WO1989012187A1 - Entrainement a vitesse/rapport d'engrenage variables - Google Patents

Entrainement a vitesse/rapport d'engrenage variables Download PDF

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Publication number
WO1989012187A1
WO1989012187A1 PCT/US1988/002004 US8802004W WO8912187A1 WO 1989012187 A1 WO1989012187 A1 WO 1989012187A1 US 8802004 W US8802004 W US 8802004W WO 8912187 A1 WO8912187 A1 WO 8912187A1
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WO
WIPO (PCT)
Prior art keywords
gear
race
segments
transmission
power
Prior art date
Application number
PCT/US1988/002004
Other languages
English (en)
Inventor
Harold L. Walker
Original Assignee
Walker Harold L
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 Walker Harold L filed Critical Walker Harold L
Priority to PCT/US1988/002004 priority Critical patent/WO1989012187A1/fr
Publication of WO1989012187A1 publication Critical patent/WO1989012187A1/fr

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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
    • F16H29/00—Gearings for conveying rotary motion with intermittently-driving members, e.g. with freewheel action
    • F16H29/12—Gearings for conveying rotary motion with intermittently-driving members, e.g. with freewheel action between rotary driving and driven members
    • F16H29/16—Gearings for conveying rotary motion with intermittently-driving members, e.g. with freewheel action between rotary driving and driven members in which the transmission ratio is changed by adjustment of the distance between the axes of the rotary members
    • F16H29/18—Gearings for conveying rotary motion with intermittently-driving members, e.g. with freewheel action between rotary driving and driven members in which the transmission ratio is changed by adjustment of the distance between the axes of the rotary members in which the intermittently-driving members slide along approximately radial guides while rotating with one of the rotary members
    • 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

  • This invention relates generally to drive transmissions and more particularly to infinitely variable drive transmis ⁇ sions, useful in chain/pulley and direct drive applications.
  • Transmission mechanisms which are movable relative to a power shaft to increase and decrease, the radius of an arcuate ' power stroke delivered to a driven member are typified by the structures disclosed in U.S. Patents 4,219,044 to Erickson et al and U.S. 4,164,153 to Moritsch et al.
  • Typical gear change mechanisms which utilize rota- tionally associated inner and outer drive and driven members can be seen in the just noted patent to Moritsch et al and in U.S. 3,081,641 to Iseman.
  • a number of devices which include a chain wheel and a pedal crank shaft having toothed ratchet mechanisms inter ⁇ posed therebetween are disclosed in those patents classified in Class 180, subclasses 230, 231; Class 280, subclasses 236, 238, 251, 259, 260, 261, 262 and 431; Class 284, subclasses 431 and Class 474, subclasses 55, 69 and 70 and Class 74, subclasses 190, 190.5, 194, 393 and 810.
  • the objects of the present invention in variable ratio transmissions are the provision of automatic gear pitch control throughout the full range capacity of the transmis ⁇ sion, infinitely variable ratio, automatic shift to both higher and lower ratios, optional manual shift, shifting under torque, higher efficiency : .in the most used ratios, torque sensitive power shifting and shifting in non-oper ⁇ ating mode, as well as under torque, high ratio transmis ⁇ sion, and locking into gear or ratio of choice , .
  • the present invention provides such a transmission which may be enclosed for dirt-free operation, is light-weight and requires minimal maintenance.
  • an output drive assembly comprising a circular gear member having a cir-cumferentially toothed gear surface, a circular gear segment race having a circumferential race surface radially spaced from and juxtaopposed to the gear surface, the gear member and race being integral and having a common axis, an inner bearing about which the gear member and integral race rotate and are supported, a plurality of gear segments mounted between the gear surface and race surface for rotation on the race, with spring means for slightly biasing 1 them radially for retaining the gear segment assemblies o the race with the teeth of the segments spaced from the teeth of the gear surface, a gear segment cam pivotal] y mounted on the bearing, and a control arm secured to the c bearing and which restrains the bearing against rotation, other than rotation imparted to it by the control arm and which may be used for manual positioning of the output drive assembly.
  • An axial extension of the bearing is disposed within parallel preferably arcuate guide surfaces of a
  • the plurality of gear segments each having a multi ⁇ plicity of teeth engage the teeth of the circumferential gear member through a power arc of their rotational strokes, the circumferential extent of the arc being determined by the position of the cam and of the gear segment relative to the axis of a drive shaft.
  • the output drive assembly is movable relative to and in a plane normal to the axis of the drive shaft ⁇ to increase and decrease the radius of the power arc and is driven about its bearing by the power shaft through a power disc which is connected to the shaft and provides radial slots which guide the gear segments radially as the output drive assembly is moved. As the power disc rotates, it delivers rotational power to the gear segments and thus to the output drive assembly.
  • the output drive assembly is guided by the guide member so that its center is offset from the axis of the drive shaft when in the lower ratio mode; i.e., when the radius of the power arc stroke, from drive shaft axis to gear segment, i short, to effect a slightly longer radius at the end of the power arc for quick disengagement of the gear segment at the end of its power stroke as the next segment engages the gear surface of the output drive member under torque.
  • the output assembly is moved in a slight arc, via the arcuate surfaces of the independently mounted guide member, away from the power shaft axis as lower transmission ratios are approached.
  • this arc conveniently, may be defined by curving the guide along an arc with a radius extending from the rear axle of the bicycle to retain chain tension.
  • the bearing of the output drive assembly is rotatable via the control arm to position the gear segment cam and, therefore, the engagement of the segments with the circumferential gear at points before and after a neutral plane extending normal and parallel to the axis of the power output assembly.
  • cam positioning or re ⁇ positioning is eliminated where automatic gear ratio change from high to low is not desired.
  • the cam is mounted for rotational positioning independently of the bearing so that automatic gear ratio change or pitch control (the change in the extent of the power arc) is effected independently of the movement of a control arm and may be used in combination with a control arm where manual movement of the power output drive assembly and automatic pitch control are both desired.
  • the output drive assembly is automatically moved to increase the radius of the power stroke by the rotating gear segments in response to the torque effected on the power disc through the shaft.
  • control arm or equivalent control mechanism may be used to hold the output drive assembly locked in any position relative to te drive shaft and may also be used to manually move the output drive assembly to increase or
  • control arm and thus the power output drive assembly may be biased when the assembly is moved through the mid to low gear ratio positions, particularly when the output drive assembly is mounted for vertical movement, to restrain the assembly against gravita ⁇ tional forces.
  • the control arm may also be biased throughout the low to mid and mid to high gear ratio positions to assist movement of the assembly in the low to mid range and to restrain movement in the mid to high range.
  • a spring operable only in the mid to low range operates between the control arm and the frame of a bicycle or machine;, in another, the control arm itself is an extended bar spring and operates to shift; i.e., move the assembly, and bias it at the same time.
  • the output drive assembly is not movable relative to and in a plane normal to the axis of the drive shaft, but rather is mounted directly to the frame or housing on or in which the transmission is used.
  • the cam is mounted to provide a wide arc through which it may be positioned and through which the gear segments may engage and then disengage the circumferential gear member, thus increasing or decreasing the power stroke as the segments are introduced to the circumferential gear farther away or closer to the axis of the power shaft.
  • the cam may be mounted on a link the terminus of which is at the center or axis of the integral race and circumferential gear with a link connecting the terminus of the cam for rotating it from outside the assembly.
  • the cam should either be spring biased toward the circumferential gear or to comprise a spring as well as a camming surface so that the gear segments do not "slam" into the teeth of the circumferential gear with resulting wear or even malfunc ⁇ tioning.
  • the structure may be used both around the pedal crank and at the hub of the rear or driven wheel where it may be fitted, as may the assembly about the pedal crank, for substitution for present day multiple sprocket and derailleur mechanisms.
  • the cam may ?e, particu ⁇ larly in industrial applications, activated via hydraulic or electromagnetic means.
  • the basic output drive assembly and power disc can be ganged with one, two or more further output drive assemblies and power discs in the construction of a relatively small and efficient transmission.
  • Fig. 1 is a diagramatic side elevational view showing the transmission of the invention as applied to a bicycle;
  • Fig. 2 is a diagrammatic end view of the transmission of Fig. 1 taken along the lines 2-2 of Fig. 1;
  • Fig. 3 is a diagrammatic end view, partially in section, of the transmission of Figs. 1 and 2 showing some details of construction;
  • Figs. 4 and 4A are diagrammatic front and side views of the upper portions of the control arm of the transmission of Figs. 1-3;
  • Fig. 5 is a diagrammatic front view of a gear segment race bearing and separately rotatable gear segment cam
  • Fig. 6 is a diagrammatic front view of a cam race bearing and spring rod control arm of a modification of the invention.
  • Fig. 7 is a diagrammatic side view of a power train employing the transmission of the invention in a machine in which the power output assembly connects a direct output drive shaft, rather than a sprocketed wheel driving a chain;
  • Fig. 8 is a schematic side elevational view showing a modified form of the invention in which the output assembly is stabilized
  • Fig. 9 is a schematic side elevational view of another modified form of the invention as applied to the rear or driven wheel of a bicycle;
  • Fig. 10 is a schematic end view of the transmission of Fig. 9;
  • Fig. 11 is a schematic diagram showing the location of the pins which extend actually from the gear segments when 1 angled slots are used in the power disc;
  • Fig. 12 is a schematic " side elevational view of the output assembly showing the position of ' fluid and electro- magnetic cam drive elements;
  • Fig. 13 is a schematic end view of the transmission used in an industrial application and showing too the transmission assemblies ganged for effecting transmission 0 ratio changes in a gear box;
  • Fig. 14 is a schematic side elevational view of the transmission of Fig. 13;
  • Fig. 15 is a schematic elevational view of a combined transmission and differential embodying the transmission of the invention and showing a pair of ganged assemblies of the invention.
  • the transmission depicted in Figs. 1-3 is a bicycle transmission, however, the mechanical principles and struc ⁇ tures are applicable to transmissions for use in any _,_ machinery drive where variable output speeds are desirable.
  • bolts 15 secure guide member 16 to bicycle frame F via guide ears 17.
  • the output drive assembly is a driven chain wheel
  • An inner circumferential surface of sprocketed outer ring 22 is toothed as at 22A to mesh with the corresponding multiplicity of teeth of gear segments 30 which drive the sproketed outer ring 22 and integral gear segment race 23 about gear segment race bearing 25, in the direction of the arrows in Fig. 1, via rotation of a driven slotted driving disc 40 keyed or otherwise secured to drive shaft 42 of pedal drive 41.
  • the bearing 25 is annular in this instance to accommodate shaft 42. It has been found that a minimum of four gear segments are required for smooth operation and more than four are preferable; e.g., six, eight, ten, twelve gear segments, etc. It has been determined that the extended circumferential length of the gear segments including a plurality of teeth provides smooth engagement of the gear segments with the teeth of ring 22 with slippage minimized or eliminated.
  • the assembly 20 also includes control arm 45 secured at its lower end to gear segment race bearing 25; its upper end slidabiy received in a frame member F, and which restrains rotation of the bearing 25 and is used to effect clockwise and counter-clockwise movement of the gear segment race bearing 25, within guide element 16, and resultingly of gear segment cam 46, also a part of assembly 20, pivoted to the gear segment race bearing 25 at 47 to present upper cam surface 48 and gear segment assembly 30 at positions between fore and aft of a central plane normal and parallel to and passing through the axis A of driven chain assembly 20.
  • the axis A is moved with the assembly to above and below the 2 axis A of the drive shaft 42, and is positioned by guide element 16, offset to the left and below the axis of the drive shaft 42 when lowered to decrease the radius of the power arc between the shaft axis and the gear segments in the lower speed or ratio modes.
  • the radius of the power arc is longer when the gear segment approaches the end of cam surface 48 and the gear segment is released from torque and off the cam and out of engagement with the Inner teeth of the sprocketed outer ring just as soon as the next gear segment is engaged with the Inner teeth of the sprocketed outer ring to take up the torque transmitted from the drive shaft.
  • cam 46 is secured to one end of spring 46A, the other end of spring 46A being secured to gear seg ⁇ ment race bearing 25 to bias cam surface 48 upwardly about pivot 47.
  • a stop member 49 restrains radial inward movement of the lower end of cam 46 against 'the bias of spring 46A and accurately disposes the cam surface 48 for engagement of the gear segment body 30A for meshing of the inner teeth of sprocketed outer ring 22 and the teeth 33 of gear segments 30.
  • the gear segment shields 31, 31' which may be integral with gear segment body 30A, are disposed along the sides of the segments 30 In the front and to the rear of gear segment race 23 and outer sprocket ring 22 to retain the gear segment assemblies, when not meshed with the teeth of ring 22, in their circumferential path of travel between the outer surface 23A of gear segment race 23 and toothed inner surface 22A of sprocketed outer ring 22.
  • the gear segment drive pins 36 which extend axially through the slots 50 of slotted driving disc 40 are secured to the gear segments in any conventional manner, as by swaged ends of pin 37 (Fig. 3) about which the gear segment, including the drive pin, may be rotatable.
  • a spring 60 bands around the collars 61 on each drive pin 36 to retain the gear segments on the gear segment race. Only slight spring pressure is required for this purpose and any equivilant restraining structure may be used for the same purpose.
  • a cover CF shown partially in phantom in Fig. 3 may enclose the front of the drive disc thus shielding the gear segment assemblies and the power output assembly from dust.
  • an annular rear plate RP shown partially in phantom in Fig. 3, may be substituted for the weld bars 24 to provide dust cover protection to the assembly from the rear side.
  • control arm may be stopped at any desired position of the output drive assembly by interengaging groove detent elements 100 on the arm 45, and tooth elements 101 on the frame.
  • a turnbuckle 72 is provided permitting rotation of the upper portion of arm 45 about its axis.
  • a manually controlled transmission of the invention is disclosed and in which the control arm 245 is an extended bar spring.
  • One end of the spring arm is secured to the end of a turn shaft 246 rotatable by movement of the upper end of lever 247 from and to positions P, along an arcuate stopper/indicator where it may be temporarilv secured in a well known manner.
  • the bar spring control arm which is connected to an extension 325A from the race bearing 325, the bearing 325 and thus the whole power output assembly (not shown) will be lifted or lowered.
  • the cam (not shown) may be secured to the assembly and not movable relative to the race: or it may be mounted for movement fore and aft of the neutral plane as in Fig. 5 for automatic transmission variation upon shifting the lever away from stops at the position P.
  • the cam may be positioned and secured for either automatic gear change from low to high or from high to low; or between mid and low or mid and high ratios.
  • the bearing extension 325A may be cocked from the vertical thus tilting the bearing and cam to set the beginning and end of the power arc as desired and to effect increasing of the radius of the power arc in the higher ratio of transmission as discussed, supra.
  • the bias in the spring bar control arm may be upward to restrain against gravity forces exerted on the assembly when moving downwardly through the high to low gear ratio positions and to assist lifting of the assembly moving upwardly in the low to high gear positions; or so that spring exertion is imparted only in the mid to low or in the mid to high positions of the assembly.
  • the bias of the spring bar may be downward for effecting quick down-gearing from mid-cam-position, for example, with lever 247 dis ⁇ associated from the stops P.
  • extension 325A of race bearing 325 may be used as an alternate position retention element by providing detent slots along its side (phantom lines in Fig. 6) for mating with a toothed stopper movable into and out of the detent teeth along the path of travel of the assemblv.
  • the invention is disclosed in an industrial application in which the drive disc is driven by a drive shaft and, in turn, drives the power output assembly through the gear segment pins.
  • the output assembly directly connects the output shaft which, together with the assembly, is moved to increase or decrease the radius of the power stroke of each gear segment.
  • the circumferentially toothed surface faces radially outwardly from the outer surface of a central cylindrical member and the gear segment race is positioned on the inner circumfere tial surface of the outer ring previously described as the output drive member. Springing the segments radially will * not be necessary in this construction, as centrifugal force in the rotating output assembly will retain the segments on the race until cammed to mesh with the teeth of the central members.
  • the central member and the gear segment race are inte ⁇ gral, as in one previously described embodiment.
  • the position of the gear segments has been changed so that the cam may be operated, if desired, from outside the transmission, mounted, for example, on the bearing of the output shaft of the transmission.
  • the output shaft is connected through conventional joints to a stationary driven work shaft.
  • the structures of the invention lend themselves to hydraulic activation and actuation within lubricated enclosures and to activation via electro-magnets which should prove very efficient.
  • the gear segments which are only shown schematically as gear segment rollers 336, are disposed between the outer ring guide or race 333 and externally toothed circumferential gear 322 which is integral with the race 333 and journaled on inner ring guide or bearing 325.
  • the cam 346 is mounted, via means not shown, along an arc at the top of the assembly above the ' path of the gear segments 336.
  • the segments are being rotated by the power disc, not shown, at a speed sufficient for centrifugal force to keep them on . the outer ring guide 333.
  • the action of the cam positions the segments inwardly onto the external teeth of the gear ring 322 either by the action of the electro ⁇ magnets 350 positioned within the cam and actuated by power source 351; or by the action of fluid jets actuated through' holes 355 in the cam via conduit 356 from pump 357 which circulates fluid from reservoir 359 in transmission casing 358 via pump 357.
  • the power disc may be movable to increase the radii of the power arc through which the segments move; or the assembly itself may be movable relative to the power disc, as shall be more 1 specifically discussed with reference to Figs. 13 et seq.
  • the transmission of the invention again takes the form of a bicycle transmission in which the pedal 5 crank shaft 442 powers the power disc 440, the slots of which are shown diagrammicaily at lines 450, which, In turn, powers the assembly through the segments shown as segment rollers 436 and which are disposed between internally toothed ring gear 422 and segment race, not shown, the gear 0 422 and race being supported for rotation on ring gear and race bearing 425, which, in this instance, is supported by a plate 425A secured to the frame of a bicycle by any conventional means not shown. Toothed ring gear 422 is sprocketed (not shown) to accommodate bicycle chain CH. 5
  • the axis of the power output assembly is offset to the rear- or left of the axis of the pedal crank shaft 442 and there is provided at the axis a link extending radially to support at its end a cam 20 comprised of a leaf spring 446.
  • the circumferential dis ⁇ placement of the cam is effected by a link 447 operable by any conventional connection, such as a cable, by the operato /cyclis .
  • the extent of the arc of travel of the spring cam 446 is extensive as the power output assembly is not movable and the cam may, therefore, be set to effect meshing of the gear segments and gears of the ring gear 422 at positions along the arc to have the y ⁇ Q radii of the power arc of the gear segments increase and decrease as desired.
  • Figs. 9 and 10 the transmission of the Invention is shown as it may be applied to the rear or driven wheel of a bicycle and may conveniently replace the deraileur of the prior art which Is no longer necessary with 35 the single chain sprocket transmission of the present invention.
  • the rear sprocket 500 receives rotational power from the chain (not shown) coming from the sprocket wheel on the pedal crank, also not shown, in Figs. 9 and 10.
  • the sprocket wheel 500 is an axial extension of the gear segment race, not shown, and which, with the sprocket wheel 500, rotates on bearing 501 as does internally toothed gear ring, also not shown, which is integral with the race as in the constructions previously discussed.
  • the power assembly is shown in Figs. 9 and 10 as box 502 and from which extend the rollers of the gear segments 503 which drive the power disc 504 via the edges of the slots 505 in the power disc.
  • the power disc is the power output element in this construction while the power input element is the assembly, just the reverse of the constructions discussed above.
  • a spring cam similar to that described with relation to Fig. 8 is disposed at the end of a radially extending bar or link, secured to the center of the power assembly and to the frame 550 of the bicycle -which also supports the bearing on which the chain sprocket 500 and segment race and circumferential gear rotate.
  • the cam 506 is moved via the link and extended portion thereof 507 via any convenient means such as a cable wire by the operator/cyclist whereby the cam is rotated through an arc such as to dispose the gear segments 503 to mesh with the teeth of the circumferential gear along radii which increase or decrease with the positioning of the cam.
  • the power disc is thus driven and consequently drives the rear wheel through the rear wheel shaft 510 on which the power disc is secured via internally threaded bore 560, fitted to replace the deraileur of the prior art
  • the radial sloes 600 of the power disc 601 may be angled from strictly radial lines and rearwardly (from the axis to the periphery) with relation to the rotational direction of travel.
  • the gear segments shown in Fig. 11 as gear segment rollers 604
  • the gear segments 604 ride on the cam 605 and in a closer grouping such that pulsing is very much minimized.
  • Figs. 13 and 14 disclose the transmission of the invention enclosed within a housing 700 in which there is an oil reservoir 701 as discussed with relation to the con ⁇ struction shown in Fig. 12.
  • a support 702 receives a central shaft 703 in a bearing
  • the shaft 703 is secured at one end to the driven output drive assembly 704 of a first transmission in which the output assembly 704 is driven via the pins 705 of the gear segments via the power disc 706 which, In turn, is rotated by the input shaft 707.
  • the shaft 703 connects at its other end the power disc 706A of the second transmission in the housing 700.
  • the power disc 706A powers the pins 705A of the gear segments in the output drive assembly
  • the shaft 704A of the second transmission to which, along the common axis of toothed gear and segment race is secured the output shaft 707 of the transmission.
  • the shaft 703 connecting the output drive assembly of the first transmission to the power disc of the second transmission is movable upwardly and downwardly in slot 710 of support assembly 702.
  • a control arm 710 is provided to lift and lower the shaft 703 and the transmissions to which the ends of the shaft are secured.
  • Cams 711 and 712 are positioned, respectively, above and below the gear segments which mesh, respectively, downwardly and upwardly in the instance of this construction to an excernally toothed gear.
  • control arm could also control the position of the cam clockwise and counterclockwise to effect meshing of the gear segments and circumferential gear along increased and decreased radii dependant upon the relative position of the meshing gear segments and the axis of the input shaft secured to the power disc of thefirst transmission and the relative position of the meshing segments and shaft 703 secured to the power disc 706A of the second transmission.
  • the radii defining the power arc of the first transmission assembly decreases as does the radii and power arc of the second transmission.
  • the output shaft 707A ' of the transmission of Figs. 13 and 14 may be used as in input shaft of yet another double transmission transmission, and so on, such a transmission construction resulting in a relatively small and very efficient transmission.
  • control arm could actually control the position of the cam rather than lifting or lowering the transmissions to effect positioning the meshing of the segments and circumferential gear.
  • a transmission and differen ⁇ tial case 800 in which an input shaft 801 delivers rota ⁇ tional power to transmission assembly 802, the output shaft 803 of which delivers transmission power to transmission assembly 804, the output shaft 805 of which through a universal joint delivers the transmission power for forward or reverse movement of a vehicle, the wheels (not shown) of which are secured to the ends of axles 807, 808.
  • the power being transmitted to either reverse crown gear or forward crown gear 809, 810, through pinion gear 811 secured to the end of shaft 812 from universal joint 813.
  • the transmission and differential case of Fig. 15 is considered to be an excellent layout for a transmission and differential case of a power lawnmower.

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  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Transportation (AREA)
  • Transmission Devices (AREA)

Abstract

Dans la transmission décrite, des segments d'engrenage (30) sont pourvus de dents pour pouvoir se placer en prise avec un engrenage circonférentiel (22, 22A) et pour transmettre une force d'entraînement depuis un arbre centré (42) le long d'arcs de force déterminés par la position des segments (30) par rapport à l'arbre (42). Les segments (30) effectuent automatiquement le réglage des rayons allant de l'arbre (42) au segment (30) en réaction au couple transmis depuis l'arbre (42).
PCT/US1988/002004 1988-06-10 1988-06-10 Entrainement a vitesse/rapport d'engrenage variables WO1989012187A1 (fr)

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PCT/US1988/002004 WO1989012187A1 (fr) 1988-06-10 1988-06-10 Entrainement a vitesse/rapport d'engrenage variables

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PCT/US1988/002004 WO1989012187A1 (fr) 1988-06-10 1988-06-10 Entrainement a vitesse/rapport d'engrenage variables

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Cited By (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
FR2731672A1 (fr) * 1995-03-16 1996-09-20 Martin Denis Marie Daniel Variateur automatique de rapport de transmission pour bicyclette
GB2312259A (en) * 1996-04-16 1997-10-22 John James Jago Steplessly-variable ratchet gearing for a chain drive
WO2005050064A1 (fr) * 2003-11-18 2005-06-02 Mark Parry Owen Variateur mecanique de vitesse a serrage bidirectionnel actionne
CN112879526A (zh) * 2021-01-14 2021-06-01 江苏信息职业技术学院 一种用于机械设备的异形齿轮

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GB189523423A (en) * 1895-12-06 1896-07-25 Ernest Samuel Spencer Improvements in or connected with Crank Mechanism for Driving Velocipedes.
US2035478A (en) * 1932-07-20 1936-03-31 Houdry Process Corp Production of motor fuel
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Cited By (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
FR2731672A1 (fr) * 1995-03-16 1996-09-20 Martin Denis Marie Daniel Variateur automatique de rapport de transmission pour bicyclette
GB2312259A (en) * 1996-04-16 1997-10-22 John James Jago Steplessly-variable ratchet gearing for a chain drive
WO2005050064A1 (fr) * 2003-11-18 2005-06-02 Mark Parry Owen Variateur mecanique de vitesse a serrage bidirectionnel actionne
CN112879526A (zh) * 2021-01-14 2021-06-01 江苏信息职业技术学院 一种用于机械设备的异形齿轮
CN112879526B (zh) * 2021-01-14 2022-02-15 江苏信息职业技术学院 一种用于机械设备的异形齿轮

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