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WO1998011364A1 - Variateur de vitesse - Google Patents

Variateur de vitesse Download PDF

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Publication number
WO1998011364A1
WO1998011364A1 PCT/IT1997/000221 IT9700221W WO9811364A1 WO 1998011364 A1 WO1998011364 A1 WO 1998011364A1 IT 9700221 W IT9700221 W IT 9700221W WO 9811364 A1 WO9811364 A1 WO 9811364A1
Authority
WO
WIPO (PCT)
Prior art keywords
shaft
cogwheels
speed change
change gear
rotation axis
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/IT1997/000221
Other languages
English (en)
Inventor
Enrico Nino
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.)
Individual
Original Assignee
Individual
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
Priority claimed from IT96PZ000003 external-priority patent/IT1289432B1/it
Priority claimed from IT97PZ000002 external-priority patent/IT1297972B1/it
Application filed by Individual filed Critical Individual
Priority to AU43964/97A priority Critical patent/AU4396497A/en
Publication of WO1998011364A1 publication Critical patent/WO1998011364A1/fr
Anticipated expiration legal-status Critical
Ceased legal-status Critical Current

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
    • F16H55/00—Elements with teeth or friction surfaces for conveying motion; Worms, pulleys or sheaves for gearing mechanisms
    • F16H55/32—Friction members
    • F16H55/52—Pulleys or friction discs of adjustable construction
    • F16H55/54—Pulleys or friction discs of adjustable construction of which the bearing parts are radially adjustable
    • 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
    • F16H9/00—Gearings for conveying rotary motion with variable gear ratio, or for reversing rotary motion, by endless flexible members
    • F16H9/02—Gearings for conveying rotary motion with variable gear ratio, or for reversing rotary motion, by endless flexible members without members having orbital motion
    • F16H9/04—Gearings for conveying rotary motion with variable gear ratio, or for reversing rotary motion, by endless flexible members without members having orbital motion using belts, V-belts, or ropes
    • F16H9/10—Gearings for conveying rotary motion with variable gear ratio, or for reversing rotary motion, by endless flexible members without members having orbital motion using belts, V-belts, or ropes engaging a pulley provided with radially-actuatable elements carrying the belt

Definitions

  • the invention concerns a stepless speed change gear.
  • it is used in drive transmission between a motor and a user with the aim of providing an angular velocity variation ratio in output on a rotating shaft with respect to an input speed, with continuous variation selection.
  • the first of these relates to the maximum transmittable torque, which is limited by the fact that drive transmission is guaranteed by the friction forces developing between the conical plates of the pulleys and the sides of the transmission belt and not, for example, by the shear stress resistance of the teeth constituting the gearings of a traditional mechanical transmission.
  • the maximum transmittable power is further limited by the resistance to traction of the belt used, which may be synthetic in the case of more economical applications, or which may be made of metal. In the latter case a special conformation is used, using metal belts and anchors constituting the belt itself.
  • Another type of known-type device for continuous drive variation is constituted by hydraulic converters, essentially consisting of a variable-delivery pump and a hydraulic actuator.
  • the principle is as follows: drive is transmitted to the variable delivery pump and a variable delivery of hydraulic oil is obtained; by sending the oil to an actuator (hydraulic motor), the latter will assume a rotation velocity which depends on the delivery sent thereto, different from the delivery supplied to the pump, thus realising the requested variation in speed.
  • an actuator hydraulic motor
  • the energy efficiency of this device is particularly low, given the inevitable losses incurred when supplying and removing energy from the hydraulic oil. Disclosure of Invention
  • the present invention achieves the above-mentioned aim by providing a speed change gear able to transmit motion from a first to a second shaft, as characterized in the claims that follow numbered from 1 to 8, comprising: at least one support solidly constrained to the first shaft; at least two rotatable gearwheels, solid in rotation with the support and connected by means of a mechanical transmission to the second shaft and able on command to vary in distance from the rotation axis of the first shaft; at least one flexible mechanical organ, enmeshing with the gearwheels, on which organ the gearwheels revolve, which organ is conformed and arranged in such a way that one of the wheels in always enmeshed; means for adjusting the timing among the cogs of the cogwheels and the flexible mechanical organ according to the distance of the wheels from the rotation axis of the first shaft.
  • the means for timing adjustment might comprise means for impressing rotation on the cogwheels about their respective axes by moving them radially with respect to the axis of the first shaft.
  • the means for impressing rotation might comprise two splined shafts wherein the splines are helicoid, along each of which splines a gearwheel of the mechanical transmission can slide; the gearwheel being part of the mechanical transmission connecting the gearwheels to the second shaft.
  • the speed change gear can comprise, for example, at least one driving gear of the flexible mechanical organ, a position of which driving gear is variable on command.
  • the gear wheels are slidable on radial guides predisposed on the first support.
  • the speed change gear can comprise a plurality of idler gears, solid in rotation with the first support, arranged circumferentially thereto, on which the flexible mechanical organ is wound and enmeshes.
  • the idler gears can be commanded to vary their distance from the rotation axis of the first shaft.
  • the mechanical transmission connecting the gear wheels to the second shaft is geared and can comprise at least one gearwheel able to slide radially with respect to the rotation axis of the first shaft.
  • the flexible mechanical organ can be, for example, a normal chain or roller track, or a Morse chain, or other known devices having linked toothings, preferably semi-circularly or semi-polygonally wound around a rotating or fixed support.
  • the flexible mechanical organ functions as a rolling track for two gearwheels which engage alternatingly thereon.
  • the rolling track constituted for example by the chain or other like device, is wound in such a way as to give rise to an open ring, substantially a semi-circumference.
  • the two gearwheels are located symmetrically with respect to the rotation axis of the support, which can be, for example, a main plate drawing the two gear wheels in rotation.
  • a number of gearwheel revolutions is obtained which number is greater than one and which depends on the position of the gearwheels with respect to the centre of rotation of the plate.
  • the motion can be imparted to the gearwheels in such a way that, by rotating the main plate, a number of output revolutions will be obtained that which depends, as in the previous case, on the position of the gearwheels with respect to the centre of the plate, but which is in any case smaller than the number of input revolutions.
  • the invention behaves as a multiplier, or overgear, of the number of input revolutions with respect to the output revolutions, while in the second case it behaves as a reducer.
  • the coupling of two main plates gives rise to a device which can multiply the angular input speed or reduce it, realising a synchronous transmission and obviating slide problems, and considerably increasing the transmittable tangential force.
  • the invention achieves the above-mentioned aim by providing a speed change gear for transmitting motion from a first shaft to a second shaft, as characterized in the appended claims numbered from 9 to 16, comprising: at least one first support, solidly constrained to the first shaft at least two rotatable gearwheels, solid in rotation with the support and connected by means of a mechanical transmission to the second shaft and able on command to vary in distance from the rotation axis of the first shaft; at least one flexible mechanical organ, enmeshing with the gearwheels, on which organ the gearwheels revolve, which organ is conformed and arranged in such a way that one of the wheels in always enmeshed; means for adjusting the timing among the cogs of the cogwheels and the flexible mechanical organ according to the distance of the wheels from the rotation axis of the first shaft.
  • the timing adjustment means can comprise means for rotating the gearwheels about their respective axes by effect of displacing them radially about the axis of the first shaft.
  • the means for rotating preferably comprise a second flexible mechanical organ enmeshing with the gear wheels and having adjustable-position ends.
  • the means for timing adjustment can comprise means for lengthening and shortening a tract of the flexible mechanical organ comprised between the gearwheels.
  • the lengthening and shortening means preferably, though not necessarily, comprise a wheel coupled with the above-mentioned tract, with possibility of varying the distance of said wheel from the axis of the first shaft.
  • it can comprise: a second support solidly constrained to the second shaft; at least two gearwheels, solid in rotation with the second support, said at least two gearwheels on command being able to vary their distance from the rotation axis of the second shaft, said gearwheels enmeshing with the first flexible mechanical organ in such a way that at least one thereof is always enmeshed; means for adjusting, according to the distance of the gearwheels from the rotation axis of the second shaft, the timing between the cogs of the wheels and the first flexible organ.
  • the first flexible mechanical organ - which might be, for example, a normal chain with links and rollers - is mobile during functioning and is used for the transmission of motion between the two gearings (drive gearing and driven gearing) comprising the gearwheels located at the variable-radius circumference.
  • the chain enmeshes on the specially- synchronised gearwheels, eliminating slippage problems (through creating a synchronous transmission) and considerably increasing the transmittable tangential force.
  • figure 1 shows a schematic and simplified plan view of a first embodiment of the gear speed change of the invention
  • figure 2 shows the device of figure 1 in a different operative configuration
  • figure 3 is an enlarged-scale schematic section made according to the III-III of figure 2
  • figure 4 is a schematic and simplified plan view of a second embodiment of the invention
  • figure 5 is a schematic perspective view of the gear speed change of figure 4.
  • FIG. 1 shows a gear speed change
  • FIG. 1 shows a gear speed change
  • FIG. 1 shows a gear speed change
  • FIG. 1 shows a gear speed change
  • FIG. 1 shows a gear speed change
  • FIG. 1 shows a gear speed change
  • FIG. 1 shows a gear speed change
  • FIG. 1 shows a gear speed change
  • FIG. 1 shows a gear speed change
  • FIG. 1 shows a gear speed change
  • FIG. 1 shows a gear speed change
  • the chain 4 is wound in such a way as to form an open polygon, the number of sides thereof depending on the number of gearwheels 2 and idler wheels 3 present; in effect, the chain 4 represents a variable- configuration rolling track, symmetrical in a vertical plane; the two gearwheels 2 can be located either internally or externally of the rolling track.
  • the invention functions as follows. When the first shaft 11 is rotated, the main plate 1 is drawn along with it. There are two gearwheels 2 on the main plate 1 , connected thereto by bearings or other known means so that the gearwheels 2 can rotate on their own axes (which are orthogonal to the plate 1 ) and, when necessary, perform radial translations along the grooves 13.
  • One of the two gearwheels 2 is securely enmeshed in the chain 4 , as can be seen in figures 1 and 2.
  • the chain 4 is constrained at its opposite ends by two chain-tighteners 10, so that the gear wheel 2 enmeshed in the chain 4 is forced to rotate in an opposite direction to the rotation direction of the main plate 1.
  • the remaining gearwheel 2 is also set in rotation, since the motion is transmitted by the enmeshed gearwheel 2, by means of the crown 6 solidly constrained thereto, from the crown 6 to a pinion 8, from the pinion 8 to the splined shaft 7, then to the other pinion 8 and then to the central crown 5; then from the central crown 5 (in inverse order) through another pinion 8, the other splined shaft 7, the other pinion 8, and thence to the crown 6 keyed on the other gearwheel 2 not engaged on the chain 4.
  • the motion between the two wheels 2 can also be transmitted using other known means without any consequent loss in the invention " s validity.
  • axes A-B and C- D constitute axes of symmetry for the gearwheels 2 and the chain 4 wound about the semi-polygon (or semi-circle) to the left of axis C-D, and there will be a whole number of chain 4 links wound about the gearwheels 2 and part of the idler wheels 3.
  • the velocity with which the two gearwheels 2 are rotated depends on the angular velocity of the plate 1 , the dimensions of the gearwheels 2 themselves and the radial position of the gearwheels 2 on the plate 1. With geometric positions and angular velocity of the main plate 1 the same, the speed of the gearwheels 2 and thus the central crown 5 the gearwheels 2 are connected to, can be varied continuously simply by continuously varying the radial position of the gearwheels 2 by causing them to slide along the radial grooves 13.
  • the gearwheels 2 receives drive from the central crown 5 and by enmeshing in the chain 4 draw the main plate 1 in rotation and, therefore, also the first shaft 1 1 connected thereto, thus providing the output.
  • the invention functions as a reducer.
  • the variation of the radial position of the two gearwheels 2 has to be accompanied by a variation in the radial position of the idler wheels 3 keyed by bearings and supports in the grooves 13 of the main plate 1.
  • the function of the idler wheels 3 is to cause the chain 4 to wind in such a way as to form a semi- circumference functioning as a rolling track for the gearwheels 2.
  • This function can be substituted, without detracting from the invention, by other known devices such as, for example, a system of rests acting externally to the main plate 1 and curving the chain so as to form the rolling track for the gearwheels 2 in the radial position required. Furthermore, the gearwheels 2 can be located externally of the semi-circumference without the invention losing its validity.
  • the variation in the radial position of the gearwheels 2 and the idler wheels 3 on the main plate 1 can be obtained using known means such as, for example, con rods connected on one side to the gearwheels 2 and the idler wheels 3 and on the other side to a slidable sleeve on the first shaft 1 1 or the second shaft 12 and whose axial position imposes a radial position on the gearwheels 2 and the idler wheels 3.
  • Another method could be constituted by a multiple cam device whose relative rotation with respect to the main plate 1 locates the gearwheels 2 and the idler wheels 3 in the desired radial position.
  • the radial displacement of the gearwheels 2 and the idler wheels 3 was obtained by using steel cables activated by a slidable sleeve on the first shaft 1 1.
  • the radial displacement of the gearwheels 2 and the idler wheels 3 must be accompanied by a variation in the length of the chain 4 wound in a semi-circle (or open polygon) about the gearwheels 2 and the idler wheels 3.
  • This change in length is obtained by means of a rotation or translation of the chain-stretchers 10, whose movement is connected to the movement of the radial position command of the gearwheels 2 and the idler wheels 3, which movement is obtained using known means not described herein for reasons of brevity.
  • the variation in the radial position of the gearwheels 2 and the idler wheels 3 must be accompanied by a change in the position of the two intermediate wheels 9, whose task is to guarantee that the chain 4 embraces the main plate 1 over a 180° span in order to prevent the gearwheels 2 from becoming both enmeshed on the chain 4; this is to prevent the gearwheels 2 and idler wheels 3 from occasioning jolts during the radial position change manoeuvre - i.e. the transmission ratio change operation.
  • figure 1 the invention is shown in an "open" position, that is with the gearwheels 2 and the idler wheels 3 located at a greater radial distance, about halfway along the main plate 1 radius, while in figure 2 the invention has undergone an adjustment operation which has brought the gearwheels 2 and the idler wheels 3 to a smaller radial distance, in a position close to the rotation axis of the main plate 1.
  • This adjustment obviously, has also changed the position of the intermediate wheels 9 and the chain-stretchers 10.
  • Each shaft 101 and relative gearing comprises a series of idler wheels 105, at least two pairs of gearwheels 106 and 107 having steps which are compatible with the first chain 103, a second chain 108 for synchronising twin gearwheels 106 and 107, two terminals 109 and 1 10 for controlling the second chain 108, an idler wheel 1 1 1 for compensating the timing displacement.
  • Each pair of twin gearwheels 106 and 107 is constituted by two coaxial wheels constrained one to the other, one above and one below, which rotate freely on their shared axis.
  • the lower of the twin gearwheels enmeshes with the first or primary chain 103, and for this reason is termed the primary wheel, while the upper wheel enmeshes with the secondary chain, in effect a timing chain 108, and so is termed the secondary wheel.
  • the above-described synchronous gear speed change functions as follows. Starting with a description of the first shaft 101 and its relative gearings, from the figure it can be seen how the primary chain 103 winds about two of the lower wheels of the twin gearwheels 106 and 107 as well as part of the idler wheels 105.
  • the timing or secondary chain 108 enmeshes on the upper wheels of the gearwheels 106 and 107 and also about part of the idler wheels 105.
  • the take-up idler wheel 104 must guarantee an extent of primary chain 103 winding about both gearings constrained to the first and second shafts 101 and 102 which extent of winding ensures that the length of first chain 103 left on the two gearings of the shafts 101 and 102 is shorter than the length of chain comprised between the two pairs of timing gearwheels 106 and 107.
  • the primary wheel of gearwheels 106 re-contacts with the primary chain 103 in the zone indicated by Bl .
  • the circumference of the perimeter of the first shaft gearing 101 can be divided by the step of the primary chain 103 and result in a whole number.
  • the teeth of gearwheels 106 and 107 enmeshing with the primary chain 103 were part of a crown cogwheel having the diameter of the gearing of the first shaft 101 and enmeshing with the primary chain 103.
  • the primary wheel of gearwheels 106 by effect of the rotation of the gearing of the first shaft 101 , would enmesh perfectly with the primary chain 103 at every revolution of the first shaft 101 , guaranteeing regular transmission of motion between the gearing of the first shaft 101 and the primary chain 103.
  • the equation [1] shows how the number of links is a linear function of R.
  • M becomes a whole number having periodic frequency.
  • the added radial displacement of idler wheel 111 compensates by the fraction of step P necessary to bring M back into a whole number value.
  • the displacement of the idler wheel 1 1 1 is limited by the fact that the maximum M variation value is ⁇ P/2.
  • the extra displacement of idler wheel 111 is achieved using known means not illustrated here for reasons of brevity, and is synchronised with the radial displacement of those other wheels 105, 106 and 107 which make up the gearing.
  • the link-number compensation can be achieved using other methods apart from the one described above; for example, by simply effecting a rotation (using known means omitted from the present description for reasons of simplification) of the pair of gearwheels 106 about a rotation axis passing through the centre of the toothing of said pair of gearwheels 106.
  • a rotation using known means omitted from the present description for reasons of simplification
  • the oscillation can be either clockwise or anticlockwise, depending on the phase displacement of the primary chain 103, and thus dependently on the radius of the gearing of the first shaft 101.
  • the above is also true when the gearing of the first shaft 101 is no longer a circumference but a polygon with N sides.
  • the variation of diameter 2R of the gearing of the first shaft 101 means that the quantity of chain 103 wound about the various wheels must also change, in particular must increase by R and vice versa.
  • the part of chain comprised between gearwheels 106 and 107 is guaranteed by a rotation of gearwheel 106 activated by the control terminal 109 and a rotation of gearwheel 107 activated by the control terminal 110.
  • the entity of these rotations is clearly dependent on the variation of R.
  • the movements of terminals 109 and 1 10 are connected with the mechanisms varying the diameter of the gearing of the first shaft 101 by means of known means, not illustrated for reasons of simplicity.
  • the variation in the diameter of the gearing of the first shaft 101 can be carried out in all angular positions of the first shaft 101 except for those positions where there is a simultaneous enmeshing of gearwheel 106 with a tract of primary chain 103 situated in zone Bl and of wheel 107 with a tract of primary chain 103 situated in zone Al.
  • a variation in the quantity of primary chain 103 wound about the gearing of the first shaft 101 and second chain 108 comprised between gearwheels 106 and 107 cannot correspond to a variation in R.
  • this situation regards only a few rotation degrees and that the variation in radius R can easily be prevented (using known means not illustrated for reasons of simplicity) when the gearing of the first shaft 101 is in the previously-described angular position.
  • the above description is equally valid for the gearing of the second shaft 102.

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  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Transmission Devices (AREA)

Abstract

L'invention concerne un variateur de vitesse capable de produire un rapport de variation sélectionnable en continu entre la vitesse angulaire de sortie et la vitesse d'entrée. Le dispositif de l'invention se caractérise principalement en ce que la transmission entre un moteur et un utilisateur est assurée par un système à deux roues dentées (2) placées à une certaine distance d'un axe de rotation d'une plaque principale (1) qui vient en prise avec une chaîne à rouleaux (4) fonctionnant comme un chemin de roulement pour les roues dentées (2). Pendant le fonctionnement, les roues dentées (2) peuvent être replacées en continu à des distances variables de l'axe de rotation de la plaque (1) et ainsi faire varier la circonférence d'une révolution, produisant ainsi différentes vitesses angulaires à vitesse angulaire d'entrée similaire. Le dispositif selon l'invention, dans lequel on utilise des engrenages à chaîne normaux, peut transmettre des forces tangentielles considérables de manière synchronisée, sans glissement entre les divers éléments.
PCT/IT1997/000221 1996-09-09 1997-09-10 Variateur de vitesse Ceased WO1998011364A1 (fr)

Priority Applications (1)

Application Number Priority Date Filing Date Title
AU43964/97A AU4396497A (en) 1996-09-09 1997-09-10 A stepless speed change gear

Applications Claiming Priority (4)

Application Number Priority Date Filing Date Title
IT96PZ000003 IT1289432B1 (it) 1996-09-09 1996-09-09 Variatore di velocita sincrono
ITPZ96A000003 1996-09-13
IT97PZ000002 IT1297972B1 (it) 1997-06-12 1997-06-12 Variatore di velocita continuo ad ingranaggi
ITPZ97A000002 1997-06-13

Publications (1)

Publication Number Publication Date
WO1998011364A1 true WO1998011364A1 (fr) 1998-03-19

Family

ID=26331961

Family Applications (1)

Application Number Title Priority Date Filing Date
PCT/IT1997/000221 Ceased WO1998011364A1 (fr) 1996-09-09 1997-09-10 Variateur de vitesse

Country Status (2)

Country Link
AU (1) AU4396497A (fr)
WO (1) WO1998011364A1 (fr)

Cited By (11)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2002088575A1 (fr) * 2001-03-28 2002-11-07 Eckart Hettlage Transmission a courroie crantee
EP1600664A1 (fr) 2004-05-28 2005-11-30 Albrecht Baumann Transmission à variation continue et procédé de fonctionnement
WO2006122507A1 (fr) * 2005-05-20 2006-11-23 Huidong Zhang Roue de transmission à diamètre variable, dispositif à vitesse variable et transmission continue automatique
EP3009713A4 (fr) * 2013-06-10 2016-06-01 Jatco Ltd Mécanisme de transmission variable en continu
CN106286735A (zh) * 2016-11-15 2017-01-04 黄华 盘形无极变速器
WO2018014895A1 (fr) * 2016-07-19 2018-01-25 Röhl André Franz Dispositif de transmission manuelle continue doté d'une variation du rapport de transmission en fonction du couple pour transmission de force par complémentarité de forme
IT201600097489A1 (it) * 2016-09-28 2018-03-28 Giorgio Cattini Variatore di velocita'
CN108506439A (zh) * 2018-05-17 2018-09-07 张锐 一种变速传动系统
CN109552545A (zh) * 2019-01-28 2019-04-02 石甫业 无级变速器及其驱动方法、自行车及自行车的控制系统
CN113942787A (zh) * 2021-09-07 2022-01-18 杭州先罗输送机械有限公司 一种提升机可变直径的复合式链轮张紧装置
DE102021003461A1 (de) 2021-07-03 2023-01-05 Ali Akbar Tarighatjou Das neue CVT-Getriebe

Citations (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3374691A (en) * 1966-05-11 1968-03-26 Charles R. Schottel Variable speed transmission
DE3247692A1 (de) * 1982-12-23 1984-06-28 Arne 5830 Schwelm Schmidt Stufenlos verstellbares getriebe

Patent Citations (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3374691A (en) * 1966-05-11 1968-03-26 Charles R. Schottel Variable speed transmission
DE3247692A1 (de) * 1982-12-23 1984-06-28 Arne 5830 Schwelm Schmidt Stufenlos verstellbares getriebe

Cited By (17)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2002088575A1 (fr) * 2001-03-28 2002-11-07 Eckart Hettlage Transmission a courroie crantee
EP1600664A1 (fr) 2004-05-28 2005-11-30 Albrecht Baumann Transmission à variation continue et procédé de fonctionnement
WO2005116485A1 (fr) * 2004-05-28 2005-12-08 Albrecht Baumann Transmission a reglage continu, son utilisation et procede pour la faire fonctionner
US7887451B2 (en) 2004-05-28 2011-02-15 Albrecht Baumann Infinitely variable transmission, use thereof, and method for the operation thereof
WO2006122507A1 (fr) * 2005-05-20 2006-11-23 Huidong Zhang Roue de transmission à diamètre variable, dispositif à vitesse variable et transmission continue automatique
US9765860B2 (en) 2013-06-10 2017-09-19 Jatco Ltd Continuously variable transmission mechanism
KR101745813B1 (ko) 2013-06-10 2017-06-27 쟈트코 가부시키가이샤 무단 변속 기구
EP3009713A4 (fr) * 2013-06-10 2016-06-01 Jatco Ltd Mécanisme de transmission variable en continu
WO2018014895A1 (fr) * 2016-07-19 2018-01-25 Röhl André Franz Dispositif de transmission manuelle continue doté d'une variation du rapport de transmission en fonction du couple pour transmission de force par complémentarité de forme
IT201600097489A1 (it) * 2016-09-28 2018-03-28 Giorgio Cattini Variatore di velocita'
CN106286735A (zh) * 2016-11-15 2017-01-04 黄华 盘形无极变速器
CN108506439A (zh) * 2018-05-17 2018-09-07 张锐 一种变速传动系统
CN109552545A (zh) * 2019-01-28 2019-04-02 石甫业 无级变速器及其驱动方法、自行车及自行车的控制系统
CN109552545B (zh) * 2019-01-28 2024-02-27 石甫业 无级变速器及其驱动方法、自行车及自行车的控制系统
DE102021003461A1 (de) 2021-07-03 2023-01-05 Ali Akbar Tarighatjou Das neue CVT-Getriebe
CN113942787A (zh) * 2021-09-07 2022-01-18 杭州先罗输送机械有限公司 一种提升机可变直径的复合式链轮张紧装置
CN113942787B (zh) * 2021-09-07 2023-02-10 杭州先罗输送机械有限公司 一种提升机可变直径的复合式链轮张紧装置

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