WO2005064185A1 - 流体継手 - Google Patents
流体継手 Download PDFInfo
- Publication number
- WO2005064185A1 WO2005064185A1 PCT/JP2004/017143 JP2004017143W WO2005064185A1 WO 2005064185 A1 WO2005064185 A1 WO 2005064185A1 JP 2004017143 W JP2004017143 W JP 2004017143W WO 2005064185 A1 WO2005064185 A1 WO 2005064185A1
- Authority
- WO
- WIPO (PCT)
- Prior art keywords
- turbine
- impeller
- shell
- torus
- baffle plate
- Prior art date
Links
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
- F16H41/26—Shape of runner blades or channels with respect to function
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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
- F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
- F16D33/00—Rotary fluid couplings or clutches of the hydrokinetic type
- F16D33/18—Details
- F16D33/20—Shape of wheels, blades, or channels with respect to function
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16H—GEARING
- F16H45/00—Combinations of fluid gearings for conveying rotary motion with couplings or clutches
- F16H45/02—Combinations of fluid gearings for conveying rotary motion with couplings or clutches with mechanical clutches for bridging a fluid gearing of the hydrokinetic type
- F16H2045/0273—Combinations of fluid gearings for conveying rotary motion with couplings or clutches with mechanical clutches for bridging a fluid gearing of the hydrokinetic type characterised by the type of the friction surface of the lock-up clutch
- F16H2045/0294—Single disk type lock-up clutch, i.e. using a single disc engaged between friction members
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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
Definitions
- the present invention relates to a fluid coupling, and more particularly to a fluid coupling provided between a member on the engine side of a vehicle and a transmission.
- Fluid couplings have conventionally been used as power transmission devices for ships and large vehicles. When used for automobiles, it is used as an alternative to a dry clutch device for a manual transmission.
- Such a fluid coupling has an impeller and a turbine arranged opposite to each other.
- the impeller has an impeller blade portion and an impeller hub provided on the inner peripheral side of the impeller blade portion.
- the impeller blade portion has an annular impeller shell and a plurality of impeller blades fixed to the impeller shell.
- the turbine has a turbine blade portion and a turbine knob provided on the inner peripheral side of the turbine blade portion.
- the turbine blade section has an annular turbine shell and a plurality of turbine blades fixed to the turbine shell. The impeller and the turbine are rotatably supported on each other via bearings.
- the impeller is connected to the crankshaft, which is a member on the engine side, via the front cover, and the turbine is connected to the input shaft on the transmission side. Power is transmitted by the working fluid filled in the impeller and the turbine.
- characteristics A in FIG. That is, in the low speed ratio range, the input capacitance coefficient decreases as the input capacitance coefficient increases and goes to the high speed ratio range.
- the stall state in which the speed ratio is "0" corresponds to a state in which the vehicle is stopped by stepping on the brake while the engine is idling.
- Patent document 1 Japanese Patent Application Laid-Open No. 2003-156074
- An object of the present invention is to make it possible to sufficiently reduce an input capacitance coefficient in a low speed ratio range.
- Another object of the present invention is to make it possible to sufficiently reduce the input capacity coefficient in the low speed ratio range, and to suppress the decrease in the input capacity coefficient in the speed ratio range other than the low speed ratio range. is there.
- a fluid coupling according to the present invention is provided between a transmission on a vehicle engine side and a transmission, and includes an impeller, a turbine, a bearing, and a baffle plate.
- the impeller is a member that constitutes a fluid chamber, and has an impeller blade portion and an annular impeller hub provided on the inner peripheral side of the impeller blade portion.
- the turbine is located in the fluid chamber opposite the impeller. Further, this turbine has a turbine blade part which forms a torus together with the impeller blade part, and an annular turbine knob provided on the inner peripheral side of the turbine blade part.
- the bearing rotatably supports the impeller hub with respect to the turbine knob.
- the baffle is provided in the torus and blocks a part of the flow of the working fluid flowing in the torus.
- the working fluid in the torus is formed in a perforated bin blade portion for allowing the working fluid in the torus to flow out of the torus in a low speed ratio region.
- the working fluid is filled inside the impeller and the turbine. Power from the engine is input to the impeller, transmitted to the turbine via the working fluid, and output to a transmission-side member connected to the turbine. At this time, the A part of the flow of the working fluid is obstructed by the baffle plate, and the input capacity coefficient in a low speed ratio range is reduced. Further, a hole is formed in the turbine blade portion, and the working fluid flows out of the torus through the hole. For this reason, the input capacity coefficient in the low speed ratio range further decreases.
- the hole is formed at a position where the working fluid is more likely to flow out of the torus in the low speed ratio region than in the high speed ratio region. Therefore, a decrease in the input capacity coefficient outside the low speed ratio range is suppressed.
- the baffle plate is disposed on the inner peripheral portion of the turbine blade portion so as to protrude to the outer peripheral side, and the hole is formed in a direction in which the working fluid flows in the turbine blade portion. It is provided on the upstream side of the baffle and near the baffle.
- the working fluid circulates along the outer periphery of the torus. Therefore, the flow of a part of the working fluid is hindered by the baffle provided on the inner peripheral portion of the turbine blade portion. Then, a part of the working fluid disturbed by the baffle plate flows out of the torus through the hole.
- the flow of the working fluid in the torus is shifted to the direction in which the central rotational axial force is also moved to the outer peripheral side due to centrifugal force.
- the flow of the working fluid is weaker than the flow in the low speed ratio region. For this reason, the flow of the working fluid is hindered by the baffle plate, and it is difficult to flow out of the truss through the hole.
- the input capacity coefficient is sufficiently reduced in the low speed ratio range, and the input capacity coefficient is suppressed in the high speed ratio range.
- the turbine blade portion has an annular turbine shell and a plurality of turbine blades fixed on the turbine shell, and the baffle plate is provided on the inner peripheral side of the turbine shell with an impeller. Is provided along the inner peripheral portion of the turbine shell on the side surface facing the.
- the fluid coupling further includes a turbine knob fixed to an inner peripheral end of the turbine shell for transmitting torque to the transmission, and an inner peripheral end of the baffle plate is provided with a turbine. Fixed to the knob.
- the impeller has an annular impeller shell and a plurality of impeller blades fixed on the impeller shell, is mounted on a component on the engine side, and has a transmission on an outer peripheral portion.
- a front cover having an outer peripheral projection that bends and projects to the side, the outer peripheral part of the impeller shell is fixed to the outer peripheral projection of the front cover, and a fluid chamber is formed by the impeller shell and the front cover.
- the holes formed in the turbine blade portion allow the working fluid in the torus to flow between the turbine and the front cover.
- the fluid coupling according to one embodiment of the present invention further includes a lock-up clutch disposed between the turbine and the front cover for mechanically connecting the front cover and the turbine.
- FIG. 1 is a cross-sectional view of a fluid coupling according to one embodiment of the present invention.
- FIG. 2 is a view showing characteristics of a fluid coupling.
- FIG. 1 shows a sectional view of a fluid coupling 1 as one embodiment of the present invention.
- the fluid coupling 1 transmits the torque of the engine to the transmission, not shown to the left of FIG. 1, and not to the right of FIG. O—O in FIG. 1 is the rotation axis of the fluid coupling 1.
- the fluid coupling 1 mainly includes a front cover 2, an impeller 3, a turbine 4, and a lock-up clutch 6.
- the front cover 2 can be attached to a component such as an engine-side crankshaft (not shown), and receives torque input from the engine.
- the outer peripheral portion of the front cover 2 is provided with an outer peripheral side protruding portion 11 which bends and protrudes to the opposite side (the transmission side) of the engine (not shown).
- the impeller 3 includes an annular impeller shell 16 and a plurality of impeller blades 17 fixed on the impeller shell 16.
- the impeller shell 16 is fixed to the outer peripheral side protruding portion 11 of the front cover 2.
- the impeller shell 16 and the front cover 2 form a fluid chamber filled with a working fluid therein.
- the inner peripheral end of the impeller shell 16 is fixed to the impeller hub 18.
- the impeller hub 18 is mainly composed of a main body 18c, which is a disk-shaped member. Section, respectively.
- the inner peripheral surface of the outer cylindrical portion 18a contacts the outer peripheral surface of the ball bearing 8.
- the turbine 4 is arranged at a position facing the impeller 3 inside the fluid chamber, and forms a torus with the impeller 3.
- the turbine 4 includes an annular turbine shell 21 and a plurality of turbine blades 22 fixed on the turbine shell 21.
- the inner peripheral end of the turbine shell 21 is fixed to a turbine knob 23 for transmitting torque to a transmission (not shown).
- the turbine knob 23 is provided with a turbine knob boss 24 radially opposed to the outer tubular portion 18a of the impeller hub 18 so as to protrude toward the transmission.
- a shoulder 25 facing the transmission in the axial direction is formed on the transmission-side surface of the turbine hub 23 near the boundary with the turbine hub boss 24.
- the shoulder 25 comes into contact with the side of the ball bearing 8 on the engine side.
- the turbine hub 23 has a spline groove 26 on the inner peripheral side that engages with the turbine shaft 7 that transmits torque to the transmission.
- the turbine shaft 7 is It is arranged so as not to fit with the front cover 2.
- the ball bearings 8 are arranged in a radial gap between the outer cylindrical portion 18a of the impeller hub 18 and the turbine hub boss 24 of the turbine hub 23 so as to abut against each.
- the ball bearing 8 includes an outer race 31 on the outer circumference side, an inner race 32 on the inner circumference side, and a plurality of balls 33 as rolling elements.
- Chamfers are formed at the corners formed by the outer peripheral surface and the side surface of the outer race 31 and at the corner formed by the inner peripheral surface and the side surface of the inner race 32.
- a baffle plate 35 which is an annular plate member, is disposed on a side surface facing the impeller 3.
- the baffle plate 35 is provided along the inner peripheral portion of the turbine shell 21, and only the outer peripheral end portion 35 a is separated from the turbine shell 21 and projects into the torus. This baffle plate 35 blocks a part of the flow of the working fluid at the turbine outlet.
- the inner peripheral end of the baffle plate 35 is fixed to the turbine hub 23 together with the turbine shell 21!
- the turbine shell 21 has a hole 21a for allowing the working fluid in the torus to flow out of the torus.
- the hole 21a is provided in the turbine 4 on the upstream side of the baffle plate 35 in the direction in which the working fluid flows and close to the baffle plate 35.
- the lock-up clutch 6 is a device for mechanically connecting the front cover 2 and the turbine 4. Lock-up clutch 6 is arranged in a space between front cover 2 and turbine 4.
- the lock-up clutch 6 mainly includes a piston 41, a damper mechanism 42, and a force.
- the piston 41 is a disk-shaped member that can move in the axial direction and the circumferential direction, and is arranged in a space between the front force bar 2 and the turbine 4.
- the piston 41 has an inner cylindrical portion 43 that is bent toward the transmission and extends from the disc-shaped member body 41a to the inner peripheral portion, and an outer cylindrical portion that is also bent and extends similarly. 44 are provided on the outer peripheral side.
- the inner peripheral side cylindrical portion 43 is supported movably in the axial direction and the circumferential direction with respect to the outer peripheral surface of the turbine knob 23.
- a seal ring 45 is disposed on the outer peripheral surface of the turbine hub 23 on the engine side.
- the seal ring 45 seals an inner peripheral portion of a space between the front cover 2 and the turbine 4.
- the damper mechanism 42 includes a drive member 52 including a pair of plate members 56 and 57, a driven member 53, and a plurality of torsion springs 54.
- the pair of plate members 56 and 57 constituting the drive member 52 are arranged side by side in the axial direction.
- the pair of plate members 56 and 57 are fixed to each other by a plurality of rivets 55, and are further fixed to the piston 41.
- the piston 41 and the drive member 52 rotate integrally.
- the pair of plate members 56 and 57 are arranged such that the inner peripheral portions are spaced apart from each other in the axial direction.
- a plurality of cut-and-raised portions 56a and 57a are formed in the inner peripheral portion of each of the plate members 56 and 57 and arranged in the circumferential direction.
- the cut-and-raised portions 56a and 57a serve as support portions for supporting the torsion spring 54.
- the driven member 53 is a disk-shaped member, and is disposed in the inner peripheral portion of the pair of plate members 56 and 57 in the axial direction.
- the driven member 53 is engaged with the outer peripheral surface of the turbine hub 23 by a spline groove 53a formed in the inner peripheral portion.
- the driven member 53 has window holes 58 corresponding to the cut-and-raised portions 56a and 57a.
- the window hole 58 is a hole extending in the circumferential direction.
- the plurality of torsion springs 54 are coil springs extending in the circumferential direction and housed in the window holes 58 and the cut-and-raised portions 56a and 57a.
- the circumferential end of the torsion spring 54 is supported by the window hole 58 and the circumferential ends of the cut-and-raised portions 56a and 57a. Further, the torsion spring 54 is restricted from moving in the axial direction by the cut-and-raised portions 56a and 57a.
- a friction facing 61 is provided on the outer peripheral portion of the piston body 41a on the engine side.
- a friction surface 62 is formed at a portion of the front cover 2 facing the friction facing 61.
- the friction facing 61 is a member for sufficiently engaging the piston 41 and the front cover 2 by friction.
- the torque of the engine is transmitted from the front cover 2 to the piston 41 by the friction fusing 61 and the friction surface 62 abutting and frictionally engaging with each other. Further, this torque is transmitted to the transmission via the damper mechanism 42, the turbine hub 23, and the turbine shaft 7.
- Characteristic C shows the characteristics of a conventional fluid coupling, in which only a baffle plate is provided and a hole is provided.
- the position shapes of the baffle plate and the holes are not limited to those of the above-described embodiment, and the position shape is such that the drop of the input capacity coefficient in the low speed ratio region is larger than that in the high speed ratio region. Then.
- the input capacitance coefficient can be sufficiently reduced in the low speed ratio range.
- the input capacity coefficient can be sufficiently reduced in the low speed ratio range, and the reduction of the input capacity coefficient in the speed ratio range other than the low speed ratio range should be suppressed.
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- Engineering & Computer Science (AREA)
- General Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- Control Of Fluid Gearings (AREA)
- Mechanical Operated Clutches (AREA)
Abstract
Description
Claims
Applications Claiming Priority (2)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
JP2003430204A JP2005188617A (ja) | 2003-12-25 | 2003-12-25 | 流体継手 |
JP2003-430204 | 2003-12-25 |
Publications (1)
Publication Number | Publication Date |
---|---|
WO2005064185A1 true WO2005064185A1 (ja) | 2005-07-14 |
Family
ID=34736330
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
PCT/JP2004/017143 WO2005064185A1 (ja) | 2003-12-25 | 2004-11-18 | 流体継手 |
Country Status (2)
Country | Link |
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JP (1) | JP2005188617A (ja) |
WO (1) | WO2005064185A1 (ja) |
Families Citing this family (2)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
JP5189942B2 (ja) * | 2008-09-29 | 2013-04-24 | アイシン・エィ・ダブリュ工業株式会社 | 邪魔板を備えた流体継手 |
CN102927237A (zh) * | 2012-10-31 | 2013-02-13 | 陕西航天动力高科技股份有限公司 | 一种液力变矩器 |
Citations (6)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
JPS389163B1 (ja) * | 1959-09-22 | 1963-06-14 | ||
JPS402016B1 (ja) * | 1961-10-18 | 1965-02-03 | ||
JPS4850163A (ja) * | 1971-10-22 | 1973-07-14 | Gen Motors Corp | |
JPS5381793U (ja) * | 1976-12-08 | 1978-07-06 | ||
JPS56131034U (ja) * | 1980-03-07 | 1981-10-05 | ||
JP2003206958A (ja) * | 2002-01-15 | 2003-07-25 | Yutaka Giken Co Ltd | バッフルプレート付き流体継手 |
-
2003
- 2003-12-25 JP JP2003430204A patent/JP2005188617A/ja active Pending
-
2004
- 2004-11-18 WO PCT/JP2004/017143 patent/WO2005064185A1/ja active Application Filing
Patent Citations (6)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
JPS389163B1 (ja) * | 1959-09-22 | 1963-06-14 | ||
JPS402016B1 (ja) * | 1961-10-18 | 1965-02-03 | ||
JPS4850163A (ja) * | 1971-10-22 | 1973-07-14 | Gen Motors Corp | |
JPS5381793U (ja) * | 1976-12-08 | 1978-07-06 | ||
JPS56131034U (ja) * | 1980-03-07 | 1981-10-05 | ||
JP2003206958A (ja) * | 2002-01-15 | 2003-07-25 | Yutaka Giken Co Ltd | バッフルプレート付き流体継手 |
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Publication number | Publication date |
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JP2005188617A (ja) | 2005-07-14 |
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