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WO1987006662A1 - Dispositifs a friction - Google Patents

Dispositifs a friction Download PDF

Info

Publication number
WO1987006662A1
WO1987006662A1 PCT/GB1987/000276 GB8700276W WO8706662A1 WO 1987006662 A1 WO1987006662 A1 WO 1987006662A1 GB 8700276 W GB8700276 W GB 8700276W WO 8706662 A1 WO8706662 A1 WO 8706662A1
Authority
WO
WIPO (PCT)
Prior art keywords
clutch
elements
gear train
layshaft
friction elements
Prior art date
Application number
PCT/GB1987/000276
Other languages
English (en)
Inventor
Claude Peter Windsor-Smith
Raymond Alfred Tailby
Original Assignee
Windsor Smith Claude P
Tailby Raymond A
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 Windsor Smith Claude P, Tailby Raymond A filed Critical Windsor Smith Claude P
Publication of WO1987006662A1 publication Critical patent/WO1987006662A1/fr

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
    • F16H3/00—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion
    • F16H3/02—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion without gears having orbital motion
    • F16H3/08—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion without gears having orbital motion exclusively or essentially with continuously meshing gears, that can be disengaged from their shafts
    • F16H3/087—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion without gears having orbital motion exclusively or essentially with continuously meshing gears, that can be disengaged from their shafts characterised by the disposition of the gears
    • F16H3/091—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion without gears having orbital motion exclusively or essentially with continuously meshing gears, that can be disengaged from their shafts characterised by the disposition of the gears including a single countershaft
    • 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
    • F16D13/00—Friction clutches
    • F16D13/22—Friction clutches with axially-movable clutching members
    • F16D13/38—Friction clutches with axially-movable clutching members with flat clutching surfaces, e.g. discs
    • F16D13/52—Clutches with multiple lamellae ; Clutches in which three or more axially moveable members are fixed alternately to the shafts to be coupled and are pressed from one side towards an axially-located member
    • 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
    • F16D13/00—Friction clutches
    • F16D13/58—Details
    • F16D13/60—Clutching elements
    • F16D13/64—Clutch-plates; Clutch-lamellae
    • F16D13/648—Clutch-plates; Clutch-lamellae for clutches with multiple lamellae
    • 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
    • F16D25/00—Fluid-actuated clutches
    • F16D25/08—Fluid-actuated clutches with fluid-actuated member not rotating with a clutching member
    • F16D25/082—Fluid-actuated clutches with fluid-actuated member not rotating with a clutching member the line of action of the fluid-actuated members co-inciding with the axis of rotation
    • 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
    • F16H2200/00—Transmissions for multiple ratios
    • F16H2200/003—Transmissions for multiple ratios characterised by the number of forward speeds
    • F16H2200/0047—Transmissions for multiple ratios characterised by the number of forward speeds the gear ratios comprising five forward speeds

Definitions

  • This invention relates to friction devices.
  • An example of the application of the invention is to mult i- inter leaved plate-type clutch mechanisms for multi-layshaft (two or more layshafts) constant mesh change speed gear trains. Certain aspects of the matter disclosed herein may be applicable to friction mechanisms for use in other applications including both clutch and brake mechanisms.
  • the friction device may be a multi-plate interleaved clutch assembly.
  • the clutch assembly may comprise an assembly of interleaved plates, one set having drive means at its outer periphery and the other set having drive means at its inner periphery.
  • the plates or clutch elements are provided with means for frictio al engagement.
  • Such means may comprise the provision of friction means to transmit drive by frictional engagement between successive clutch elements.
  • such friction means has been provided in the form of a friction facing on one of the sets of clutch elements.
  • the floating clutch element may comprise a metallic clutch plate or element faced with friction material, the clutch elements of the two drivably connected sets being plain metal plates.
  • the floating clutch element may be a plain metal plate and the driven clutch elements may be friction -surfaced.
  • the main difference between the floating clutch element and the other clutch elements between which it is sandwiched is that it lacks drive elements and transmits drive between its neighbours by frictional engagement therewith.
  • a clutch assembly incorporating the floating friction element is the take-off-from-rest clutch of a six ratio gear train and the assembly has particularly smooth operating characteristics.
  • a multi-plate clutch assembly for a multi-layshaft gear train wherein a clutch- actuating piston and cylinder assembly is arranged to transmit clutch actuating thrust to the clutch elements through rotary bearing means.
  • the rotary bearing means comprises a race of rotary elements such as balls or rollers.
  • the race may be mounted directly on the piston.
  • the piston may be slidable within a cylinder formed in the housing of the gear train.
  • the cylinder may be a bore formed in an end wall of the gear train housing.
  • the cylinder may be formed in a cylinder member supported by the gear train housing intermediate the ends thereof. The latter arrangement is appropriate where the clutch means is itself located otherwise than at the end of the housing.
  • the invention also provides a drive transmission comprising a gear train as defined above.
  • the gear train may be provided in combination with drive output means to a front wheel drive automobile transmission.
  • the ⁇ ear train may be connected to automatic control means effecting clutch control and ratio changing in accordance with sensed vehicle motion variables.
  • Clutch engagement may be provided by means of fluid pressure control apparatus providing for progressive clutch engagement, particularly for take-off from rest, whereby an automatic vehicle tranmission can be provided without the need for a torque converter or fluid coupling.
  • the invention also provides a friction device and a gear train incorporating same having any novel feature or any novel combination of features disclosed herein.
  • Fig 1 shows a section through a gear train
  • Fig 2 shows, somewhat diagrammatic ally , a modification of the gear train of Fig 1
  • Fig 3 is a diagram of the gear train of Fig 1.
  • a gear train 10 comprises a first layshaft 12, an input or main shaft 14 and a second layshaft 16 , all mounted within a gear train housing 18.
  • Gears 20 and 22 on layshaft 12 are in ddlrect constant mesh with main shaft gears 24, 26 respectively.
  • gears 26 and 28 on layshaft 16 are in direct constant mesh with main shaft gears 24 and 26 also.
  • a main shaft gear 30 is in direct constant mesh with a gear 32 on layshaft 16.
  • Layshaft 12 carries an output gear 34. The latter directly drives a differential mechanism 36 from which propel lor shafts 38 transmit drive in opposite directions to the front wheels of an aut omobi le . '
  • Drive input to main shaft 14 is through a torsionally damped mechanical input coupling 40.
  • Drive is transmitted at all times via the housing 42 of a clutch 44 to main shaft input gear 30 and hence to layshaft input gear 32, and hence at all times to layshaft 16 ⁇ tself .
  • Input clutch 44 provides for direct transmission of drive to the main shaft output gears 24, 26.
  • Clutch assemblies 46 , 48 on layshaft 16 provide for selective transmission of drive from the layshaft.16 to its output gears 26 and 28 - respectively.
  • drive input from coupling 40 can be transmitted direct on engagement of clutch 44 , or at two higher torque ratios on selective engagement of clutches 46 and 48.
  • input shaft 14 and layshaft 16 provide effectively three transmission ratios between the input coupling and the input shaft gears 24 and.26.
  • torque can be transmitted at two selectable additional ratios to final output gear 34 by selective operation of layshaft clutches 50 and 52, whereby the gear train 10 provides six torque paths in all.
  • Input gear 22 of layshaft 12 is directly coupled to the housing 54 of clutch 50, of which the clutch inner member 56 is directly coupled to layshaft 12.
  • layshaft input gear 20 is directly coupled to the inner member 58 of clutch the 52, and latter* s housing 60 is directly mounted on the layshaft 12.
  • Input shaft 14 is jour ailed on ball races 62 and 64 which are closely spaced and provide excellent support for the main shaft output gears 24 and 26.
  • layshaft 16 is journalled on ball races 66 and 68 which provide similar support for that shaft.
  • Output shaft 12 is journalled on roller races 70 and 72.
  • Gear train 10 is extremely compact and provides a six torque path automatic transmission with direct mechanical drive input and the attendant fuel efficiency characteristics.
  • Clutch 48 is employed for drive take-up from rest. It comprises an interleaved assembly of annular clutch elements. These elements comprise a first set of clutch elements 74 keyed at their inner peripheries to the clutch inner member 76 which is directly mounted on layshaft 16. A second set of clutch elements 78 are keyed at their outer peripheries to the clutch housing 18 which is directly drivably coupled to the layshaft output gear 28.
  • the floating clutch elements 82 Sandwiched between the clutch elements 74 and 78 are a series of floating clutch elements 82. These latter are not dr ivably coupled to the inner or outer clutch members 76 and 80 but are located ax i a l ly . between these members and are free ly rotatable . They serve to frictionally engage the clutch elements 74 and 78 and to transmit drive therebetween .
  • the floating clutch elements 82 each comprise an annular steel plate having a friction surface on its opposite f aces . Their construction is similar to that of a conventional clutch element , but without the provision of torque -transmitting dr ive formations at either their inner or outer peripher ies .
  • the f loating clutch elements 82 are surprisingly found to reduce or eliminate vibration , judder and any stick/slip tendency of the clutch e lements " . 74 and 78 , whereby the drive take-up and gear change characteristics of the transmission are greatly improved .
  • Similar provision may be made in the other clutches of the gear train or any one cr more of them according to need .
  • Clutch 48 is actuated by a piston 84 slidable in a bore formed in the end wall of. housing 18 and acting through a ball race 86 on an annular pressure member 88, whereby compressive thrust is applied to the clutch elements for clutch engagement purposes.
  • piston 84 is non-rotatable and is directly supplied with fluid pressure, hydraulic or pneumatic through a suitable inlet coupling (not shown) formed in the housing 18. Similar provision is made for clutches 46, 50 and 52.
  • Fig 2 shows a modification of the gear train of Fig 1.
  • one of the six available transmission ratios is equal to one of the others due to the equal layshaft spacing, whereby only five different ratios are available. Therefore, in Fig 2, in order to achieve six different transmission ratios, the gear 24 on input shaft 14 is provided in the form of a two-gear cluster 24 A, 24B. Corresponding changes are provided on layshafts 12 and 16, the former having an input gear 20A meshing with gear 24A, and the latter having its gears 26 A, 28A meshing with the input shaft gears 24A, 24B respectively.
  • a clutch assembly which employs a needle roller race and is so compact that it can replace the synchronisation clutch assembly of a conventional single layshaft gear train , thereby permitting automatic or semi-automatic control of the gear train .
  • clutch-actuating pistons acting through ball or roller races or like bearing means provides the very considerable advantage that the considerable fluid loss which has in the past occurred between the rotating pistons and their cylinder assemblies is avoided , whereby a much smaller hydraulic pump can be employed , such as a remote pump feeding the gear box and a limited slip differential or the like .
  • the clutch elements themselves can be of any suitable form conventional or otherwise with any suitable driving arrangement , including of course the conventional axially slidable keys and key ways .
  • References above to frictional engagement of the friction elements and the floating elements are intended to include not only actual physical contact but also drive transmission in the presence of a film of oil on the confronting surfaces.

Landscapes

  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Structure Of Transmissions (AREA)
  • Hydraulic Clutches, Magnetic Clutches, Fluid Clutches, And Fluid Joints (AREA)

Abstract

Un embrayage à refroidissement liquide (48) pour un train d'engrenages de changement de vitesse à engrènement constant d'arbres intermédiaires multiples comprend de multiples éléments d'embrayage annulaires intercalés (74, 78) couplés axialement de manière coulissante par des crabots d'entraînement à leurs périphéries interne et externe d'une manière conventionnelle. Pris en sandwich entre les éléments d'embrayage se trouvent une série d'éléments flottants (82) qui ne sont pas couplés de manière entraînante à l'un ou l'autre des éléments d'embrayage interne ou externe mais qui sont situés axialement entre eux et tournent librement. Les éléments (82) sont d'une construction similaire à celle des éléments d'embrayage. Leur présence sert à éviter le problème bien connu du collage-patinage. L'actionnement des éléments d'embrayage s'effectue à l'aide de pistons non rotatifs (84) agissant par l'intermédiaire de chemins de roulement de billes (86) de sorte que les pistons n'ont pas besoin de tourner avec les éléments d'embrayage.
PCT/GB1987/000276 1986-04-25 1987-04-27 Dispositifs a friction WO1987006662A1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
GB868610184A GB8610184D0 (en) 1986-04-25 1986-04-25 Friction devices
GB8610184 1986-04-25

Publications (1)

Publication Number Publication Date
WO1987006662A1 true WO1987006662A1 (fr) 1987-11-05

Family

ID=10596853

Family Applications (1)

Application Number Title Priority Date Filing Date
PCT/GB1987/000276 WO1987006662A1 (fr) 1986-04-25 1987-04-27 Dispositifs a friction

Country Status (4)

Country Link
EP (1) EP0303612A1 (fr)
JP (1) JPH01503080A (fr)
GB (1) GB8610184D0 (fr)
WO (1) WO1987006662A1 (fr)

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP0896165A1 (fr) * 1997-08-05 1999-02-10 Messier Bugatti Dispositif de friction dans l'huile à disques coaxiaux
FR2774731A1 (fr) * 1997-12-19 1999-08-13 Antonov Automotive Europ Disque et dispositif d'accouplement par friction, et transmission automatique ainsi equipee

Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
FR370148A (fr) * 1906-10-02 1907-01-29 Angelin Joseph Marius Julien Perfectionnement aux embrayages à friction
US3613848A (en) * 1969-09-15 1971-10-19 Stearns Electric Corp Fluid actuated and lubricated clutch with splined release springs
FR2388165A1 (fr) * 1977-04-20 1978-11-17 Stromag Maschf Dispositif de commande actionne hydrauliquement
US4159654A (en) * 1977-08-24 1979-07-03 Honda Giken Kogyo Kabushiki Kaisha Automatic transmission apparatus
EP0012022A1 (fr) * 1978-12-05 1980-06-11 Claude Peter Windsor-Smith Engrenage à changement de vitesse

Patent Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
FR370148A (fr) * 1906-10-02 1907-01-29 Angelin Joseph Marius Julien Perfectionnement aux embrayages à friction
US3613848A (en) * 1969-09-15 1971-10-19 Stearns Electric Corp Fluid actuated and lubricated clutch with splined release springs
FR2388165A1 (fr) * 1977-04-20 1978-11-17 Stromag Maschf Dispositif de commande actionne hydrauliquement
US4159654A (en) * 1977-08-24 1979-07-03 Honda Giken Kogyo Kabushiki Kaisha Automatic transmission apparatus
EP0012022A1 (fr) * 1978-12-05 1980-06-11 Claude Peter Windsor-Smith Engrenage à changement de vitesse

Cited By (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP0896165A1 (fr) * 1997-08-05 1999-02-10 Messier Bugatti Dispositif de friction dans l'huile à disques coaxiaux
FR2767166A1 (fr) * 1997-08-05 1999-02-12 Messier Bugatti Dispositif de friction dans l'huile a disques coaxiaux
US6006885A (en) * 1997-08-05 1999-12-28 Messier-Bugatti Friction-in-oil device having coaxial disks
FR2774731A1 (fr) * 1997-12-19 1999-08-13 Antonov Automotive Europ Disque et dispositif d'accouplement par friction, et transmission automatique ainsi equipee

Also Published As

Publication number Publication date
EP0303612A1 (fr) 1989-02-22
GB8610184D0 (en) 1986-05-29
JPH01503080A (ja) 1989-10-19

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