WO1980002729A1 - Dispositif a roues de friction pour transmettre, avec un rapport de vitesse variable de maniere continue, un mouvement rotatif entre deux arbres coaxiaux - Google Patents

Dispositif a roues de friction pour transmettre, avec un rapport de vitesse variable de maniere continue, un mouvement rotatif entre deux arbres coaxiaux Download PDF

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Publication number
WO1980002729A1
WO1980002729A1 PCT/AT1980/000016 AT8000016W WO8002729A1 WO 1980002729 A1 WO1980002729 A1 WO 1980002729A1 AT 8000016 W AT8000016 W AT 8000016W WO 8002729 A1 WO8002729 A1 WO 8002729A1
Authority
WO
WIPO (PCT)
Prior art keywords
friction
friction ring
ring
driver
transmission
Prior art date
Application number
PCT/AT1980/000016
Other languages
German (de)
English (en)
Inventor
R Falkner
Original Assignee
R Falkner
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 R Falkner filed Critical R Falkner
Priority to AU5981481A priority Critical patent/AU5981481A/xx
Publication of WO1980002729A1 publication Critical patent/WO1980002729A1/fr
Priority to JP56501693A priority patent/JPS57500748A/ja
Priority to AT81901320T priority patent/ATE9387T1/de
Priority to PCT/AT1981/000011 priority patent/WO1981003367A1/fr
Priority to EP81901320A priority patent/EP0052625B1/fr
Priority to DE8181901320T priority patent/DE3165970D1/de
Priority to DD81230259A priority patent/DD159196A5/de

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
    • F16H15/00—Gearings for conveying rotary motion with variable gear ratio, or for reversing rotary motion, by friction between rotary members
    • F16H15/48—Gearings for conveying rotary motion with variable gear ratio, or for reversing rotary motion, by friction between rotary members with members having orbital motion
    • F16H15/50—Gearings providing a continuous range of gear ratios
    • F16H15/54—Gearings providing a continuous range of gear ratios in which two members co-operate by means of rings or by means of parts of endless flexible members pressed between the first-mentioned members
    • 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
    • F16H15/00—Gearings for conveying rotary motion with variable gear ratio, or for reversing rotary motion, by friction between rotary members
    • F16H15/48—Gearings for conveying rotary motion with variable gear ratio, or for reversing rotary motion, by friction between rotary members with members having orbital motion
    • F16H15/50—Gearings providing a continuous range of gear ratios

Definitions

  • Friction gear for the continuously variable transmission of a rotary movement between two coaxial shafts
  • the invention relates to a friction to the infinitely variable transmission of a rotary movement between a driving shaft and a coaxial 'n output shaft, with a housing-fixed concentric friction wheel having two spaced ih ⁇ rem axial distance variable Reibkränze each with a transfer surface, and with a in the transmission surface rolling friction ring, which is rotatably mounted on a rotating and radially displaceable driver with the drive shaft, and with an output member between the friction ring and the output shaft.
  • Such a transmission can be found, for example, in AT-PS 222.966. It has a very large area of application and can in particular also be used wherever, in addition to the requirement for a continuously variable reduction ratio which can be set precisely to infinity, there is only little space available for the installation of the transmission.
  • the known transmission has constructive weaknesses in the transmission of the rotary movement between the radially adjustable friction ring, which is therefore variable in its eccentricity, and the output shaft, which takes place by means of a hollow wobble shaft coupling as the output member. Only when the reduction ratio is infinite does the hollow wobble shaft coupling run concentrically with the output shaft, while in any other position it wobbles, which results in a double cardan joint connection with the friction ring and the output shaft.
  • the radial adjustment of the friction ring inevitably takes place towards the drive shaft by the approach of the two friction rings of the friction wheel fixed to the housing, away from the drive shaft by means of a spring which is prestressed between the drive shaft and the driver. It has been shown that in the transmission of particularly high torques, the spring inserted between the drive shaft and the driver cannot, in particular, exert the necessary contact pressure of the friction ring on the friction wheel if uneven loads occur.
  • the invention has now set itself the task of improving the known transmission in its output part and to eliminate a swash shaft coupling with all the disadvantages inherent in it. Furthermore, in a preferred embodiment, an inevitable radial displacement of the driver in both directions is also to be achieved.
  • this object is achieved in that a second friction wheel, which is concentrically arranged on the output shaft, is provided as the output member, with two friction rings which can be changed in axial distance from one another, each with a transmission surface, on which the friction ring rolls along a second conical transmission surface , wherein the transmission ranges between the friction ring and the first outer and the second inner friction wheel are offset from one another by 180.
  • the offset of the transmission range by 180 is known from gear transmissions with an eccentrically double-toothed intermediate member, for example from US Pat. No. 546,249.
  • the eccentrically changeable friction ring is now, on the one hand, as in AT-PS 222.966, with its outward-facing transmission surface in the housing-fixed, concentrated trical friction wheel, but on the other hand, due to the solution according to the invention, it is also forced with its inwardly directed transmission surface into the concentric friction wheel connected to the output shaft.
  • the transmission of the rotational movement between the radially and thus eccentrically shifting friction ring and the second concentric friction wheel takes place directly without an intermediate member, and the axial distance change of the friction rings of the second friction wheel is achieved by its axial coupling with the first outer friction wheel.
  • one friction ring of both friction wheels is axially displaceable, with both friction rings being assigned a common displacement device and an axial roller bearing being arranged between them.
  • the driver of the friction ring is assigned an axially displaceable adjusting device, the axial displacement of which moves the driver radially via the articulated lever.
  • At least one compensating body can be coupled to the articulated levers, which is displaced radially opposite the driver by the adjusting device in order to balance the driver at least statically.
  • the inventive design of the friction gear also has the further advantage that the mass of the eccentrically variable components is restricted to the friction ring, so that a smaller one is used to compensate for the changing imbalance. counter-changeable balancing mass is required.
  • the design according to the invention offers the possibility of providing the balancing weights axially on both sides of the friction ring, so that not only a static but also a dynamic balancing. tion can be reached.
  • a preferred embodiment of the ⁇ invention also avoids large extent the occurrence of tilting moments and thus uneven loads on the Ubertragungsflachen in that the plane of symmetry of the two friction wheels and the friction ring are together.
  • Fig. 1 shows a longitudinal section through a first exemplified embodiment "of the invention
  • Figure 2 is a longitudinal section through a second gameforsbei.
  • Figure 5 shows a longitudinal section through a third gameforsbei.
  • Fig. 6 is a section along the line VI - VI of Fig. 5; U.N
  • FIG. 7 shows a longitudinal section through a fourth exemplary embodiment.
  • a driver 2 is connected in a rotationally fixed manner to the drive shaft 1, but its eccentricity and preferably also axially adjustable.
  • the drive shaft 1 in the area of the driver 2 has a square section 17 which penetrates a recess 18 of the driver 2.
  • the recess 18 has the same width, but a greater length than the square section 17, so that the driver 2 can be displaced in the longitudinal direction of the recess 18.
  • the driver 2 is surrounded by a radial roller bearing 21 on which a cranked disc 3 is rotatably mounted.
  • a friction ring 4 is fastened to the side of the disk 3, said friction ring having four conical transmission surfaces 30, 31 and having a convex octagonal cross section.
  • the two outwardly directed conical transmission surfaces 30 engage between two friction rings 7, 8 of a first, outer friction wheel 6 connected non-rotatably to the housing 5, whereby they interact in one area with the transmission surfaces 33 of the friction rings 7, 8 .
  • the distance between the two friction rings 7, 8 can be changed, which is achieved by axially displacing a friction ring 8.
  • the two other, inwardly directed, conical transmission surfaces 31 of the friction ring 4 engage in between two friction rings 10, 11 of a second, inner friction wheel 9, which can also be changed at a distance from one another, the transmission surfaces 31 being in a region offset by 180 cooperate with the transmission surfaces 34 of the friction rings 10, 11.
  • a friction ring 10 is axially fixed and the second friction ring 11 is designed to be axially displaceable, the second friction ring 11 being axially displaceable but non-rotatably mounted on a cranked part of the second friction wheel 9.
  • the second friction wheel 9 is non-rotatably connected to the output shaft 12.
  • the two axially displaceable friction rings 8, 11 are adjustable by a common displacement device 14, 15, 16, an axial roller bearing 13 being arranged between the two friction rings 8, 11, since they rotate relative to one another.
  • the displacement device has an adjusting ring 15 which can be rotated on a thread 14 of an annular extension 32 which is fixed to the housing and surrounds the output shaft 12.
  • the adjusting ring 15 acts on a plurality of pressure bolts 16 which are axially displaceable in the bores 28 of the housing sides 29 and abut on the displaceable friction ring 8 of the outer friction wheel 6 fixed to the housing.
  • the rotation of the adjusting ring 15 brings about a common change in the spacing between the friction rings of the two friction wheels 6, 9.
  • the eccentric arrangement of the friction ring 4 causes an oscillating movement of the friction ring 4 when the drive shaft 1 is rotated, the outer transmission surfaces 30 of which roll on the transmission surfaces 33 of the friction rings 7, 8 of the outer friction wheel 6, line contact being provided on both sides.
  • the necessary contact pressure is achieved by a device for increasing the eccentricity, which is formed in the embodiment shown in FIG. 1 by a spring 19 which is inserted into the recess 18 of the driver 2, and radially on the square portion 17 of the drive shaft 1 supports.
  • the spring 19 other parts can also be provided, for example a hydraulically extendable component, an axially displaceable pulling wedge, the movement of the pulling wedge being able to be coupled with the movement of the friction rings or the like 5 and 6 are described.
  • the use of a spring 19 has the advantage in the transmission of not too great torques and uniform loading that the spring, which increases with increasing compression, is reduced by a suitable choice of spring the eccentricity increasing torque to be transmitted is approximately equal.
  • the spring 19 increases the eccentricity of the driver 2 and the disk 3, and thus also the friction ring 4, and the friction rings 7, 8 and 10, 11 apart moves, while at the same time providing the necessary pressure on both the outer and the inner friction wheel. There is a slight axial displacement of the friction ring 4.
  • the increase in the eccentricity leads to a reduction in the reduction ratio, which is inversely proportional to the difference in diameter of the outer friction wheel 6 and the friction ring 4.
  • Friction ring 4 is encompassed along its entire circumference by both the friction rings 7, 8 and the friction rings 10, 11, so that any relative movement between the three parts is excluded. Since the driver 2 in this case ⁇ is arranged exactly centrally on the drive shaft 1, this runs freely in the radial roller bearing 21, and the Dre movement of the driver 2 is not transmitted to the disc 3. In this case, the reduction ratio is infinite.
  • compensating bodies 23 which can be moved in opposite directions are provided. 3 and 4, the arrangement of the compensating body is shown in the two limit positions. 3 shows the position in which the infinite reduction ratio is given, ie in which there is no imbalance in the driver 2.
  • the compensating bodies 23 are arranged symmetrically to the longitudinal axis of the recess 18 of the driver 2 on levers 22 which cross each other and have elongated holes 25. A displacement of the driver 2 into the position shown in FIG. 4 causes an opposite movement of the two compensating bodies 23 and thus a static balancing of the driver. Dynamic balancing is achieved in that the compensating bodies 22 are arranged axially on both sides of the driver 2.
  • FIG. 2 A slightly different embodiment is shown in which the friction ring 4 and the axially fixed friction rings
  • the friction wheels 6, 9 have radially flat boundary surfaces.
  • the friction ring 4 is not axially shifted when changing its eccentricity.
  • the transmission surfaces 30, 31, 33, 34 are the same as in FIG. 1, as are the displaceable friction rings
  • Pins 26 projecting outward through threaded-section-like slots 27 in the housing 5, which are arranged in the friction ring 8 of the outer friction wheel 6, project outward.
  • handle parts (not shown) or an adjusting ring can also be arranged on the pins 26. This version has a shorter length of the transmission.
  • a reduction scale can be provided along the adjusting ring.
  • the radial, eccentric adjustment of the driver 2 is inevitably shown in both directions by its own adjustment device 36 to 40, and on the other hand, the displacement devices 14 to 16 or 26, 27 shown in FIGS. 1 and 2 Return springs 35 replaced.
  • the adjusting device 36 to 40 on the drive shaft side of the housing 5 is for the radial adjustment of the driver 2 of the friction ring 4 arranged.
  • the housing side wall 51 is provided with a hollow cylindrical extension 45 which is coaxial with the drive shaft 1 and which carries an external thread 40.
  • a • adjusting ring 36 is rotatable -on the thread 40 and presses on Anpreßbolzen 37, which penetrate the housing side wall 51 für ⁇ , to a stationary printing plate 38.
  • the square portion 17 of the drive shaft 1 is opposite the Ausulate ⁇ approximately embodiments of FIGS. 1 and 2 extended on both sides over the driver 2, an intermediate plate 39 being rotatably and axially displaceable on the part of the square section 17 facing the housing side wall 51 and a compensating body 42 being rotatably and axially and also radially displaceable thanks to a recess 53.
  • the recess 53 has the same width as the square section 17, but a longer length in comparison.
  • An axial roller bearing 43 is provided between the stationary pressure plate 38 and the intermediate plate 39 rotating with the drive shaft, and a pressure bearing 44 is inserted between the intermediate plate 39 and the compensating body 42.
  • the thrust bearing 44 serves to reduce the friction between the coaxial intermediate plate 39 and the radially displaceable compensating body 42, and can for example consist of balls or rollers held in a cage, not shown, the grooves 52 running in the radial displacement device roll away.
  • the compensating body 42 serves for balancing the driver 2 and is therefore radially displaceable in opposite directions.
  • four articulated levers 41 are provided, each of which forms a parallel gram link.
  • the compensating body 42 is provided with two slots which run parallel to the longer side of the recess 53, one slot being provided on each side of the recess 53.
  • Two hinge axes 48 pass through the equalizing body 42 parallel to the shorter side of the recess 53 and form the bearings for the articulated levers 41 arranged in pairs.
  • Two opposing articulated levers 41 are further connected in the middle by a guide pin 47, in a longitudinal slot 46 of the square portion 17 axially slidably sin the other ends of the two-armed articulated levers 41 are in the same way in the driving element 2 stored, ⁇ ie of "Fig. 6 is seen more clearly.
  • the carrier 2 has zw slots 50, which extend parallel and on both sides of the longer side of the recess 18 in the driver 2.
  • the ends of the two-armed articulated lever 41 are mounted in articulated axes 49 which extend parallel to the shorter side of the recess 18 through the driver 2.
  • An axial pressure on the Compensating body 42 moves the guide pin 47 in the longitudinal slot 46. Since the friction rings 30, 31 of the friction ring 4 - on the friction rings 33, 34 of the Rei wheels 6, 9 are present, the free axial displaceability of the disk 3 connected to the friction ring 4 with 2 is not given.
  • the articulated levers 41 are therefore rotated about the guide bolts 47, as a result of which the driver 2 on the one hand and the compensating body 42 on the other hand are displaced radially, but in opposite directions
  • a further, equally designed compensating body 42 is preferably arranged on the part of the square section 17 of the drive shaft 1 facing the output shaft 12, which also has a pair of equalizing bodies 42 arranged articulated lever 41 is connected to the Mitneh ⁇ mer 2, which are also guided on the driver in the slots 50 and are mounted on the hinge axes 49.
  • These articulated levers 41 are also provided with guide bolts 47, which are also axially displaceably guided in the longitudinal slot 46 of the square section 17.
  • This structural design of the adjusting device is suitable both for the embodiment shown in FIG. 5 with four conical transmission surfaces 30, 31 of the friction ring 4 and for an embodiment corresponding to FIG. 2 with only two such transmission surfaces.
  • the change in the eccentricity that is to say the radial displacement of the driver, is caused by "" the "tapered” transmission surfaces - - - - • also an axial displacement " ds""M'it ⁇ rehme_rs".”-
  • the output body - shaft-side compensating body will remain virtually or even completely axially unchangeable and can only be adjusted radially 2, however, the driver 2 remains axially unchanged, and the two compensating bodies 42 are alternately axially displaced when the adjusting device is actuated.
  • a plurality of return springs 35 are prestressed between the housing side wall 29 and the displaceable friction ring 8 of the outer friction wheel 6 in order to reset the two displaceable friction rings 8, 11 of the friction wheels 6, 9.
  • both the adjustment of the eccentricity of the friction ring 4 and the axial displacement of the friction rings 8 and 11 of the friction wheels take place 6, 9 inevitably in both directions.
  • the displacement device 14 to 16 shown in FIG. 1 is adopted for the axial displacement of the friction rings 8, 11, and the adjustment device 36 to 40 shown in FIG. 5 is provided for the radial adjustment of the driver 2.
  • the cone angles of the transmission surfaces 30, 31, 33 and 34, the angles of the articulated levers 41, and the pitches of the threads 14 and 40 can be matched to one another by experiments in such a way that the two adjusting rings 15 and 36 are coupled to one another and can be operated together.
  • the resetting of the respective parts of the transmission which are not directly pressurized via the adjusting rings 15 or 36 takes place indirectly during the adjustment from the other adjusting ring 36 or 15, so that there is no need for any return spring and the contact pressure is not dependent on the spring.
  • the adjusting device 36 to 40 of FIG. 5 can be. of course, also combine with the displacement device according to FIG. 2. It is also possible to adjust the pressure plate ⁇ 38 ⁇ in the figure; ⁇ 5 and- 7 in the manner de -Ver- position of the friction ring - 8- according to Fig. 2 au-sz ⁇ rbxldenr
  • the - pressure plate 38 can therefore be provided with pins which through thread-like slits in the housing- 5 protrude radially outwards.
  • the transmission according to the invention has a continuously variable reduction ratio in the case of a coaxial drive and output shaft and a particularly space-saving design, and is also particularly suitable for high torques and uneven loads thanks to the indirect power transmission via the friction ring.
  • the infinite reduction eliminates the need for an additional clutch and provides special protection for the drive.

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  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Friction Gearing (AREA)

Abstract

Sur un arbre d'entrainement (1) est monte un organe d'entrainement (2) qui est solidaire en rotation de cet arbre, mais deplacable radialement et axialement; un disque (3) est monte a rotation sur cet organe d'entrainement (2) par l'intermediaire d'un palier a roulement (21) et porte un anneau de friction (4) presentant quatre surfaces de transmission coniques (30, 31). Les surfaces de transmission (30) de l'anneau de friction (4) roulent sur des surfaces de transmission (33) de deux couronnes de friction (7, 8) d'une roue de friction (6) solidaire du boitier et les surfaces de transmission (31) roulent sur des surfaces de transmission (34) des deux couronnes de friction (10, 11) d'une deuxieme roue de friction (9) montee sur l'arbre entraine (12), concentriquement a la roue de friction (6). L'espacement des couronnes de friction (7, 8) respectivement (10, 11) est variable. Lors de la rotation de l'arbre d'entrainement (1), l'anneau de friction (4) accomplit un lent mouvement oscillant autour de l'arbre d'entrainement (1) et transmet ce mouvement a la roue de friction (9). Les deux domaines de transmission sont decales de 180 . L'etendue de l'excentricite est reglable entre un maximum et zero, ce qui permet de realiser une demultiplication jusqu'a l'infini.
PCT/AT1980/000016 1979-06-01 1980-05-23 Dispositif a roues de friction pour transmettre, avec un rapport de vitesse variable de maniere continue, un mouvement rotatif entre deux arbres coaxiaux WO1980002729A1 (fr)

Priority Applications (7)

Application Number Priority Date Filing Date Title
AU5981481A AU5981481A (en) 1980-05-23 1980-05-23 Friction wheel device for transmitting, with a continuously variable speed ratio, a rotary motion between two coaxials shafts
JP56501693A JPS57500748A (fr) 1980-05-23 1981-05-21
AT81901320T ATE9387T1 (de) 1980-05-23 1981-05-21 Getriebe zur stufenlos veraenderbaren uebertragung einer drehbewegung zwischen zwei koaxialen wellen.
PCT/AT1981/000011 WO1981003367A1 (fr) 1980-05-23 1981-05-21 Mecanisme a reglage continu pour la transmission d'un mouvement rotatif entre deux arbres coaxiaux
EP81901320A EP0052625B1 (fr) 1980-05-23 1981-05-21 Mecanisme a reglage continu pour la transmission d'un mouvement rotatif entre deux arbres coaxiaux
DE8181901320T DE3165970D1 (en) 1980-05-23 1981-05-21 Mechanism with contiuous adjustment for the transmission of a rotary motion between two coaxial shafts
DD81230259A DD159196A5 (de) 1980-05-23 1981-05-25 Getriebe zur stufenlos veraenderbaren uebertragung einer drehbewegung zwischen zwei koaxialen wellen

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
AT399679A AT360811B (de) 1979-06-01 1979-06-01 Reibradgetriebe
AT3996/79 1979-06-01

Publications (1)

Publication Number Publication Date
WO1980002729A1 true WO1980002729A1 (fr) 1980-12-11

Family

ID=3558239

Family Applications (1)

Application Number Title Priority Date Filing Date
PCT/AT1980/000016 WO1980002729A1 (fr) 1979-06-01 1980-05-23 Dispositif a roues de friction pour transmettre, avec un rapport de vitesse variable de maniere continue, un mouvement rotatif entre deux arbres coaxiaux

Country Status (5)

Country Link
EP (1) EP0029435A1 (fr)
AT (1) AT360811B (fr)
FR (1) FR2458008A1 (fr)
IT (2) IT8021940V0 (fr)
WO (1) WO1980002729A1 (fr)

Cited By (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO1981003367A1 (fr) * 1980-05-23 1981-11-26 R Falkner Mecanisme a reglage continu pour la transmission d'un mouvement rotatif entre deux arbres coaxiaux
US4920827A (en) * 1988-03-08 1990-05-01 Bridgestone Cycle Co., Ltd. Stepless speed change device
US4924730A (en) * 1987-08-25 1990-05-15 Jaguar Cars Limited Transmission systems
US5013288A (en) * 1989-01-21 1991-05-07 Jaguar Cars Limited Transmission systems

Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2831373A (en) * 1953-06-11 1958-04-22 Graham Transmissions Inc Variable speed friction gearing
US3020782A (en) * 1957-01-24 1962-02-13 Sacchi Giulio Speed change device having resiliently deformable wheels
FR1332135A (fr) * 1963-12-16
DE1191650B (de) * 1962-08-01 1965-04-22 Gerhard Hegner Stufenlos verstellbares Reibrad-Exzentergetriebe
DE2559437A1 (de) * 1975-07-18 1977-03-24 Heynau Gmbh Hans Stufenlos einstellbares reibungsgetriebe mit umlaufender doppelkegelscheibe

Patent Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
FR1332135A (fr) * 1963-12-16
US2831373A (en) * 1953-06-11 1958-04-22 Graham Transmissions Inc Variable speed friction gearing
US3020782A (en) * 1957-01-24 1962-02-13 Sacchi Giulio Speed change device having resiliently deformable wheels
DE1191650B (de) * 1962-08-01 1965-04-22 Gerhard Hegner Stufenlos verstellbares Reibrad-Exzentergetriebe
DE2559437A1 (de) * 1975-07-18 1977-03-24 Heynau Gmbh Hans Stufenlos einstellbares reibungsgetriebe mit umlaufender doppelkegelscheibe

Cited By (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO1981003367A1 (fr) * 1980-05-23 1981-11-26 R Falkner Mecanisme a reglage continu pour la transmission d'un mouvement rotatif entre deux arbres coaxiaux
US4924730A (en) * 1987-08-25 1990-05-15 Jaguar Cars Limited Transmission systems
US4920827A (en) * 1988-03-08 1990-05-01 Bridgestone Cycle Co., Ltd. Stepless speed change device
US5013288A (en) * 1989-01-21 1991-05-07 Jaguar Cars Limited Transmission systems

Also Published As

Publication number Publication date
IT8021940V0 (it) 1980-05-30
ATA399679A (de) 1980-06-15
AT360811B (de) 1981-02-10
IT1149967B (it) 1986-12-10
FR2458008A1 (fr) 1980-12-26
EP0029435A1 (fr) 1981-06-03
IT8022476A0 (it) 1980-05-30

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