrees with respect to the axial direction, but the inclination angles of the first taper surface 35d and the second taper surface 63a are limited to 45 degrees. Not.
  • the connecting ring 60 is assembled to the retaining plate 37 and the driven plate 35.
  • the annular portion 61 is disposed on the outer side in the radial direction with respect to the outer peripheral claw portion 30c, but the radial positions of the connecting intermediate portion 62 and the claw portion tip 63 are substantially the same as the radial positions of the outer peripheral claw portion 30c. For this reason, when the connecting ring 60 is assembled to the retaining plate 37 and the driven plate 35, it is expected that the connecting ring 60 interferes with the outer peripheral claw portion 30 c of the piston body 36.
  • the opening 37 c when viewed from the axial direction, the opening 37 c is disposed between the adjacent outer peripheral claw portions 30 c, and accordingly, the connection intermediate portion 62 and the claw portion tip 63 of the connection ring 60. Are also inserted between the adjacent outer peripheral claw portions 30c. For this reason, the coupling ring 60 does not interfere with the piston main body 36 during assembly, and the coupling claw portion 65 of the coupling ring 60 can be inserted into the opening 37c as shown in FIG.
  • connection ring 60 When the connecting claw portion 65 is further pushed into the turbine 4 side while the annular portion 61 is in contact with the retaining plate 37, the claw tip end 63 enters the turbine 4 side of the claw portion 35b, and the connecting intermediate portion 62 is in the original state. Return to. Thus, the assembly of the connection ring 60 is completed. ⁇ Operation> Next, the operation of the torque converter 1 will be described.
  • the front cover 2 and the piston 30 may rotate relative to each other.
  • the piston 30 is attracted to the front cover 2 side, and so-called drag torque may be generated by the hydraulic oil around the first friction plate 51 and the second friction plate 52.
  • the piston 30 is hardly pulled toward the front cover 2 because the piston 30 is pulled toward the turbine 4 by the connecting ring 60. Therefore, the generation of drag torque can be suppressed.
  • connection ring 60 is an integral member, but the connection ring 60 may be composed of a plurality of members.
  • connection ring unit 160 is composed of two members. Specifically, the connection ring unit 160 includes a wire ring 165 (an example of a ring member) and a connection ring 169 that connects the wire ring 165 and the driven plate 135.
  • the connection ring 169 includes an annular portion 161 hooked on the claw portion 135 b and a plurality of connection claw portions 168 hooked on the wire ring 165.
  • the annular portion 161 is disposed between the piston 30 and the turbine 4 in the axial direction, and is formed by bending an annular plate. Specifically, the annular portion 161 has a disc portion 163 and a cylindrical portion 162.
  • the disc portion 163 is an annular plate and is disposed between the claw portion 135 b of the driven plate 135 and the turbine 4.
  • the disc portion 163 is in contact with the claw portion 135b in the axial direction, and when the piston 30 and the turbine 4 rotate relative to each other, the claw portion 135b and the disc portion 163 slide.
  • the cylindrical portion 162 extends from the inner peripheral edge of the disc portion 163 to the piston 30 side, and is disposed on the radially inner side of the claw portion 135b.
  • the plurality of connecting claws 168 are arranged at equal intervals in the circumferential direction.
  • the connecting claw portion 168 extends from the annular portion 161 to the turbine 4 side, and is formed by bending a plate-like portion protruding from the annular portion 161.
  • the connecting claw portion 168 includes a claw portion tip 166 disposed on the opposite side of the driven plate 35 from the piston 30, and a connecting intermediate portion 164 that connects the annular portion 61 and the claw portion tip 166. ing.
  • the connecting intermediate portion 164 extends from the tubular portion 162 to the front cover 2 side, and further extends obliquely outward from the tubular portion 162 in the radial direction.
  • the connecting intermediate portion 164 passes through the opening 37 c of the retaining plate 37.
  • a claw end 166 is formed at the end of the connecting intermediate portion 164.
  • the claw portion tip 166 is disposed on the side of the retaining plate 37 opposite to the turbine 4 (front cover 2 side), and the end portion of the coupling intermediate portion 164 is bent inward in the radial direction.
  • the claw portion tip 166 protrudes radially inward from the end of the connecting intermediate portion 164, but is disposed on the radially outer side of the tubular portion 162 of the annular portion 161.
  • the claw portion 235b extends radially inward and axially from the inner peripheral portion of the fixed portion 235a.
  • a gap S is secured between the fixed portion 235 a and the turbine 4.
  • a claw portion tip 263 of the connecting plate 260 is disposed in the gap S.
  • the connecting claw portion 269 is hooked on the driven plate 235, and has a cylindrical connecting intermediate portion 262 and a claw portion tip 263.
  • the connection intermediate portion 262 extends from the outer peripheral edge of the connection plate main body 261 to the turbine 4 side, and is disposed on the radially inner side of the claw portion 235b.
  • the claw portion tip 263 is an annular portion that extends radially outward from the end of the connecting intermediate portion 262 on the turbine 4 side, and is formed by bending the end of the connecting intermediate portion 262.
  • the claw portion tip 263 is in contact with the claw portion 235b in the axial direction.
  • the claw portion tip 263 is provided with a tapered surface 263a.
  • the tapered surface 263a is inclined with respect to the axial direction and faces the turbine 4. In the present embodiment, the tapered surface 263a is inclined about 45 degrees with respect to the axial direction.

Landscapes

  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Physics & Mathematics (AREA)
  • Acoustics & Sound (AREA)
  • Aviation & Aerospace Engineering (AREA)
  • Hydraulic Clutches, Magnetic Clutches, Fluid Clutches, And Fluid Joints (AREA)
  • Mechanical Operated Clutches (AREA)

Abstract

L'invention porte sur un dispositif de verrouillage (7) équipé d'une plaque entraînée (35), d'un piston (30), d'un ressort (33), et d'une bague de liaison (60). Le piston (30) est supporté par une turbine (4) de façon à pouvoir se déplacer axialement et à pouvoir tourner, et se déplace axialement en fonction changement de pression. La bague de liaison (60) relie le piston (30) à la plaque entraînée (35).
PCT/JP2011/052112 2010-02-22 2011-02-02 Dispositif de verrouillage Ceased WO2011102220A1 (fr)

Priority Applications (1)

Application Number Priority Date Filing Date Title
KR1020127022187A KR101457461B1 (ko) 2010-02-22 2011-02-02 록업 장치

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
JP2010-035754 2010-02-22
JP2010035754A JP4884543B2 (ja) 2010-02-22 2010-02-22 ロックアップ装置

Publications (1)

Publication Number Publication Date
WO2011102220A1 true WO2011102220A1 (fr) 2011-08-25

Family

ID=44482813

Family Applications (1)

Application Number Title Priority Date Filing Date
PCT/JP2011/052112 Ceased WO2011102220A1 (fr) 2010-02-22 2011-02-02 Dispositif de verrouillage

Country Status (3)

Country Link
JP (1) JP4884543B2 (fr)
KR (1) KR101457461B1 (fr)
WO (1) WO2011102220A1 (fr)

Families Citing this family (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP6297252B2 (ja) * 2012-09-13 2018-03-20 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
KR101803952B1 (ko) 2016-05-25 2017-12-01 한국파워트레인 주식회사 차량용 토크 컨버터
KR102215494B1 (ko) * 2018-12-31 2021-02-15 주식회사 카펙발레오 차량용 토크 컨버터

Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS59160955U (ja) * 1983-04-15 1984-10-27 日産自動車株式会社 ロツクアツプトルクコンバ−タ
JPH02118256A (ja) * 1988-10-26 1990-05-02 Daikin Mfg Co Ltd トルクコンバータ用ロックアップクラッチの摩擦装置
JPH0723850U (ja) * 1993-10-07 1995-05-02 株式会社大金製作所 トルクコンバータのロックアップ装置
JPH07180768A (ja) * 1993-12-24 1995-07-18 Nsk Warner Kk ロックアップ機構付きトルクコンバータ
JPH08312749A (ja) * 1995-05-18 1996-11-26 Nissan Motor Co Ltd トルクコンバータ

Family Cites Families (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS59160955A (ja) * 1984-02-21 1984-09-11 Matsushita Electric Ind Co Ltd 防爆式密閉形アルカリ蓄電池

Patent Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS59160955U (ja) * 1983-04-15 1984-10-27 日産自動車株式会社 ロツクアツプトルクコンバ−タ
JPH02118256A (ja) * 1988-10-26 1990-05-02 Daikin Mfg Co Ltd トルクコンバータ用ロックアップクラッチの摩擦装置
JPH0723850U (ja) * 1993-10-07 1995-05-02 株式会社大金製作所 トルクコンバータのロックアップ装置
JPH07180768A (ja) * 1993-12-24 1995-07-18 Nsk Warner Kk ロックアップ機構付きトルクコンバータ
JPH08312749A (ja) * 1995-05-18 1996-11-26 Nissan Motor Co Ltd トルクコンバータ

Also Published As

Publication number Publication date
JP4884543B2 (ja) 2012-02-29
JP2011169442A (ja) 2011-09-01
KR101457461B1 (ko) 2014-11-03
KR20120117903A (ko) 2012-10-24

Similar Documents

Publication Publication Date Title
US8857586B2 (en) Lockup device for torque converter
CN107202147B (zh) 减振装置
US20110011691A1 (en) Lockup device
KR102321117B1 (ko) 토크 컨버터의 록업 장치
JP2011047442A (ja) トルクコンバータ用ロックアップ装置
CN107202146B (zh) 液力变矩器
US7222706B2 (en) Lockup device for hydraulic torque transmission device
JP4884543B2 (ja) ロックアップ装置
KR102323869B1 (ko) 토크 컨버터의 록업 장치
JP2007292087A (ja) 流体式トルク伝達装置およびそれに用いられるロックアップ装置
JP2012077810A (ja) 流体伝動装置およびその製造方法
US6866129B2 (en) Lockup device for fluid-type torque transmission device
JP2014047811A (ja) トルクコンバータ
JP2017166668A (ja) トルクコンバータのロックアップ装置
US20080029359A1 (en) Torque Converter
JP2006090375A (ja) 流体式トルク伝達装置のロックアップ装置
JP6668124B2 (ja) トルクコンバータのロックアップ装置
JP2004116611A (ja) 流体式トルク伝達装置のロックアップ装置
KR101763415B1 (ko) 차량용 토크 컨버터
JP2004116610A (ja) ロックアップ装置のピストン連結機構
JP2003269575A5 (fr)
JP2006153029A (ja) 流体式トルク伝達装置のロックアップ装置
JP2007051752A (ja) 流体式トルク伝達装置
JP2006064065A (ja) 流体式トルク伝達装置
KR20260013231A (ko) 클러치 플레이트 안티-래틀 특징부

Legal Events

Date Code Title Description
121 Ep: the epo has been informed by wipo that ep was designated in this application

Ref document number: 11744508

Country of ref document: EP

Kind code of ref document: A1

NENP Non-entry into the national phase

Ref country code: DE

ENP Entry into the national phase

Ref document number: 20127022187

Country of ref document: KR

Kind code of ref document: A

122 Ep: pct application non-entry in european phase

Ref document number: 11744508

Country of ref document: EP

Kind code of ref document: A1