WO1998023481A1 - Entrainement par chaine a rapport de transmission variable - Google Patents

Entrainement par chaine a rapport de transmission variable Download PDF

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Publication number
WO1998023481A1
WO1998023481A1 PCT/CH1997/000445 CH9700445W WO9823481A1 WO 1998023481 A1 WO1998023481 A1 WO 1998023481A1 CH 9700445 W CH9700445 W CH 9700445W WO 9823481 A1 WO9823481 A1 WO 9823481A1
Authority
WO
WIPO (PCT)
Prior art keywords
chain
chain drive
toothed
drive according
guide
Prior art date
Application number
PCT/CH1997/000445
Other languages
German (de)
English (en)
Inventor
Rolf Bächtiger
Original Assignee
Baechtiger Rolf
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 Baechtiger Rolf filed Critical Baechtiger Rolf
Priority to EP97913070A priority Critical patent/EP0877700A1/fr
Publication of WO1998023481A1 publication Critical patent/WO1998023481A1/fr

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Classifications

    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B62—LAND VEHICLES FOR TRAVELLING OTHERWISE THAN ON RAILS
    • B62M—RIDER PROPULSION OF WHEELED VEHICLES OR SLEDGES; POWERED PROPULSION OF SLEDGES OR SINGLE-TRACK CYCLES; TRANSMISSIONS SPECIALLY ADAPTED FOR SUCH VEHICLES
    • B62M9/00—Transmissions characterised by use of an endless chain, belt, or the like
    • B62M9/04—Transmissions characterised by use of an endless chain, belt, or the like of changeable ratio
    • B62M9/06—Transmissions characterised by use of an endless chain, belt, or the like of changeable ratio using a single chain, belt, or the like
    • B62M9/08—Transmissions characterised by use of an endless chain, belt, or the like of changeable ratio using a single chain, belt, or the like involving eccentrically- mounted or elliptically-shaped driving or driven wheel; with expansible driving or driven wheel

Definitions

  • the present invention relates to a chain drive according to the preamble of claim 1.
  • Chain drives are often used for largely wear-free and slip-free power transmission between two shafts that are relatively far apart.
  • the shafts are provided with gears that are connected to each other by a chain.
  • the gear ratio of the chain drive is determined by the choice of the diameter of the gears used.
  • several gear wheels of different diameters are provided on at least one shaft to change the transmission ratio.
  • the transmission ratio or the ratio of the diameters of the gears connected to one another via the chain can be adjusted in stages. It is known that the (drive) chain should always run at right angles to both shafts and must not be twisted.
  • a chain drive with an automatically changing transmission ratio is known from EP 0 116 731 A1.
  • this drive in which the transmission ratio is automatically adjusted by the continuous change in the diameter of a variable gear, two interconnected outer plates are provided, which are connected via a spring to a star wheel, the ends of which are connected radially in via a web small gear wheels guided to the outer plates are connected, which form the ring gear of the variable gear wheel.
  • the two plates are rotated relative to the star wheel, as a result of which the small gear wheels are shifted inwards or outwards.
  • the diameter of the variable gearwheel and the gear ratio are changed proportionally to the change in torque.
  • the continuously variable chain drive known from EP 0 116 731 A1 has the following disadvantage in particular. Since the continuous adjustment of the transmission ratio also results in a continuous change in the diameter of the drive wheel, the tooth pitch of the drive teeth provided for engagement in the link chain (roller chain) rarely corresponds to the division of the roles of the link chain. In this case, the drive teeth can directly during the mutual engagement hit a roll of the link chain, which jeopardizes the correct operation of the chain drive. Under certain circumstances, the link chain can completely disengage from the drive wheel. At least, increased loads on the drive teeth and link chain can be expected. There is also the risk that the toothed wheels will not engage in the toothed chain. However, this increases the stress on the teeth engaging in the chain and on the individual chain links.
  • a spring is also used, which must have a high spring constant in order to be able to change the transmission ratio in a normal range.
  • the spring is tensioned, causing the gears to be pulled inwards (small radius of the gear). After reducing the applied torque, the gears must be pushed outwards again by the spring force.
  • Spring elements with the necessary spring constants are hardly customary on the market and are difficult to assemble. Since the drive chain rests only at a few points of the gearwheel having the shape of a polygon, the torque transmitted to this wheel or the tensile force exerted by this wheel on the chain changes several times during each revolution. Vibrations and impacts result in a deterioration in the efficiency of the chain drive. This modulation of the load torque acting on the drive shaft also has a particularly negative effect on the ride comfort in bicycles which are equipped with such a chain drive.
  • the present invention is therefore based on the object of creating an automatic chain drive with radially displaceable segments which have at least one drive tooth which can always intervene correctly between the rollers of a link chain, regardless of the set transmission ratio. Furthermore, the use of a spring with an extremely high spring constant and a disruptive modulation of the torque acting on the drive shaft should be avoided.
  • an almost constant load torque is automatically set by changing the transmission ratio.
  • the correct engagement of the tangentially displaceable chain teeth in the link chain means that there are hardly any signs of wear.
  • the use of several drive teeth for each radially displaceable segment also results in an even distribution of the tensile force. Modulation of the torque acting on the drive shaft is thereby avoided.
  • By using a separate spring element for each segment for example, easily mountable coil springs with a relatively low spring constant can be used.
  • the individual spring elements assigned to each radially displaceable segment in particular also prevent the occurrence of an interfering mechanical play in the bearings and guideways. Further measures for the synchronization of the drive teeth with the link chain make the engagement of the drive teeth between the rollers of the link chain even more precise.
  • FIG. 1 a chain drive provided for mounting on a bicycle
  • FIG. 2 a sprocket formed from a plurality of radially displaceable segments 2, which is provided for pulling a link chain 1
  • FIG. 3 a sectional view and a side view of one of the ones shown in FIG. 2 Segments 2, which consists of a guide part 20 and a sprocket 10 slidably mounted therein
  • FIG. 4 shows a sectional view of the guide part 20
  • FIG. 5 shows the sprocket 10
  • FIG. 6 shows the chain drive according to FIG. 1 with tension elements 40 provided for driving the segments 2
  • FIG. 7 shows a sectional view of the chain drive shown in FIG. 6
  • FIG. 8 shows the chain drive according to FIG. 1 with integrated tension elements 40
  • FIG 8 shows a sectional view of the chain drive shown in FIG. 8
  • FIG. 10 shows a chain drive provided with a damping mechanism
  • FIG. 11 shows the damping mechanism according to FIG. 10 in detail
  • FIG. 12 shows a preferred embodiment of the segments 102 shown in FIG. 2, which are arranged in a hollow body 300,
  • FIG. 13 shows the hollow body 300 with a segment 102 mounted radially displaceably therein, and FIG. 14 shows a coupling rod 108 suitable for connecting the segments 102.
  • a chain drive according to the invention connected via a shaft 7 to pedals 5, which has six tooth segments 2 arranged in a circle and intended for pulling a link chain 1, which are arranged between two guide plates 3 and radial in guide tracks 6 provided therein (the term radial means in context, a movement that takes place on a straight, inclined or curved path approximately from the center to the edge of the guide plate; this movement is only preferably carried out precisely along the radius).
  • the link chain 1 is guided over an outer wheel 4, so that preferably never more than half of the toothed segments 2 are in engagement with the link chain 1 in an area eb at the same time.
  • FIG. 2 it can be seen that the radial displacement of the toothed segments 2 makes it possible to set different diameters of the gearwheel formed by the toothed segments 2 (see circle k1, circle k2). It can be seen from FIG. 1 that at the same time a relatively large number of teeth 11 engage in the link chain 1. Furthermore, it can be seen that there are only small distances between the individual tooth segments 2 or their ends, in which the link chain 1 is not supported. The link chain 1 is therefore guided almost along a circular path even when the tooth segments 2 are pushed outwards, as a result of which the torque acting on the shaft 7 remains almost constant. 2 are also preferred in one Design provided rods 8 shown, which are used to mutually couple the toothed segments 2 at a distance that ensures that all teeth 11 of the coupled toothed segments 2 can engage correctly in the link chain 1.
  • Fig. 3 shows a sectional view (see Fig. 3b) and a side view of the toothed segment 2 (see Fig. 3a), which consists of a guide part 20 shown in detail in Fig. 4 and a ring gear 10 shown in detail in Fig. 5, which has six teeth 11, a wing 13 on both sides and a coupling element 14.
  • the ring gear 10 has the two eyelets 15 and 16 shown for fastening a coupling rod 8 and a control lever 9.
  • the guide part 20 has two wing tracks 22 for receiving the ring gear 10, within which the two wings 13 of the ring gear 10 are slidably mounted.
  • the ring gear 10 is held by a one-part or multi-part elastic element or a spring element 24, which is arranged between two stops 23 provided in the guide part 20 and is preferably connected to the coupling element 14 of the ring gear 10 via a connecting element 25.
  • the ring gear 10 can therefore be moved laterally in the guide part 20 until the coupling element 14 abuts one of the stops.
  • the guide part 20 has a guide bar 21 which can be guided in a guide track 6 of the guide plate 3 (to reduce the friction losses, instead of the guide bars 21, guide rollers 6 can also be provided in the guide tracks 6.
  • a Tooth segment 2 is therefore mounted so that it can be displaced radially between the two guide plates 3 by means of the guide strips 21 provided on both sides.
  • the displaceability of the ring gear 10 in the guide part 20 enables the teeth 11 to be synchronized, which is normally required after each radial displacement of the toothed segments 2. If the first tooth 17 of a not yet synchronized sprocket 10 meets a roller of the link chain 1, the sprocket 10 is pushed back or forward until the sprocket 10 is synchronized. Thereafter, the guide part 20 is pushed further until the coupling element 14 strikes the relevant front or rear stop 23, after which the link chain 1 is pulled along by the relevant tooth segment 2.
  • the first tooth 17 (left and / or right) of the ring gear 10 is preferably designed in such a way that it always impinges with a flank on a roller of the link chain 1, after which the ring gear 10 is moved by the roller sliding over the first tooth 17 Link chain 1 moved and thus synchronized.
  • the tooth segments 2 engaging in the link chain 1 are coupled to one another (via the link chain 1).
  • the remaining tooth segments 2 can move freely against one another and compensate for a tooth pitch difference that may arise when the gear ratio changes.
  • the approximately three tooth segments 2, which lie in the looping area eb of the link chain 1, remain radially displaceable.
  • a toothed ring 10 is synchronized before its first tooth 17 engages in the link chain 1.
  • each sprocket 10 is connected on the front via an axis 35 and an eyelet 16 to a control lever 9 projecting through the wing 13, for example, and on the rear via an axis 34 and an eyelet 15 with a coupling rod 8 which is connected to the following tooth segment 2 or protrudes into its guide part 20 and can be fixed by the control lever 9 of the following toothed segment 2.
  • the control lever 9 rotatable about the axis 35, which is depressed by the link chain 1, has a tooth 31 which engages in one of the recesses 32 provided in the coupling rod 8 and which is not yet in engagement with the link chain 1 in the guide part 20 displaceably mounted ring gear 10 moves until the correct tooth division occurs over both tooth segments 2.
  • This synchronization process or the coupling of a toothed segment 2 takes place shortly before engagement in the link chain 1.
  • the control lever 9 provided on the toothed segment 2 continuously scans the distance to the link chain 1 and is depressed by the latter as soon as the toothed segment 2 approaches the link chain 1 .
  • the tooth segments 2 engaging in the link chain 1 are therefore additionally coupled to one another via the coupling rod 8.
  • the remaining tooth segments 2 can in turn move freely against one another and compensate for a tooth pitch difference that may arise when the gear ratio changes.
  • the approximately three tooth segments 2 thus form the effective part of the drive gear. Adjusting the diameter of the gearwheel is possible within certain limits, namely until the coupling element 14 (possibly the connecting element 25) hits the stop 23.
  • the coupling rods 8 are preferably bent, for example in accordance with the central circumference of the drive wheel or the corresponding receiving opening in the guide part 20. This makes it easier to insert the coupling rods 8 into the guide parts 20. Furthermore, the link chain 1 can be supported between the toothed segments 2 by a corresponding bending of the coupling rods 8. In contrast to the gears shown in EP 0 030 992 A1 or EP 0 185 799 A1, the toothed segments 2 are guided on both sides in guide plates 3 and not only by a guide plate and an adjusting disk serving for the radial displacement of the toothed segments 2. Tilting of the toothed segments 2 is thereby avoided.
  • the toothed segments 2 are driven on both sides by tension elements 40 (rigid tension rods, preferably bent around the drive shaft 7, or flexible elements (windable chains, etc.)) which are located inside (see FIGS. 8 and 9). or outside (see FIGS. 6 and 7) of the guide plates 3 and are connected on the one hand to a toothed segment 2 and on the other hand via a one or two-part central part 44 to the drive shaft 7.
  • Screws 43 and 47 are preferably used to create the relevant connections. The screw 47 is screwed, for example, into a thread 26 provided in the guide bar 21. It can be seen from FIGS.
  • each tooth segment 2 is kept free of play due to the spring preload acting on it.
  • the guide plates 3 each have a guide ring 46 on which is rotatably mounted in a sliding seat 45 in the central part 44. If the torque exerted by the link chain 1 via the toothed segments 2, the guide plates 3 and the central part 44 on the drive shaft 7 is greater than an intended target torque, the central part 44 moves relative to the guide plates 3. As can be seen in FIG.
  • the toothed segments 2 are pulled inwards by the pulling elements 40 (see toothed segment 2 ′′ and guide rail 21 ′′ displaced radially inwards) until the torque assumes the intended value. As soon as the pulling force exerted via the link chain 1 diminishes and the torque is reduced accordingly, the toothed segments 2 are pushed further outwards by the spiral springs 41, as a result of which the load torque again assumes the intended value.
  • the coil springs 41 are fastened between the guide plates 3 on a holder 42 and should preferably be able to be preloaded in order to set a desired target torque.
  • the holder 42 is preferably arranged to be displaceable.
  • spring elements 41 with different spring constants can be used.
  • the central part 50 connected to the drive shaft 7 in the chain drive shown in FIGS. 8 and 9 has a ring gear 54 which drives an intermediate ring 52 connected to the tension elements 40 via a plurality of gear wheels 51 connected to the guide plates 3 'via axes 53, which is rotatably mounted within the guide plates 3 '.
  • a sliding seat 56 is also provided between the guide plates 3 'and the central part 50.
  • the adjustment mechanism should preferably not follow rapid changes in the drive torque, which changes between zero and a maximum value on the bicycle with every half a pedal revolution.
  • the drive torque which changes between zero and a maximum value on the bicycle with every half a pedal revolution.
  • this damping mechanism is achieved in that the drive shaft 7, as shown in FIGS. 10 and 11, drives at least one disk 62 connected to a guide plate 3 via an axis 65 via at least two toothed wheels 60, 61, which disk 62 engages in two ways Damping effect unfolds.
  • the driven pulley 62 counteracts all rapid rotations of the drive shaft 7 relative to the guide plates 3 due to its moment of inertia and the gear ratio, so that abrupt radial movements of the toothed segments 2 are avoided.
  • This damping mechanism develops its damping effect especially when the torque fluctuates rapidly.
  • the disks 62 used are preferably provided with one or more slots 66, in which radially displaceable brake bodies 63 outwards up to a friction surface 64, e.g. the inside of a cylinder, are feasible.
  • the second damping effect is therefore based on the principle of the centrifugal governor and only noticeably sets in when the angular velocity of the drive axis 7 relative to the guide plates 3 has reached a certain size.
  • the brake bodies 63 arranged on the disks 62 are pressed outward against the friction surface 64, which counteracts a further increase in the angular velocity of the drive shaft 7 relative to the guide plates 3.
  • a viscous liquid is provided inside the disk 62 instead of the brake body 63, as a result of which a maintenance-free damping mechanism is created.
  • FIG. 12a shows a preferably configured segment 102, which is arranged in a hollow body 300 so as to be radially displaceable and can be connected to adjacent segments 102 via coupling rods 108 (see FIG. 12b).
  • the connection is not, as shown in FIG. 3, by a control lever 9, but by at least one cam 1000 arranged on the wings 113 of the displaceable ring gear 110, which for synchronization of the ring gears 110, preferably between rollers 1081, in recesses 1083 of the coupling rod 108 is introduced.
  • FIG. 14 shows a coupling rod 108 which is preferably configured and which has two plates 1084 each provided with cutouts 1083, by means of which the toothed ring 110 is encompassed such that the cutouts 1083 are arranged above a wing 113 or a cam 1000.
  • the recesses 1083 are preferably delimited by rollers 1081, through which the cam 1000 is guided and held in the recess 1083 in question.
  • the hollow bodies 300 have guide grooves 301 into which the coupling rod 108 or the plates 1084 can be inserted. By means of a radial movement of the segment 102 slidably mounted in the hollow body 300, the ring gear 110 is guided between the plates 1084 and each cam 1000 in a recess 1083 of the coupling rod 108.
  • the segments 102 in turn have a guide part 20 with guide strips 21 which are guided in a groove 305 of the hollow body 300.
  • the hollow body 300 likewise has guide strips 302 which are arranged in the guide tracks 6 of the guide plates 3 so as to be radially displaceable.
  • the hollow bodies 300 (like the segments 2 described in FIG. 3) are pressed outwards by elastic elements 41, for example spiral springs, as a result of which the effective scope of the chain drive changes. Due to the radial displacement of the segment 102, the cam 1000 is inserted into the coupling rod 108 on the one hand and the sprocket 110 is inserted into the link chain 1 on the other hand.
  • the ring gear 102 is therefore first set tangentially (synchronized) and then connected to the link chain 1.
  • Each hollow body 300 is also connected to the drive shaft (7) via a flexible or rigid tension element (40).
  • a rocker arm 400 is provided, which projects into an opening 303 of the hollow body 300 and is held therein with an axis 304.
  • the rocker arm has a lever 401 rotatable about the axis 304, on the ends of which rollers 402 and 403 are arranged.
  • a fixed, e.g. Control disc 200 connected to the vehicle frame is scanned, on which a control segment 201 is arranged at least in one sector, by means of which the rotating rocker arm 400 is tilted within an angular range 202 and segment 102 is raised. As shown in FIG.
  • 3 slots 203 are provided in the guide plate, from each of which a lever 401 with the roller 402 is guided out to the control disk 200.
  • the rocker arm 400 is preferably also guided through the guide slot 6.
  • the control disk 200 or the control segment 201 is preferably configured such that only one rocker arm 400 is actuated in each case and thus only one sprocket 110 is in engagement with the link chain 1.
  • an elastic element 306 (only one possible position is shown) is provided in the hollow body 300, by means of which the segment 102 is pressed radially inward (if necessary pulled). This also ensures that the sprocket 110 is only in engagement with the link chain 1 if this is provided by the control disk 200.

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  • Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Transportation (AREA)
  • Mechanical Engineering (AREA)
  • Transmissions By Endless Flexible Members (AREA)
  • Devices For Conveying Motion By Means Of Endless Flexible Members (AREA)

Abstract

L'entraînement par chaîne comprend des secteurs dentés (2) formant une roue dentée variable et prévus pour exercer une traction sur une chaîne articulée (1), ces secteurs étant logés mobiles radialement dans des coulisses (6) d'au moins un plateau de guidage (3) et étant reliés, via au moins un élément de traction flexible ou rigide (40), à un arbre d'entraînement (7). A une rotation de l'arbre d'entraînement (7) par rapport au plateau de guidage (3), provoquant une variation automatique et continue du rapport de transmission ou une modification de la position radiale des secteurs dentés (2), s'oppose au moins un premier élément élastique (41). L'entraînement par chaîne selon l'invention est caractérisé en ce que les secteurs dentés (2) présentent un élément de guidage (20), ainsi qu'une couronne dentée (10) montée mobile à l'intérieur de cet élément, tangentiellement à la roue dentée variable, et maintenue entre deux butées (23) par au moins un deuxième élément élastique (24), permettant ainsi la synchronisation avec la chaîne articulée (1). L'entraînement par chaîne permet d'adapter automatiquement et en continu le rapport de transmission au couple de rotation disponible, tout en garantissant l'engagement synchronisé de chaque couronne dentée (10) dans la chaîne articulée.
PCT/CH1997/000445 1996-11-28 1997-11-27 Entrainement par chaine a rapport de transmission variable WO1998023481A1 (fr)

Priority Applications (1)

Application Number Priority Date Filing Date Title
EP97913070A EP0877700A1 (fr) 1996-11-28 1997-11-27 Entrainement par chaine a rapport de transmission variable

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
CH2927/96 1996-11-28
CH292796 1996-11-28

Publications (1)

Publication Number Publication Date
WO1998023481A1 true WO1998023481A1 (fr) 1998-06-04

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Family Applications (1)

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PCT/CH1997/000445 WO1998023481A1 (fr) 1996-11-28 1997-11-27 Entrainement par chaine a rapport de transmission variable

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EP (1) EP0877700A1 (fr)
WO (1) WO1998023481A1 (fr)

Cited By (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB2363831A (en) * 2000-06-24 2002-01-09 Nigel Stephen Woodford A drive transmission device
WO2003076260A1 (fr) * 2002-03-12 2003-09-18 Alain Bernard Systeme de transmission comprenant des engrenages a reglage radial
FR2850437A1 (fr) * 2003-01-28 2004-07-30 Pascal Andre Octave Jarry Procede de variation de rapport en continu dans une transmission par element flexible sans fin, et dispositif de mise en oeuvre
WO2012145824A1 (fr) 2011-04-26 2012-11-01 1783590 Ontario Ltd. D/B/A Inmotive Éléments de segment de poulie clé, configuration d'empilement de segments et conception de came et de galet et actionnement dans un système de transmission de poulie d'échange par segment synchronisé
CN102803359A (zh) * 2010-03-18 2012-11-28 吉列公司 具有金属化和全息效应的制品
ITUB20154124A1 (it) * 2015-10-02 2017-04-02 Yves Joseph Alfred Morin Trasmissione a catena, particolarmente per biciclette, con variazione continua del rapporto di trasmissione.

Families Citing this family (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US6632597B2 (en) 2000-09-05 2003-10-14 Fuji Photo Film Co., Ltd. Methine dye and silver halide photographic material containing the same

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Publication number Priority date Publication date Assignee Title
US3867851A (en) * 1973-08-23 1975-02-25 Hagen Int Inc Radially expansible sprocket with rotatable teeth segments
EP0030992A1 (fr) 1979-12-21 1981-07-01 Johann Ecker Elément d'engrenage
EP0116731A1 (fr) 1983-02-09 1984-08-29 FULLERTON, Robert L. Transmission automatique à variation continue
GB2135743A (en) * 1979-10-29 1984-09-05 Michel Deal Variable diameter transmission wheel
EP0185799A1 (fr) 1984-12-28 1986-07-02 Dürkopp System Technik Gmbh Transmission automatique
DE3932342A1 (de) * 1989-09-28 1991-04-11 Otto Lingner Stufenlos regelbares kettenrad
WO1994004411A1 (fr) * 1992-08-21 1994-03-03 Baechtiger Rolf Engrenage a chaine a rapport de transmission variable et a chaine dentee
DE4322382A1 (de) * 1993-06-29 1995-01-12 Jaroslaw Piotr Warszewski Stufenlos selbsttätig verstellbarer Fahrradantrieb

Patent Citations (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3867851A (en) * 1973-08-23 1975-02-25 Hagen Int Inc Radially expansible sprocket with rotatable teeth segments
GB2135743A (en) * 1979-10-29 1984-09-05 Michel Deal Variable diameter transmission wheel
EP0030992A1 (fr) 1979-12-21 1981-07-01 Johann Ecker Elément d'engrenage
EP0116731A1 (fr) 1983-02-09 1984-08-29 FULLERTON, Robert L. Transmission automatique à variation continue
EP0185799A1 (fr) 1984-12-28 1986-07-02 Dürkopp System Technik Gmbh Transmission automatique
DE3932342A1 (de) * 1989-09-28 1991-04-11 Otto Lingner Stufenlos regelbares kettenrad
WO1994004411A1 (fr) * 1992-08-21 1994-03-03 Baechtiger Rolf Engrenage a chaine a rapport de transmission variable et a chaine dentee
DE4322382A1 (de) * 1993-06-29 1995-01-12 Jaroslaw Piotr Warszewski Stufenlos selbsttätig verstellbarer Fahrradantrieb

Cited By (14)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB2363831A (en) * 2000-06-24 2002-01-09 Nigel Stephen Woodford A drive transmission device
WO2003076260A1 (fr) * 2002-03-12 2003-09-18 Alain Bernard Systeme de transmission comprenant des engrenages a reglage radial
FR2850437A1 (fr) * 2003-01-28 2004-07-30 Pascal Andre Octave Jarry Procede de variation de rapport en continu dans une transmission par element flexible sans fin, et dispositif de mise en oeuvre
CN102803359A (zh) * 2010-03-18 2012-11-28 吉列公司 具有金属化和全息效应的制品
JP2014513254A (ja) * 2011-04-26 2014-05-29 １７８３５９０ オンタリオ リミテッド ディー／ビー／エイ インモーティヴ 同期式のセグメント交換型プーリ伝動システム内のキープーリセグメント機能、セグメント積層体構造、ならびにカムおよびローラの設計および作動
KR20140051852A (ko) * 2011-04-26 2014-05-02 1783590 온타리오 엘티디. 디/비/에이 인모티브 키 풀리 세그먼트 구성요소，세그먼트 스택 구성，및 동기화된 세그먼트식 교환 풀리 트랜스미션 시스템에서의 캠과 롤러 설계 및 작동 방법
WO2012145824A1 (fr) 2011-04-26 2012-11-01 1783590 Ontario Ltd. D/B/A Inmotive Éléments de segment de poulie clé, configuration d'empilement de segments et conception de came et de galet et actionnement dans un système de transmission de poulie d'échange par segment synchronisé
EP2702300A4 (fr) * 2011-04-26 2015-08-05 1783590 Ontario Ltd D B A Inmotive Éléments de segment de poulie clé, configuration d'empilement de segments et conception de came et de galet et actionnement dans un système de transmission de poulie d'échange par segment synchronisé
AU2012248069B2 (en) * 2011-04-26 2017-04-20 1783590 Ontario Ltd. D/B/A Inmotive Key pulley segment features, segment stack configuration, and cam and roller design and actuation in a synchronized segmentally interchanging pulley transmission system
US9816598B2 (en) 2011-04-26 2017-11-14 Inmotive Inc. Key pulley segment features, segment stack configuration, and cam and roller design and actuation in a synchronized segmentally interchanging pulley transmission system
KR102091717B1 (ko) * 2011-04-26 2020-03-23 1783590 온타리오 엘티디. 디/비/에이 인모티브 키 풀리 세그먼트 구성요소，세그먼트 스택 구성，및 동기화된 세그먼트식 교환 풀리 트랜스미션 시스템에서의 캠과 롤러 설계 및 작동 방법
ITUB20154124A1 (it) * 2015-10-02 2017-04-02 Yves Joseph Alfred Morin Trasmissione a catena, particolarmente per biciclette, con variazione continua del rapporto di trasmissione.
WO2017056076A1 (fr) * 2015-10-02 2017-04-06 Morin Yves Joseph Alfred Transmission par chaîne, en particulier pour bicyclettes, avec rapport de transmission à variation continue
US10766567B2 (en) 2015-10-02 2020-09-08 Yves Joseph Alfred MORIN Chain transmission, particularly for bicycles, with continuously variable transmission ratio

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