WO2002036979A1 - Selecteur de tambour et ensemble de transmission associe - Google Patents

Selecteur de tambour et ensemble de transmission associe Download PDF

Info

Publication number
WO2002036979A1
WO2002036979A1 PCT/AU2001/001415 AU0101415W WO0236979A1 WO 2002036979 A1 WO2002036979 A1 WO 2002036979A1 AU 0101415 W AU0101415 W AU 0101415W WO 0236979 A1 WO0236979 A1 WO 0236979A1
Authority
WO
WIPO (PCT)
Prior art keywords
pad
gear
drum surface
drive means
influence
Prior art date
Application number
PCT/AU2001/001415
Other languages
English (en)
Inventor
Boris Klaricic
Original Assignee
Select Design Technologies Limited
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 Select Design Technologies Limited filed Critical Select Design Technologies Limited
Priority to EP01981965A priority Critical patent/EP1346163A4/fr
Priority to AU1366602A priority patent/AU1366602A/xx
Priority to AU2002213666A priority patent/AU2002213666B2/en
Publication of WO2002036979A1 publication Critical patent/WO2002036979A1/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
    • 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
    • F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
    • F16D27/00—Magnetically- or electrically- actuated clutches; Control or electric circuits therefor
    • F16D27/10—Magnetically- or electrically- actuated clutches; Control or electric circuits therefor with an electromagnet not rotating with a clutching member, i.e. without collecting rings
    • F16D27/108—Magnetically- or electrically- actuated clutches; Control or electric circuits therefor with an electromagnet not rotating with a clutching member, i.e. without collecting rings with axially movable clutching members
    • F16D27/11—Magnetically- or electrically- actuated clutches; Control or electric circuits therefor with an electromagnet not rotating with a clutching member, i.e. without collecting rings with axially movable clutching members with conical friction surfaces, e.g. cone clutches
    • 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
    • F16D13/24—Friction clutches with axially-movable clutching members with conical friction surfaces cone clutches
    • F16D13/32—Friction clutches with axially-movable clutching members with conical friction surfaces cone clutches in which two or more axially-movable members 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
    • F16D21/00—Systems comprising a plurality of actuated clutches
    • F16D21/02—Systems comprising a plurality of actuated clutches for interconnecting three or more shafts or other transmission members in different ways
    • F16D21/04—Systems comprising a plurality of actuated clutches for interconnecting three or more shafts or other transmission members in different ways with a shaft carrying a number of rotatable transmission members, e.g. gears, each of which can be connected to the shaft by a clutching member or members between the shaft and the hub of the transmission 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
    • 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
    • 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
    • F16H3/089—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 all of the meshing gears being supported by a pair of parallel shafts, one being the input shaft and the other the output shaft, there being no countershaft involved

Definitions

  • THIS INVENTION relates to a drum selector and associated transmission assembly and in particular but not limited to a compact assembly employing two shafts.
  • the invention resides in a gear selector employing circumferentially spaced pads, each pad having a circumferentially extending pad surface, drive means driving the pads into driving engagement with a drum surface of a normally free rotating gear assembly, the gear assembly having a gear, the gear being engageable when said pad surfaces engage said drum surface under the influence of said drive means, the pads being pivotal to a drum surface unengaged position about a first pivot axis and being pivotal to a drum surface engaged position about a second pivot axis spaced from the first pivot axis.
  • the invention resides in a transmission assembly having an input, an output and gears constantly in mesh for selectively coupling the input to the output in predetermined ratio of input to output according to gear selection, at least one of said gears being a free rotating gear assembly, the free rotating gear assembly having a drum surface for engagement of said at least one gear and a gear selector, the gear selector comprising circumferentially spaced pads, each pad having a circumferentially extending pad surface, drive means driving the pads into driving engagement with said drum surface, the at least one gear of said gear assembly being engageable when said pad surfaces engage said drum surface under the influence of said drive means, the pads being pivotal to a drum surface unengaged position about a first pivot axis and being pivotal to a drum surface engaged position about a second pivot axis spaced from the first pivot axis.
  • the free rotating gear assembly includes a gear in permanent mesh with a fixed gear.
  • each pad is supported by a pad carrier having a centre of gravity spaced from the pivot axes in order to urge said pad to a drum surface unengaged position under the influence of centrifugal forces.
  • the pad carrier has a first end nearer the centre of gravity and a second end opposite said first end and there being biassing means biassing said second end against said drive means and holding said pads in a drum surface unengaged position until overcome by said drive means.
  • the drive means is preferably an annular hydraulic cylinder assembly having an axially moveable input piston, a radially moveable output piston and an intermediate hydraulic coupling between the pistons.
  • the output piston is circumferentially movable under the influence of said biassing means.
  • Figure 1 is a general view of five speed two-shaft arrangement of a transmission
  • Figure 2 is a section through B-B of Figure 1 ;
  • Figure 3 is an enlarged end view of a twin-cone clutch as shown in Figure
  • Figure 4 is a sectional view A-A of Figure 3 showing arrangement of a twin- cone clutch, hydraulic spring and hydraulic actuatorforfirst gear as shown in Figure
  • Figure 5 is an enlarged end view showing arrangement of hydraulic spring and electric solenoid actuator for drum and twin-cone gear selectors as per Figure
  • Figure 6 is a sectional view C-C of Figure 5 showing arrangement of hydraulic spring and electric actuator for operation of cone clutch
  • Figure 7 is an enlarged end view of drum type clutches used with second, third, fourth and fifth gears as per Figure 1 .
  • Figure 8 is a sectional view D-D of Figure 7 showing hydraulic spring and hydraulic actuator arrangement to operate drum clutches as per Figure 1 .
  • Figure 9 is an enlarged partial view of Figure 7 showing detailed geometry for driving elements and hydraulic spring. METHOD OF PERFORMANCE
  • transmission apparatus 10 comprising shafts, free and fixed gears operatively associated for input and output according to gear selection to be described.
  • the transmission is of the type involving free rotating gears and accompanying gear selector assemblies, each free rotating gear being in constant mesh with a fixed gear.
  • the gears required for selection of first through fifth and reverse are marked as 1 through 5 and R on each fixed gear of the combination of constant mesh free rotating and fixed gear pairs in Figure 1 .
  • Shafts 1 1 and 1 1A are supported on bearings 12A, 13 and 13B; shafts 14 and 14A are supported on bearings 12, 13A and 13C.
  • Shafts 1 1 and 1 1A, 14 and 14A are firmly connected at their respective junctures by splines.
  • First gear (1 ) and reverse gear (R) are fixed to input shafts 1 1 A and 1 1 respectively. All free gears 1 A through RA rotate on plain bearings and are attached to twin cone or drum selectors as per transmission general arrangement as shown in Figure 1.
  • a typical twin cone selector layout is shown in section at 15 and its details are shown in Figures 3 and 4.
  • a typical drum selector is shown in section at 16 and its details are shown in Figures 7, 8 and 9.
  • Figure 2 has been generated to show arrangement of annular hydraulic cylinders 1 7 and 18 and gear casing flange mountings 19 holding the hydraulic cylinders. Fluid pressure to hydraulic cylinders is supplied via inlet port 20 and bleeding of trapped air via port 21 . Corresponding ports are provided for hydraulic cylinder 18. Cylinder 17 selects gear 1 while cylinder 18 selects gear 3. Each gear pair has its own annular hydraulic cylinder.
  • FIGs 3 and 4 show detailed enlarged views of a typical twin cone selector as may be used as gear 1 selector.
  • the selector illustrated has general application to the selector to any gear.
  • the twin-cone selector increases transmission of power and torque three times to that produced by a single cone. This is achieved by the increased number of friction surfaces from one pair to three pairs. Referring to the top part of Figure 4, friction surfaces are numbered 19A, 20A and 21 A and these are shown in free or unengaged state while the bottom part of Figure 4 shows the corresponding friction surfaces as numerals 19, 20 and 21 as engaged.
  • Input shaft 1 1A is connected to a power source and carries first gear 1 firmly fixed to it and in permanent mesh with free rotating gear (1A in Figure 1 embodiment), which is in this case also a female part 22 of a cone selector as shown in Figure 4.
  • a hydraulic actuator 23 having hydraulic components as piston, seal, spring and pressure washer is received by internal gear case wall 24 formed so as to prevent any radial or axial movement of the actuator 23.
  • the circular part or crown of the hydraulic cylinder piston is formed so as to fit and act as an annular iniet piston 25 engageable with a hydraulic coupling 26, in this case the hydraulic coupling is formed as hydraulic springs or bags illustrated at 27.
  • the crown of hydraulic coupling 26 forms an outlet piston at 28 formed so as to clip in a housing of respective thrust bearings 29.
  • the function of thrust bearing 29 is to provide relative rotational movements between cone clutch male part 30 and a piston 28 of a hydraulic coupling 26 whether in idling or power transmitting mode.
  • Twin cone selector comprises male part 30, female part 22 and cones 31 and 32. Cone 31 operates as a driving cone and is constrained but free to slide parallel to the axis of rotation in circular slots 31 A formed in male part 30.
  • Cone 32 operates as a driven cone and is constrained but free to slide parallel to the axis of rotation in circular slots 33 formed in driven female part 22 of the selector assembly.
  • the movements of cones 31 and 32 are controlled by stops 34 and 35 and compression springs 36 and 37. Hydraulic fluid pressure when supplied to hydraulic cylinder 23 of Figure
  • Figures 5 and 6 show an alternative embodiment, like numerals illustrate like features, involving actuation of twin cone selectors by electric solenoids 41 and 42 in combination with a hydraulic spring coupling 43.
  • solenoids When solenoids are energized a circular plunger 44 activated by magnetomotive force presses hydraulic spring 43 and its piston against male cone 30 thus achieving engagement of the cone selector essentially as previously described.
  • the female cone 22 is shown in part and the multiple male cones 31 and 32 have been omitted.
  • Figures 5 and 6 merely illustrate an alternative drive.
  • twin cone selectors are applicable to first and reverse gears as shown in Figure 1.
  • Other gears in this general arrangement transmission are operated by drum selectors actuated by an hydraulic cylinder assembly and hydraulic spring of different shape but in principle functioning as described above.
  • a typical drum selector 9 has a friction area contact between driving pads 45 and drum 46.
  • a hydraulic spring body 47 is employed as a coupling between input and output pistons 48 and 49.
  • the hydraulic spring increases the pressure by several times on the driving pads 45 and consequently higher power and torque can be transmitted with reduced hydraulic pump pressures. In this sense the hydraulic coupling functions as a force multiplier or amplifier.
  • the hydraulic spring comprises body 47, output piston 49, input piston 48 and spring sack 50.
  • the sack 50 is made of elastic material compatible with transmission and hydraulic fluids. It is filled with fluid or gel of hydraulic properties and fully sealed making it leak-proof.
  • the spring sack 50 is shaped to fit exactly a cavity as defined by piston 49 and 48 and spring body 47.
  • This provides constant pressure on pads 45 from output piston 49 when spring sack 50 is pressed by piston 48 and converts axial movement to radial movement.
  • the force produced by output piston 49 is a function of its cross section and cross sectional area of input piston 48 as well as force from push ring 51 provided by annular hydraulic cylinder 52.
  • the drum type gear selector 9 employing the earlier described driving pad geometry, which allows a pad to be in full contact with the drum and the inclusion of the hydraulic spring coupling makes the assembly a simple and effective solution for power shift of gears.
  • the full contact is accomplished by elongated pivot 53 hole by "H1 " amount in horizontal direction and "V1 " in the vertical direction.
  • the driving pad 45 itself is also improved in strength by making it stronger in areas where required.
  • Each pad has its centre of gravity "Cg" on the left side of pivot point 53 so that the pad's centrifugal force "Cf” is acting in direction as shown in Figure 9 thus keeping the pad out of contact with the drum when it rotates in neutral.
  • a spring 54 has one end hooked into a slot 55 of pad 45 and its other end is anchored at point 56, and also is resting on the hydraulic spring at Point S2.
  • the spring arrangement and its shape allow spring 54 to act in two major directions required for proper operation of pad 45.
  • One action is to pull pad 45 about its pivot point 53 to a neutral position 45A by rotating pad 45 about pivot 53 for distance "H1 , V1 " moving Point P1 into Point P2.
  • the hydraulic spring 47 is rotated about its pivot Point S1 to position 47A against spring 54.
  • centrifugal force "Cf” is a major force, which keeps the pads in a neutral position when gears are in free operating mode.
  • the result in the differential pivot P1 , P2 is to improve surface contact between the pad 45 and the drum 46.

Landscapes

  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Physics & Mathematics (AREA)
  • Electromagnetism (AREA)
  • Gear-Shifting Mechanisms (AREA)
  • Structure Of Transmissions (AREA)
  • Mechanical Operated Clutches (AREA)

Abstract

L'invention concerne une transmission faisant appel à un sélecteur de vitesse de type tambour possédant des patins périphériques (45) mettant en oeuvre la géométrie d'entraînement du patin, qui permet qu'un patin soit complètement en contact avec le tambour. Chaque patin possède son centre de gravité 'Cg' sur le côté gauche du point pivotement (53) de manière que la force centrifuge du patin 'Cf' empêche le patin d'entrer en contact avec le tambour lorsque ce dernier tourne en position neutre. Un ressort (54) possède une extrémité accrochée dans une fente (55) du patin (45) et son autre extrémité ancrée au niveau du point (56), et également posée sur le ressort hydraulique au niveau du point (S2). La disposition du ressort (54) ainsi que sa forme permettent à ce dernier d'agir dans deux directions principales requises pour le fonctionnement correct du patin (45). Une action consiste à tirer le patin (45) sur son point de pivotement (54) vers une position neutre (45A) par rotation du patin (45) sur le pivot (53) pour une distance 'H1' déplaçant le point (P1) au point (P2). Simultanément, lorsque le patin est tiré en position (45A), le ressort hydraulique (49) est tourné autour de son point de pivotement (S1) en position (47A). Ces deux mouvements placent le patin (45) dans sa position de repos avec des espaces de dégagement 'G1' et 'G2' au niveau de l'arrière et de l'avant du patin respectivement. Il faut noter que la force centrifuge 'Cf' est une force importante, qui maintient les patins dans une position neutre lorsque les vitesses se trouvent dans un mode de fonctionnement libre.
PCT/AU2001/001415 2000-11-03 2001-11-02 Selecteur de tambour et ensemble de transmission associe WO2002036979A1 (fr)

Priority Applications (3)

Application Number Priority Date Filing Date Title
EP01981965A EP1346163A4 (fr) 2000-11-03 2001-11-02 Selecteur de tambour et ensemble de transmission associe
AU1366602A AU1366602A (en) 2000-11-03 2001-11-02 Drum selector and associated transmission assembly
AU2002213666A AU2002213666B2 (en) 2000-11-03 2001-11-02 Drum selector and associated transmission assembly

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
AUPR1231 2000-11-03
AUPR1231A AUPR123100A0 (en) 2000-11-03 2000-11-03 Drum clutch and associated transmission assembly

Publications (1)

Publication Number Publication Date
WO2002036979A1 true WO2002036979A1 (fr) 2002-05-10

Family

ID=3825274

Family Applications (1)

Application Number Title Priority Date Filing Date
PCT/AU2001/001415 WO2002036979A1 (fr) 2000-11-03 2001-11-02 Selecteur de tambour et ensemble de transmission associe

Country Status (4)

Country Link
EP (1) EP1346163A4 (fr)
AR (1) AR031207A1 (fr)
AU (2) AUPR123100A0 (fr)
WO (1) WO2002036979A1 (fr)

Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2000008357A1 (fr) * 1998-08-04 2000-02-17 Preload International Limited Technique et dispositif permettant de commander l'engrenement et le desengrenement de roues d'engrenage
US6092432A (en) 1996-10-09 2000-07-25 Klaricic; Boris Countershaft transmission with constant mesh reverse gearing
WO2000071909A1 (fr) 1999-05-24 2000-11-30 Select Design Technologies Limited Une transmission

Family Cites Families (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE1239145B (de) * 1959-05-29 1967-04-20 Karl Obermoser Dr Ing Reibungskupplung oder -bremse
US3338350A (en) * 1965-04-28 1967-08-29 Horton Mfg Co Inc Frictional torque transmitting device
DE2123749A1 (de) * 1971-05-13 1972-11-23 Robert Bosch Gmbh, 7000 Stuttgart Kupplungseinrichtung zur Kraftübertragung zwischen einem Antrieb und einer Pumpe
DE3414406A1 (de) * 1984-04-17 1985-10-24 Fa. Andreas Stihl, 7050 Waiblingen In einer kupplungstrommel angeordneter rotor fuer eine fliehkraftkupplung
US5503261A (en) * 1994-07-15 1996-04-02 Automotive Concepts Technology Bi-directional centrifugal clutch

Patent Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US6092432A (en) 1996-10-09 2000-07-25 Klaricic; Boris Countershaft transmission with constant mesh reverse gearing
WO2000008357A1 (fr) * 1998-08-04 2000-02-17 Preload International Limited Technique et dispositif permettant de commander l'engrenement et le desengrenement de roues d'engrenage
WO2000071909A1 (fr) 1999-05-24 2000-11-30 Select Design Technologies Limited Une transmission

Non-Patent Citations (1)

* Cited by examiner, † Cited by third party
Title
See also references of EP1346163A4

Also Published As

Publication number Publication date
AR031207A1 (es) 2003-09-10
EP1346163A4 (fr) 2006-01-25
EP1346163A1 (fr) 2003-09-24
AU1366602A (en) 2002-05-15
AUPR123100A0 (en) 2000-11-30

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