WO1998045621A1 - Systeme de transmission en ligne et moyeu de roue a plusieurs rapports dans un dispositif d'entrainement helicoidal - Google Patents

Systeme de transmission en ligne et moyeu de roue a plusieurs rapports dans un dispositif d'entrainement helicoidal Download PDF

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Publication number
WO1998045621A1
WO1998045621A1 PCT/IB1998/000598 IB9800598W WO9845621A1 WO 1998045621 A1 WO1998045621 A1 WO 1998045621A1 IB 9800598 W IB9800598 W IB 9800598W WO 9845621 A1 WO9845621 A1 WO 9845621A1
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WO
WIPO (PCT)
Prior art keywords
gear
assembly
input
orbital
rotation
Prior art date
Application number
PCT/IB1998/000598
Other languages
English (en)
Inventor
Mighel Doroftei
Original Assignee
Helical Dynamics International Inc.
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 Helical Dynamics International Inc. filed Critical Helical Dynamics International Inc.
Priority to AU67428/98A priority Critical patent/AU6742898A/en
Publication of WO1998045621A1 publication Critical patent/WO1998045621A1/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
    • B62M1/00—Rider propulsion of wheeled vehicles
    • B62M1/24—Rider propulsion of wheeled vehicles with reciprocating levers, e.g. foot levers
    • A—HUMAN NECESSITIES
    • A01—AGRICULTURE; FORESTRY; ANIMAL HUSBANDRY; HUNTING; TRAPPING; FISHING
    • A01K—ANIMAL HUSBANDRY; AVICULTURE; APICULTURE; PISCICULTURE; FISHING; REARING OR BREEDING ANIMALS, NOT OTHERWISE PROVIDED FOR; NEW BREEDS OF ANIMALS
    • A01K89/00—Reels
    • A01K89/015—Reels with a rotary drum, i.e. with a rotating spool
    • A—HUMAN NECESSITIES
    • A61—MEDICAL OR VETERINARY SCIENCE; HYGIENE
    • A61G—TRANSPORT, PERSONAL CONVEYANCES, OR ACCOMMODATION SPECIALLY ADAPTED FOR PATIENTS OR DISABLED PERSONS; OPERATING TABLES OR CHAIRS; CHAIRS FOR DENTISTRY; FUNERAL DEVICES
    • A61G5/00—Chairs or personal conveyances specially adapted for patients or disabled persons, e.g. wheelchairs
    • A61G5/02—Chairs or personal conveyances specially adapted for patients or disabled persons, e.g. wheelchairs propelled by the patient or disabled person
    • A—HUMAN NECESSITIES
    • A63—SPORTS; GAMES; AMUSEMENTS
    • A63B—APPARATUS FOR PHYSICAL TRAINING, GYMNASTICS, SWIMMING, CLIMBING, OR FENCING; BALL GAMES; TRAINING EQUIPMENT
    • A63B21/00—Exercising apparatus for developing or strengthening the muscles or joints of the body by working against a counterforce, with or without measuring devices
    • A63B21/005—Exercising apparatus for developing or strengthening the muscles or joints of the body by working against a counterforce, with or without measuring devices using electromagnetic or electric force-resisters
    • A63B21/0056—Exercising apparatus for developing or strengthening the muscles or joints of the body by working against a counterforce, with or without measuring devices using electromagnetic or electric force-resisters using electromagnetically-controlled friction, e.g. magnetic particle brakes
    • A—HUMAN NECESSITIES
    • A63—SPORTS; GAMES; AMUSEMENTS
    • A63B—APPARATUS FOR PHYSICAL TRAINING, GYMNASTICS, SWIMMING, CLIMBING, OR FENCING; BALL GAMES; TRAINING EQUIPMENT
    • A63B21/00—Exercising apparatus for developing or strengthening the muscles or joints of the body by working against a counterforce, with or without measuring devices
    • A63B21/15—Arrangements for force transmissions
    • A—HUMAN NECESSITIES
    • A63—SPORTS; GAMES; AMUSEMENTS
    • A63B—APPARATUS FOR PHYSICAL TRAINING, GYMNASTICS, SWIMMING, CLIMBING, OR FENCING; BALL GAMES; TRAINING EQUIPMENT
    • A63B21/00—Exercising apparatus for developing or strengthening the muscles or joints of the body by working against a counterforce, with or without measuring devices
    • A63B21/15—Arrangements for force transmissions
    • A63B21/157—Ratchet-wheel links; Overrunning clutches; One-way clutches
    • A—HUMAN NECESSITIES
    • A63—SPORTS; GAMES; AMUSEMENTS
    • A63B—APPARATUS FOR PHYSICAL TRAINING, GYMNASTICS, SWIMMING, CLIMBING, OR FENCING; BALL GAMES; TRAINING EQUIPMENT
    • A63B24/00—Electric or electronic controls for exercising apparatus of preceding groups; Controlling or monitoring of exercises, sportive games, training or athletic performances
    • A63B24/0003—Analysing the course of a movement or motion sequences during an exercise or trainings sequence, e.g. swing for golf or tennis
    • A63B24/0006—Computerised comparison for qualitative assessment of motion sequences or the course of a movement
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B62—LAND VEHICLES FOR TRAVELLING OTHERWISE THAN ON RAILS
    • B62K—CYCLES; CYCLE FRAMES; CYCLE STEERING DEVICES; RIDER-OPERATED TERMINAL CONTROLS SPECIALLY ADAPTED FOR CYCLES; CYCLE AXLE SUSPENSIONS; CYCLE SIDE-CARS, FORECARS, OR THE LIKE
    • B62K3/00—Bicycles
    • B62K3/02—Frames
    • B62K3/10—Frames of single-beam type, i.e. connecting steering head to rear axle
    • 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
    • B62M1/00—Rider propulsion of wheeled vehicles
    • B62M1/14—Rider propulsion of wheeled vehicles operated exclusively by hand power
    • 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
    • B62M17/00—Transmissions characterised by use of rotary shaft, e.g. cardan shaft
    • 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
    • F16H25/00—Gearings comprising primarily only cams, cam-followers and screw-and-nut mechanisms
    • F16H25/08—Gearings comprising primarily only cams, cam-followers and screw-and-nut mechanisms for interconverting rotary motion and reciprocating motion
    • F16H25/12—Gearings comprising primarily only cams, cam-followers and screw-and-nut mechanisms for interconverting rotary motion and reciprocating motion with reciprocation along the axis of rotation, e.g. gearings with helical grooves and automatic reversal or cams
    • A—HUMAN NECESSITIES
    • A63—SPORTS; GAMES; AMUSEMENTS
    • A63B—APPARATUS FOR PHYSICAL TRAINING, GYMNASTICS, SWIMMING, CLIMBING, OR FENCING; BALL GAMES; TRAINING EQUIPMENT
    • A63B22/00—Exercising apparatus specially adapted for conditioning the cardio-vascular system, for training agility or co-ordination of movements
    • A63B22/0025—Particular aspects relating to the orientation of movement paths of the limbs relative to the body; Relative relationship between the movements of the limbs
    • A63B2022/0038—One foot moving independently from the other, i.e. there is no link between the movements of the feet
    • A—HUMAN NECESSITIES
    • A63—SPORTS; GAMES; AMUSEMENTS
    • A63B—APPARATUS FOR PHYSICAL TRAINING, GYMNASTICS, SWIMMING, CLIMBING, OR FENCING; BALL GAMES; TRAINING EQUIPMENT
    • A63B24/00—Electric or electronic controls for exercising apparatus of preceding groups; Controlling or monitoring of exercises, sportive games, training or athletic performances
    • A63B24/0003—Analysing the course of a movement or motion sequences during an exercise or trainings sequence, e.g. swing for golf or tennis
    • A63B24/0006—Computerised comparison for qualitative assessment of motion sequences or the course of a movement
    • A63B2024/0009—Computerised real time comparison with previous movements or motion sequences of the user
    • A—HUMAN NECESSITIES
    • A63—SPORTS; GAMES; AMUSEMENTS
    • A63B—APPARATUS FOR PHYSICAL TRAINING, GYMNASTICS, SWIMMING, CLIMBING, OR FENCING; BALL GAMES; TRAINING EQUIPMENT
    • A63B22/00—Exercising apparatus specially adapted for conditioning the cardio-vascular system, for training agility or co-ordination of movements
    • A63B22/20—Exercising apparatus specially adapted for conditioning the cardio-vascular system, for training agility or co-ordination of movements using rollers, wheels, castors or the like, e.g. gliding means, to be moved over the floor or other surface, e.g. guide tracks, during exercising
    • A63B22/201—Exercising apparatus specially adapted for conditioning the cardio-vascular system, for training agility or co-ordination of movements using rollers, wheels, castors or the like, e.g. gliding means, to be moved over the floor or other surface, e.g. guide tracks, during exercising for moving a support element in reciprocating translation, i.e. for sliding back and forth on a guide track
    • A63B22/205—Exercising apparatus specially adapted for conditioning the cardio-vascular system, for training agility or co-ordination of movements using rollers, wheels, castors or the like, e.g. gliding means, to be moved over the floor or other surface, e.g. guide tracks, during exercising for moving a support element in reciprocating translation, i.e. for sliding back and forth on a guide track in a substantially vertical plane, e.g. for exercising against gravity
    • A—HUMAN NECESSITIES
    • A63—SPORTS; GAMES; AMUSEMENTS
    • A63B—APPARATUS FOR PHYSICAL TRAINING, GYMNASTICS, SWIMMING, CLIMBING, OR FENCING; BALL GAMES; TRAINING EQUIPMENT
    • A63B2220/00—Measuring of physical parameters relating to sporting activity
    • A63B2220/10—Positions
    • A63B2220/13—Relative positions
    • A—HUMAN NECESSITIES
    • A63—SPORTS; GAMES; AMUSEMENTS
    • A63B—APPARATUS FOR PHYSICAL TRAINING, GYMNASTICS, SWIMMING, CLIMBING, OR FENCING; BALL GAMES; TRAINING EQUIPMENT
    • A63B2230/00—Measuring physiological parameters of the user
    • A63B2230/04—Measuring physiological parameters of the user heartbeat characteristics, e.g. ECG, blood pressure modulations
    • A63B2230/06—Measuring physiological parameters of the user heartbeat characteristics, e.g. ECG, blood pressure modulations heartbeat rate only
    • A—HUMAN NECESSITIES
    • A63—SPORTS; GAMES; AMUSEMENTS
    • A63B—APPARATUS FOR PHYSICAL TRAINING, GYMNASTICS, SWIMMING, CLIMBING, OR FENCING; BALL GAMES; TRAINING EQUIPMENT
    • A63B2230/00—Measuring physiological parameters of the user
    • A63B2230/40—Measuring physiological parameters of the user respiratory characteristics
    • A63B2230/42—Measuring physiological parameters of the user respiratory characteristics rate

Definitions

  • the present invention pertains to a transmission system for changing the gear ratio between an input portion and an output portion thereof, and, in particular, to an in-line multi-gear assembly and a multi-gear wheel hub both of which permit changing of the gear ratio, a helical drive transmission system employing the in-line multi-gear assembly and/or the multi-gear wheel hub, a method for transmitting power at different gear ratios from a helical drive to a driven wheel, and a bicycle utilizing such a helical drive transmission system 2.
  • a conventional bicycle includes a pair of pedals mounted onto a crank shaft having a main driving sprocket affixed thereto. Input power provided by the rider to the pedals is typically transferred from the driving sprocket to the rear wheel of the bicycle via a chain loop that extends between the main driving sprocket and a rear driven sprocket mounted on the hub of the rear wheel.
  • the gear ratio in such a bicycle is typically altered by providing a plurality of different sized sprockets for the main driving sprocket and/or the rear driven sprocket.
  • One or more derailers physically move the chain between the different sized sprockets, thereby altering the gear ratio.
  • the helical drive disclosed in the '982 application transmits power provided by the user to the rear wheel of the bicycle at only one transmission
  • an object of the present invention to provide a transmission system for use with a helical drive that permits changing of the transmission ratio between the output of the helical drive and the output of the transmission system.
  • this object is achieved by providing an in-line multi-gear assembly that includes an input carrier assembly operatively coupled to the output portion of a helical drive such that an axis of rotation of the input carrier assembly is substantially aligned with an axis of rotation of the output portion of the helical drive.
  • a gear assembly coupled to the input carrier assembly has a plurality of gears selectively engageable in various combinations to provide a selectively variable transmission ratio.
  • An output assembly is coupled to the output of the gear assembly.
  • the gear assembly includes a ratchet shell cap rotateably connected to the helical drive, a ring gear carrier concentrically located inside the ratchet shell cap, and .a planetary gear carrier assembly concentrically located inside the ring gear carrier.
  • the ring gear carrier assembly and the ratchet shell cap are adapted to be rotateably engaged such that a rotation of the input carrier assembly induces a rotation of the output assembly at a first transmission ratio.
  • the input carrier assembly, ring gear carrier assembly, planetary gear carrier assembly and output assembly are adapted to be rotateably engaged such that a rotation of the input carrier assembly induces a rotation of the output assembly at a second transmission ratio.
  • the input carrier assembly, planetary gear carrier assembly, ring gear carrier assembly and ratchet shell cap are adapted to be rotateably engaged such that a rotation of the input carrier assembly induces a rotation of the output assembly at a third transmission ratio.
  • a multi-gear wheel hub having two input gears and a gear assembly associated therewith.
  • Each input gear is coupled to an output portion of the helical drive such that the axis of rotation of the input gear is at a non-zero angle relative to the axis of rotation of the output portion of the helical drive.
  • the gear assembly includes a main shaft, a bushing rotateably mounted on an end portion of the main shaft, an orbital shaft coupled to the bushing such that rotation of bushing causes the orbital shaft to orbit the main shaft.
  • a rotating member rotates about the main shaft outside an orbit of the orbital shaft.
  • First and second stationary gears are mounted on the main shaft.
  • First and second orbital gears are rotateably mounted on the orbital shaft.
  • first and second ring gears are mounted on the rotating member.
  • a shifting mechanism alternatively positions the first orbital gear in an engaged relationship with the first stationary gear and the first ring gear and positions the second orbital gear in an engaged relationship with the second stationary gear and the second ring gear.
  • first and second stationary gears, first and second orbital gears, and first and second ring gear selected such that the first transmission ratio is different from the second transmission ratio.
  • No prior multi-gear wheel hub has dual input gears, one on each end of the hub.
  • This object is achieved by providing the steps of providing input power to an input portion of a first helical drive, transferring rotational energy from an input portion of a transmission system to an output portion thereof, wherein the transmission system has a selectively variable transmission ratio using the above described in-line multi-gear transmission system and or the multi-gear hub to provide a variety of alternative transmission ratios for transferring rotational energy from the input portion to the output portion of the transmission system, and coupling the output portion of the transmission system to said drive member.
  • Fig. 1 is side view of a bicycle having a helical drive system for transmitting input power to a drive wheel according to a first embodiment of the present invention
  • Fig. 2 is a top view of the bicycle illustrated in Fig. 2;
  • Fig. 3 is an exploded view of the helical drive system including a helical drive and an in-line multi-gear transmission assembly;
  • Fig. 4 is a side view of the helical drive system illustrated in Fig. 3;
  • Fig. 5A-5C are perspective views of a helical carrier assembly used in the helical drive system illustrated in Fig. 1;
  • Fig. 6 is a perspective view of helical shaft and input portion of the helical drive illustrated in Figs. 3-4;
  • Fig. 7 is a perspective view of a retaining nut in an input carrier assembly used in the in-line multi-gear transmission assembly of Fig. 3;
  • Fig. 8 is a perspective view of an input carrier in the input carrier assembly used in the in-line multi-gear transmission assembly of Fig. 3;
  • Fig. 9 is a perspective view of a ratchet shell cap used in the in-line multi- gear transmission assembly of Fig. 3;
  • Fig. 10 is a perspective view of a ring gear carrier used in the in-line multi-gear transmission assembly of Fig. 3;
  • Fig. 11 is a perspective view of a planetary gear carrier used in the in-line multi-gear transmission assembly of Fig. 3;
  • Fig. 12 is a perspective view of an output assembly used in the in-line multi-gear transmission assembly of Fig. 3;
  • Fig. 13 is a perspective view of an axle assembly used in the in-line multi- gear transmission assembly of Fig. 3 with an end plate connected thereto;
  • Fig. 14 is a perspective view of a portion of a sifter cable assembly used in the in-line multi-gear transmission assembly of Fig. 3;
  • Fig. 15A-15E are perspective view of the components of a shifter mechanism used in the in-line multi-gear assembly of Fig. 3;
  • Fig. 16A is a side view of a bicycle having a helical drive system for transmitting input power to a drive wheel according to a second embodiment of the present invention
  • Fig. 16B is a top view of the bicycle illustrated in Fig. 16A;
  • Fig. 17 is a cross-sectional view of a multi-gear hub according to the principles of the present invention
  • Fig. 18 is a cross-sectional view of an overrunning clutch used in the multi-gear hub of Fig. 17;
  • Fig. 19 is a side view of a bicycle having a helical drive system for transmitting input power to a drive wheel according to a third embodiment of the present invention
  • Fig. 20 is a top view of the bicycle illustrated in Fig. 19
  • Fig. 21 is a schematic illustration of a helical drive system used in the bicycle illustrated in Figs. 19-20;
  • Fig. 22 is a top view of a bicycle having a helical drive system for transmitting input power to a drive wheel according to a fourth embodiment of the present invention
  • Fig. 23 is a schematic illustration of a helical drive system used in the bicycle illustrated in Fig. 22;
  • Fig. 24 is a top view of a bicycle having a helical drive system for transmitting input power to a drive wheel according to a fifth embodiment of the present invention.
  • Fig. 25 is a schematic illustration of a helical drive system used in the bicycle illustrated in Fig. 24;
  • Fig. 26 is a side view of a bicycle having a helical drive system for transmitting input power to a drive wheel according to a sixth embodiment of the present invention
  • Fig. 27 is a top view of the bicycle illustrated in Fig. 26;
  • Fig. 28 is a top view of the drive system used in the bicycle illustrated in Figs. 25-26;
  • Fig. 29 is a side view of the drive system used in the bicycle illustrated in Figs. 25-26;
  • Fig. 30 is a side view of a bicycle having a helical drive system for transmitting input power to a drive wheel according to a seventh embodiment of the present invention
  • Fig. 31 is a top view of the bicycle illustrated in Fig. 30;
  • Fig. 32 is a side view of the drive system used in the bicycle illustrated in
  • Fig. 33 is a side view of a bicycle having a helical drive system for transmitting input power to a drive wheel according to an eighth embodiment of the present invention
  • Fig. 34 is a top view of the bicycle illustrated in Fig. 33
  • Fig. 35 is a top view of the drive system used in the bicycle illustrated in Figs. 33-34;
  • Fig. 36 is a side view of the drive system used in the bicycle illustrated in Figs. 33-34; and Fig. 37 is a perspective view of a polycycle having a helical drive system for transmitting input power to a drive wheel according to a first embodiment of the present invention.
  • Fig. 1 illustrates a bicycle 30 having a frame 32, a seat 33, handlebars 34, and front and rear wheels 35 and 36, respectively.
  • rear wheel 36 is driven by a helical drive system 38.
  • Power is provided to helical drive system 38 via input devices 40, which in this embodiment, are actuated by the pedaling motion of the bicycle rider.
  • Helical drive system 38 includes a first and a second helical drive assembly
  • transmission assembly 45 includes a first and a second in-line multi gear transmission assembly 46 and 48.
  • Linear movement of an input device 40 in each helical drive assembly over an associated helical shaft 44 causes the helical shaft to rotate.
  • the rotational motion at the output of the helical drive assembly is input to a transmission assembly 45.
  • helical drive assembly 42 The rotational motion produced by helical drive assembly 42 is transferred by transmission assembly 45 to rear wheel 36, which acts as a driving wheel for bicycle 30.
  • left and right helical drives 42a and 42b, respectively, are provided within or attached to the forks of frame 32 to which rear wheel 36 is also attached.
  • the rides leans forwards toward handlebar 34 and pedals while in a slightly prone position with his/her legs projecting generally toward the rear of the bicycle.
  • Translational motion of the input devices is in the direction indicated by arrow X, which is in a plane intersecting a rear hub 47 of the bicycle.
  • Fig. 3 is an exploded view of a preferred exemplary embodiment of a helical drive system having an in-line multi-gear transmission assembly 46 or 48.
  • the structure for in-line multi-gear transmission assemblies 46 and 48 are identical and includes an end plate 52, an axle assembly 180, an output assembly 182, a gear assembly 186, an input carrier assembly 188, a shifter cable assembly 184, a helical drive 190 and a helical carrier assembly 192.
  • Each of the components and their interactions is explained in detail below with references to Figs. 3-15.
  • the in-line multi-gear transmission system has three selectable transmission ratios.
  • transmission systems with other transmission ratios two, four, five or six, for example are contemplated by this invention.
  • Fig. 4 illustrates an assembled helical drive system with a cutout view of a helical drive housing 62 that contains the components of the helical drive system.
  • Helical drive housing 62 has a cylindrical shape with a hollow center.
  • a slot 66 defined along a longitudinal direction on helical drive housing 62 receives a portion of input device 40.
  • Helical drive housing 62 also has a carrier end 198 to receive helical carrier assembly 192 and an output end 196 to receive output assembly 182 and an end plate 52.
  • a cutout 64 is defined on an output end 190 of helical drive housing 62 to allow output assembly 182 to transfer rotational forces from in-line multi-gear assembly 46, 48 to a hub of rear wheel 36.
  • helical ca ⁇ ier assembly 192 has an end cap
  • End cap 106 is to be fixedly and non-rotationally attached to carrier end 198 of helical drive housing 62 (see Fig. 4).
  • a shifter cable 84 (Figs. 1, 2 and 14) passes through a hole 107 defined in the center of end cap 106.
  • Helical carrier assembly bearing 104 is placed between end cap 106 and helical drive carrier 102.
  • Helical drive carrier 102 has a helical input device engaging mechanism.
  • the helical input device engaging mechanism is a slit 103 to receive one end of helical drive shaft 98 depicted in Fig. 6.
  • Helical drive shaft 98 is a twisted bar with a hollow center 84 (which is only one exemplary embodiment of helical drive devices).
  • Other types of helical drive devices are shown in the applications identified above.
  • Helical drive carrier 102 can have a variety of configurations to correspond to the variety of helical drive devices so long as it is adapted to be rotated by rotational motion of the helical drive device.
  • Figs. 7 and 8 illustrate components of a preferred exemplary embodiment of input carrier assembly 188.
  • Input carrier assembly 188 includes an input carrier 94, preferably having a cylindrical shape, with a hollow center.
  • Input carrier 94 has two surfaces: a helical drive locking surface 134, and a gear assembly locking surface 136.
  • a helical drive engaging mechanism (not shown) is disposed on helical drive locking surface 134.
  • the helical drive engaging mechanism on input carrier 94 serves a substantially identical function as helical drive carrier 102. In other words, the helical drive engaging mechanism on input ca ⁇ ier 94 receives an end of a helical drive device.
  • Gear assembly locking surface 136 has a number of tapered splines 132 protruding in the direction perpendicular to surface 136. Tapered splines 132 engage with gear assembly 186 to transfer rotational power from input carrier assembly 188 to gear assembly 186.
  • An input carrier bearing 130 is disposed at the outer surface of the hollow center of input carrier 94.
  • the hollow center is sized to receive a retaining nut 96.
  • Shifter cable 84 passes through a hole defined in a center of retaining nut 96.
  • Gear assembly 186 preferably has a number of gears selectively engageable in various combinations to transmit drive power in a various transmission ratios from input carrier assembly 188 to output assembly 182.
  • gear assembly 186 includes a ratchet shell cap 92 with a ratchet shell cap engaging mechanism, a ring gear carrier assembly 90 with a number of ring gear carrier engaging mechanisms and a planetary gear carrier assembly 74 with a number of planetary gear carrier engaging mechanisms.
  • ratchet shell cap 92 preferably has a cylindrical shape with a hollow center, and includes a bearing 170.
  • ratchet shell cap teeth 172 disposed about the inner surface of ratchet shell cap 92 serve as a ratchet shell cap engaging mechanism.
  • ring gear carrier assembly 90 preferably has a cylindrical shape with a hollow center, a planetary gear carrier locking inner surface 157, an input carrier locking inner surface 155 and ring gear carrier engaging mechanisms.
  • the ring gear carrier engaging mechanisms include a number of cogs 154 disposed on input carrier locking inner surface 155, a number of retractable pawls 152 pivotally mounted on ring gear carrier 90 and a gear 156 disposed on planetary gear carrier locking inner surface 157.
  • planetary gear carrier assembly 74 preferably has a cylindrical shape with a hollow center, an input carrier locking surface 146 and planetary gear carrier engaging mechanisms.
  • the planetary gear ca ⁇ ier engaging mechanisms includes a number of planetary pinion gears 144 mounted on planetary gear carrier assembly 74, a number of pawls 140 pivotally mounted on planetary gear carrier assembly 74, and a number of carrier pins 142 protruding from input carrier locking surface 146.
  • the pawls, both retractable pawls 152 of ring gear carrier assembly 90 and pawls 140 of planetary gear carrier assembly 74, are pivotally mounted on respective carrier assemblies such that they would preferably engage with other gears only in one direction but not in the other direction.
  • output assembly 182 includes an output gear 70, a shell 72 and a bearing 68.
  • output gear 70 is a bevel gear and shell 72 is fixedly attached to ratchet shell cap 92 (???).
  • output gear 70 is angled with respect to the axis of rotation of in-line multi-gear assembly 46a. In the exemplary embodiment depicted in Fig. 1, the rotational force is transferred from in-line multi-gear assembly 46, 48 a to a hub of rear wheel 36 at an angle of approximately 90 degrees.
  • axle assembly 180 with end plate 52 connected thereto is illustrated in Fig. 13.
  • axle assembly 180 includes an end plate end 53, an input assembly end 59 and a shifter slot arrangement 57, and a stationary sun gear 56.
  • End plate 52 is fixedly and non-rotationally connected to end plate end 53 of axle assembly 180.
  • end plate 52 is rigidly connected to output end 196 of helical drive housing 62 (as shown in Fig. 4).
  • Stationary sun gear 56 is located on axle assembly 180 so as to engage pinion gears 144 of planetary gear carrier assembly 74 when the helical drive system is assembled.
  • Shifter slot arrangement 57 of axle assembly 180 preferably has a hollow center into which shifter cable assembly 184 is provided and a shifter slot 58.
  • a protruding part of a shifter ring 78 extends through slot 58 to interact with gear assembly 186.
  • shifter cable assembly 184 includes a shifter cable 84, cable pin 122, and cable pin threading 120, a spring 88, a pin lock 86 with grooves to receive a pin 80 which has notches on both ends, shifter ring 78 with an outer surface 77 and a number of protruding parts, and a bushing 76.
  • Spring 88, pin lock 86, pin 80, shifter ring 84 and bushing 76 are mounted coaxially on shifter cable 84.
  • input carrier assembly 188, gear assembly 186 and output assembly 182 are all coaxially mounted on axle assembly 180.
  • Axle assembly 180 is preferably stationary.
  • the rotational force is received from helical drive shaft 98 by input carrier assembly 188 and the rotational force is transferred through gear assembly 186 with a selected transmission ratio to output assembly 182.
  • a transmission ratio is selected by a rider the using a shifter cable controller 49 (Fig. 1).
  • Shifter cable controller 49 moves shift cable 84 according to the rider's selection, which in turn moves shifter cable assembly 184 to engage gear assembly 186.
  • Shifter cable controller 49 is mounted on any part of bicycle 30 that can conveniently accessed by the rider.
  • shifter cable controller can be mounted on handlebars 34 or on frame 32. Any conventionally available shifter cable controller can be used as shifter cable controller 49.
  • shifter cable controller can be any one of the following: an indexed thumb controlled shifter cable controller, a not indexed continuous thumb controlled shifter cable controller, or indexed twist handle grips.
  • Shifter cable controller 49 moves shifter cable 84 in a direction so as to engage shifter cable assembly 184 with gear assembly 186 and input carrier assembly 188 to generate any one of the transmission ratios. More specifically, for a one-to-one transmission ratio, shifter cable 84 moves shifter ring 78 to lock the rotation of input carrier 94 to ring gear carrier assembly 90. This is preferably accomplished by shifter ring 78 locking tapered splines 132 on input carrier 94 to cogs 154 on ring gear carrier assembly 90. As ring gear ca ⁇ ier assembly 90 rotates, pawls 152 on ring gear carrier assembly 90 engage ratchet teeth 172 on ratchet shell cap 92 in one direction. Further, the rotation of ratchet shell cap 92 causes shell 72 to rotate output assembly 182.
  • shifter cable 84 moves shifter ring 78 so as to retract retractable pawls 152 on ring gear carrier assembly 90.
  • Tapered splines 132 of input carrier 94 remain engaged with cogs 154 of ring gear carrier assembly 90.
  • Rotation of ring gear carrier assembly 90 is transferred to planetary gear carrier assembly 74. This is accomplished by engaging gear 156 on ring gear carrier assembly 90 to pinion gears 144 on ring gear carrier assembly 74.
  • pawls 140 on planetary gear carrier assembly 74 become engaged with ratchet teeth 172 on ratchet shell cap
  • shifter cable 84 moves shifter ring 78 so as to lock tapered splines 132 on input carrier 94 to lock with pinion pins 142 on planetary gear carrier assembly 74.
  • Rotation is transferred from pinion gears 142 of planetary gear carrier assembly 74 to gear 156 of ring gear carrier assembly 90.
  • Retractable pawls 152 of ring gear carrier assembly 90 engage ratchet teeth 172 of ratchet shell cap 92 in one direction.
  • Figs. 16A and 16B illustrate a second embodiment for the transmission system for transmission power from a helical drive to a drive wheel in a bicycle.
  • Bicycle 500 in Figs. 16A and 16B is identical to bicycle 30 in Fig. 1, except for the structure for the transmission system.
  • bicycle 500 in Figs. 16A and 16B employs a multi-gear hub 502 for varying the gear ratio between the output of the helical drive and the output of the transmission assembly.
  • Multi- geared hub 502 can be used alone, as shown in Figs. 16A and 16B, or in combination with the in-line multi-gear transmission system discussed above. Details of multi-gear hub 502 and its method of operation are described below with reference to Figs. 17 and 18.
  • Multi-gear hub 502 includes a main shaft 504 that attaches to the bicycle frame.
  • Bushings 506 and 508 are rotateably mounted onto each end of main shaft 504 and are prevented from moving in a lengthwise direction along the axis of main shaft 504 by nuts 510 and 512.
  • Input gears 514 and 516 are rigidly attached to bushings 506 and 508 via nuts 509 and 511.
  • input gears 514 and 516 are beveled so that the axis of rotation of input gears 514 and 516 is angled with respect to the axis of rotation of output gears 518 and 520 disposed at the ends of helical drive shafts 522 and 524 in helical drives 42.
  • Input gears 514 and 516 in the multi-gear hub are coupled to output gears 518 and 520, respectively, so that the rotation of output gears 518 and 520 is transferred approximately 90° to input gears 514 and 516.
  • input gears 514 and 516 and output gears 518 and 520 can have any of a variety of configurations that permit rotational motion to be transferred at an angle from an external input device to rotate bushings 506 and 508, such as using a worm gear or meshed sprockets.
  • Bushing 506 rotates and engages an overrunning clutch 526 which rotates an orbital shaft carrier 528. Rotation of orbital shaft carrier 528 rotates orbital shaft 530 around main shaft 504. Similarly, bushing 508 rotates and engages an overrunning clutch 532 which rotates orbital shaft carrier 528 to rotate orbital shaft 530 around main shaft 504. Rotational motion of either bushing 506 or bushing 508 translates into orbital movement of orbital shaft 530 via overrunning clutches 526 and/or 532.
  • the overrunning clutches enable the input gears to be actuated independently of one another by an associated helical drive assembly.
  • Overrunning clutches 526 and 532 have a structure similar to the clutches used in helical drive 42. Although the clutches used in helical drive 42 are described in detail in the '982 application, overrunning clutches 526 and 532 used multi-gear hub 502 are described briefly below with reference to Fig. 18.
  • Overrunning clutch 526 or 532 includes a inner ring member 540 and an outer ring member 542.
  • inner ring member 540 has sloped shoulders 544 which wedge against rollers 546 when the inner ring member moves in a direction A with respect to the outer ring member, thereby engaging inner ring member 540 to outer ring member 542 so to both rotate together in direction A.
  • rollers 546 disengage from shoulders 544 and move into a receiving area 545 so that inner ring member 540 moves independent of outer ring member 542. It is to be understood that the shape, number and position of shoulders 544 can be varied so long as the wedging (engaging) and disengaging functions are achieved.
  • Multi-gear hub 502 includes a first stationary gear 550 and a second stationary gear 552 mounted on an intermediate portion of main shaft 504.
  • a first orbital gear 554 and a second orbital gear 556 are rotateably mounted on orbital shaft 530 via bearings 555 and 557, respectively.
  • a cylindrical rotating member 558 serving as ring gear carrier rotates about main shaft 504 outside an orbit of orbital shaft 530.
  • a first ring gear 560 and a second ring gear 562 are fixed to rotating member 558 via screws 564.
  • the first and second ring gears are spaced apart from one another and from the inner walls as the ends of the rotating member by spacers 566.
  • First and second orbital gears are moveable along orbital shaft 530 to selectively engage first and second stationary gears 550 and 552, respectively.
  • the stationary and ring gears are positioned such that if first orbital gear 554 is engaged with first stationary gear 550 and first ring gear 560, orbital rotation of orbital shaft 530 about main shaft 504 causes rotation in first orbital gear 550.
  • first ring gear 560 due to the engagement with first orbital gear 550, thereby rotating member 558 at a first transmission ratio.
  • second orbital gear 556 is engaged with second stationary gear 552 and second ring gear 562, orbital rotation of orbital shaft 530 about main shaft 504 rotates second orbital gear 556.
  • This rotation is transferred to second ring gear 562, thereby rotating member 558 at a second transmission ratio.
  • the diameters of first stationary gear 550, said first orbital gear 554, and first ring gear 560 are different from the diameters of second stationary gear 552, second orbital gear 556, and second ring gear 562 so that the first transmission ratio is different from the second transmission ratio.
  • a shifting mechanism 570 selectively and alternatively positions first orbital gear 554 in an engaged relationship with first stationary gear 550 and first ring gear 560 and positions second orbital gear 556 in an engaged relationship with second stationary gear 552 and second ring gear 562.
  • Shifting mechanism 570 includes a bolt 572 slidably disposed in a hollow center of an intermediate portion of main shaft 504. In the illustrated embodiment, bolt 572 moves along a lengthwise direction of main shaft 504 between a first position and a second position.
  • Bolt 572 includes an arm 574 that extends through a slot 576 defined along a lengthwise direction of main shaft 504.
  • first and second orbital gears 554 and 556 are coupled to arm 574 such that if bolt 572 is in the first position, first orbital gear 554 is engaged with first stationary gear 550 and first ring gear 560 and second orbital gear 556 is disengaged, and if bolt 572 is in the second position, second orbital gear 556 is engaged with second stationary gear 552 and second ring gear 562 and first orbital gear 554 is disengaged.
  • first and second orbital gears 554 and 556 are not engaged with a ring gear, effectively placing the transmission system in neutral.
  • a spring washer 580 maintains spring nut 578 in position within main shaft 504.
  • a washer 582 acts as a stopper preventing movement of bolt 572 toward spring nut 578.
  • a chain 584 is attached to an end of bolt 572 opposite spring 576 via pin 586, nut 588 and washer 590. Shifting between the first transmission ratio and the second transmission ratio is accomplished by providing a tension on chain 584.
  • a gear shifting mechanism 585 controls the tension on chain 584, and, hence, the selection of the gear ratio for multi-gear hub 30.
  • the gear shifting mechanism can be any conventional mechanism, for example indexed or continuous, and mounted on any suitable location on the bicycle.
  • rotational movement of rotating member 558 is transferred to a hub casing 592 adapted to rotate about main shaft 504 outside rotating member 558.
  • Bearings 594 between rotating member 558 and hub casing 592 permit rotational movement therebetween.
  • An overrunning clutch 596 which has substantially the same configuration as overrunning clutches 526 and 532, couples hub casing 592 to rotating member 558 such that rotation of rotating member 558 in a first direction is transferred to hub casing 592 if rotating member
  • lubrication holes 606 are provided in various portions of the multi-gear hub to provide lubrication to the surface of the components where friction is to be minimized. It is to be understood that the lubrication holes can be provided in a variety of locations and have shapes other than those illustrated in Fig. 17 so long a they serve to provide a lubricant, such as a lubricating oil, to the friction surfaces.
  • Figs. 19-21 illustrate a bicycle 608 having a helical drive system 610 for transmitting input power to a drive wheel according to a third embodiment of the present invention.
  • the bicycle illustrated in Figs. 19 and 20 is similar to the bicycle illustrated in Figs. 1 and 2, except that a different configuration for the helical drive system is employed.
  • helical drive system 610 includes a pair of helical drives 612a and 612b that are aligned with one another along a plane generally perpendicular to the longitudinal axis of bicycle 608.
  • the helical drives are arranged such that input devices (pedals) 614 are disposed in generally the same location as the pedals in a conventional bicycle. Therefore, the configuration for bicycle 608 in Figs. 19 and 20 is more familiar to the general public than the configuration illustrated in Figs. 1 and 2.
  • gears 611 and 613 are provided at the end of respective helical drive shafts 616a and 616b.
  • Gears 611 and 613 are meshed so that helical drives 612a and 612b operate in synchronization with one another.
  • a transmission system 615 couples the output of helical shafts 616a and 616b to rear wheel hub 618.
  • Transmission system 615 includes a pair of in-line multi-gear assemblies 620a and 620b coupled to helical shafts 616a and 616b for changing the transmission ratio thereof.
  • a gear assembly 622 couples the output rotational motion output from helical shafts 616a and 616b to a single drive shaft 623.
  • the gears in gear assembly 622 are selectively engageable with one another to merit engaging and disengaging of the transmission system.
  • a cable In the illustrated embodiment, a cable
  • gear 615 causes a gear 619 to move in and out of engagement with the other gears in gear assembly 622.
  • the gears in gear assembly 622 are coupled to the gears 611 and 613 via an overrunning clutch, as illustrated in Fig. 18, to permit the bicycle to freewheel.
  • a bevel gear 624 at the rearward end of drive shaft and a bevel gear 626 on hub 618 transfers rotational energy to rear wheel 36 of bicycle 608.
  • Fig. 21 is a schematic illustration of the helical drive and transmission systems showing the various components all in a same plane for ease of illustration.
  • Figs. 22-23 illustrate a bicycle 708 having a helical drive system 710 for transmitting input power to a drive wheel according to a forth embodiment of the present invention.
  • the bicycle illustrated Fig. 22 is similar to the bicycle illustrated in Figs. 19 and 20, except that helical drive system 710 includes two drive shafts 712 and 714 for transmitting rotational motion to the rear wheel hub, rather than one drive shaft as in the embodiment depicted in Figs. 19 and 20.
  • a transmission system 716 couples the output of helical shafts 718a and 718b to a hub 719 of a rear wheel 720.
  • Transmission system 716 includes a pair of in-line multi-gear assemblies 722a and 722b coupled to helical shafts 718a and 718b, respectively, for changing the transmission ratio thereof.
  • Each of in-line multi-gear assemblies 722a and 722b couples to one of drive shafts 712 and 714.
  • a synchronization gear 724 selectively meshes with gears 726 and 727 provided at the output of the helical drive assemblies. When meshed, the synchronization gear causes the helical drive assemblies to operate in a synchronized manner.
  • Other components are substantially identical to the helical drive system depicted in Figs. 19 and 20.
  • Fig. 24 illustrates a poly-cycle 808 having a helical drive system 810 for transmitting input power to a pair of driven wheels 812a and 812b according to a fifth embodiment of the present invention.
  • the poly-cycle illustrated Fig. 24 is similar to the bicycle illustrated in Figs. 19 and 20, except that two rear wheels 812a and 812b are employed in this embodiment.
  • a drive shaft 814 couples with a pair of hub shafts 816a and 816b extending from the hubs (not shown) of rear wheels 812a and 812b.
  • a gear assembly 820 couples the output of the helical drives to drive shaft 814.
  • the components in the transmission system of this embodiment are substantially identical to the helical drive system depicted in Figs. 19-23.
  • Figs. 26-29 illustrate a polycycle 908 having a helical drive system 910 for transmitting input power to a pair of drive wheels 912a and 912b according to a sixth embodiment of the present invention.
  • the poly-cycle illustrated Figs. 26 and 27 is similar to the poly-cycle illustrated in Fig. 24, except that this embodiment includes a pair of helical drive assemblies 914a and 914b that are aligned with one another along a plane generally parallel to the longitudinal axis of poly-cycle 908. This configuration reduces the overall width of the helical drive system.
  • Helical drive assemblies 914a and 914b are structurally similar to those discussed above in the previous embodiments and include in-line multi-gear transmission assemblies 916a and 916b coupled to helical shafts.
  • the configuration for gear assembly 920 that transfers rotational motion from the helical drive assemblies to the rear wheel is fundamentally the same as the helical drive assemblies of the prior embodiments.
  • the primary different between this embodiment and previous embodiments is the placement and orientation of drive shaft 922 relative to gear assembly 920 due to the alignment of the helical drive assemblies 914a and 914b along the centerline of the bicycle.
  • Other components of the helical drive and transmission systems are substantially identical to the helical drive system depicted in Fig. 24.
  • Figs. 30 and 31 illustrate a bicycle 1008 having a helical drive system 1010 for transmitting input power to a drive wheel according to a seventh embodiment of the present invention.
  • the bicycle illustrated Figs. 30 and 31 is similar to the bicycle illustrated in Figs. 22, except that this embodiment includes a pair of helical drives 1012a and 1012b that are aligned with one another along a plane generally parallel to the longitudinal axis of bicycle 1008, as the embodiment illustrated in Figs. 26 and 27.
  • a pair of drive shafts 1014a and 1014b are coupled to a gear assembly 1016 having a configuration similar to that illustrated in Figs. 26-29.
  • Other components are substantially identical to the helical drive system depicted in Fig. 22.
  • Figs. 33 and 34 illustrate a bicycle 1108 having a helical drive system 1110 for transmitting input power to a drive wheel according to an eighth embodiment of the present invention.
  • the bicycle illustrated Figs. 33 and 34 is similar to the bicycle illustrated in Figs. 30 and 31, except that this embodiment includes one drive shaft 11 12 rather than two. Other components are substantially identical to the helical drive system depicted in Figs. 30 and 31.
  • Fig. 37 illustrates a tandem polycycle 1208 having a pair of helical drive systems 1210a and 1210b for transmitting input power to a pair of drive wheels 1212a and 1212b according to a ninth embodiment of the present invention.
  • Polycycle 1208 includes in-line multi-gear assemblies 1214, 1216, 1218 and 1220 associated with each helical drive shaft and a multi-gear hubs 1222 and
  • polycycle 1224 associated with each helical drive system 1201a and 1210b.
  • Other components of polycycle 1208 are substantially the same as those illustrated in the previous embodiments.
  • the helical drive transmission system employing the inline multi-gear assembly and/or the multi-gear wheel hub are contemplated by the present invention.
  • more than one in-line multi-gear transmission assemblies can be employed in the transmission system.
  • the in-line multi-gear transmission assemblies can be provided at locations in the transmission system other than directly coupled to the helical shaft.
  • an in-line multi-gear transmission assembly can be provided along the drive shaft.
  • the number of transmission ratios and the use of both an in-line multi-gear transmission assembly and a multi-gear hub in the same machine are also possible.
  • a helical drive bicycle may be made with both in-line transmissions as in Fig. 1, and a multi-gear hub, as in Fig. 16B.
  • a bicycle can be made with more than one in-line transmission in series, (for example, one attached to a drive shaft, and one attached to the helical member). Any such serial dual transmission bike would then offer a multiplied range of gear ratios. For example, a two speed in-line transmission with a five speed hub transmission, would yield a 10 speed bike, and could simulate the gears available on a conventional 10 speed bike with derailleurs, sprockets, and a chain.
  • a three speed in-line transmission and a two speed hub transmission are shown here. Other embodiments, could have other numbers of speeds, either more or less.
  • a single drive shaft as in Figs. 19, 20, and 21, is used, then a conventional multi-gear hub with a single input gear can be used, either with or without an in-line transmission. Braking of these bicycles are by conventional hand brake mechanisms.
  • Sprint bike embodiments may have no brakes.
  • the bike embodiments of the present invention can also be made with helical drives that are not integrated into the frame but attached to the exterior of the frame.
  • the multi-gear hub is shown with two input gears, one on each end of the hub. Instead of these dual input gears other dual input devices, such as sprockets, can be used where appropriate, one on each end of the hub. Also, here pinion gears are shown with the hub and drive shaft, but other gear arrangements between hub and drive shaft can be used, such as a worm gear.

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  • Engineering & Computer Science (AREA)
  • Health & Medical Sciences (AREA)
  • Mechanical Engineering (AREA)
  • Life Sciences & Earth Sciences (AREA)
  • General Health & Medical Sciences (AREA)
  • Physical Education & Sports Medicine (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Transportation (AREA)
  • Orthopedic Medicine & Surgery (AREA)
  • Biophysics (AREA)
  • Environmental Sciences (AREA)
  • Physics & Mathematics (AREA)
  • Electromagnetism (AREA)
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  • Veterinary Medicine (AREA)
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  • Biodiversity & Conservation Biology (AREA)
  • Public Health (AREA)
  • Animal Behavior & Ethology (AREA)
  • Structure Of Transmissions (AREA)

Abstract

L'invention concerne un système de transmission en ligne (46, 48) à plusieurs rapports pourvu d'un ensemble support d'entrée (188) couplé à la partie sortie d'un dispositif d'entraînement hélicoïdal (190), de manière que l'axe de rotation de l'ensemble support d'entrée (188) soit sensiblement aligné avec l'axe de rotation de la partie sortie du dispositif d'entraînement hélicoïdal (190). Un ensemble engrenage (186) disposé dans le système de transmission en ligne (46, 48) et un moyeu à plusieurs rapports (502) transmettent l'énergie de rotation de la partie entrée à la partie sortie dudit ensemble (186).
PCT/IB1998/000598 1997-04-07 1998-04-06 Systeme de transmission en ligne et moyeu de roue a plusieurs rapports dans un dispositif d'entrainement helicoidal WO1998045621A1 (fr)

Priority Applications (1)

Application Number Priority Date Filing Date Title
AU67428/98A AU6742898A (en) 1997-04-07 1998-04-06 In-line multi-gear transmission system and multi-gear wheel hub in a helical drive system

Applications Claiming Priority (24)

Application Number Priority Date Filing Date Title
US4296397P 1997-04-07 1997-04-07
US4296497P 1997-04-07 1997-04-07
US4192497P 1997-04-07 1997-04-07
US60/042,964 1997-04-07
US60/042,963 1997-04-07
US60/041,924 1997-04-07
US4376297P 1997-04-08 1997-04-08
US60/043,762 1997-04-08
US4413797P 1997-04-16 1997-04-16
US60/044,137 1997-04-16
US4446297P 1997-04-17 1997-04-17
US60/044,462 1997-04-17
US4532697P 1997-05-01 1997-05-01
US60/045,326 1997-05-01
US4950997P 1997-06-09 1997-06-09
US4950797P 1997-06-09 1997-06-09
US4910297P 1997-06-09 1997-06-09
US60/049,507 1997-06-09
US60/049,102 1997-06-09
US60/049,509 1997-06-09
US5027597P 1997-06-20 1997-06-20
US60/050,275 1997-06-20
US89803997A 1997-07-18 1997-07-18
US08/898,039 1997-07-18

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Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US20210010575A1 (en) * 2019-07-12 2021-01-14 Z-One and Only Technology Inc. Helical drive mechanism and handle mechanism for wheelchair with helical drive

Citations (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US1559578A (en) * 1925-03-07 1925-11-03 Humphrey F Morgan Driving mechanism
US3646822A (en) * 1969-04-30 1972-03-07 Luis Alberto Pocaterra Mechanical transmission system
US3937309A (en) * 1973-07-25 1976-02-10 Fichtel & Sachs Ag Multiple speed hub for a bicycle and like vehicle
US4865152A (en) * 1986-04-10 1989-09-12 Gardner Elmer W Jr Electrohydraulic vehicle drive system
US5228354A (en) * 1992-05-13 1993-07-20 Massachusetts Institute Of Technology Multispeed, shaft-driven vehicle drive
US5577412A (en) * 1992-10-16 1996-11-26 Vasiliev; Gennady V. Apparatus for converting a reciprocating motion into unidirectional rotation

Patent Citations (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US1559578A (en) * 1925-03-07 1925-11-03 Humphrey F Morgan Driving mechanism
US3646822A (en) * 1969-04-30 1972-03-07 Luis Alberto Pocaterra Mechanical transmission system
US3937309A (en) * 1973-07-25 1976-02-10 Fichtel & Sachs Ag Multiple speed hub for a bicycle and like vehicle
US4865152A (en) * 1986-04-10 1989-09-12 Gardner Elmer W Jr Electrohydraulic vehicle drive system
US5228354A (en) * 1992-05-13 1993-07-20 Massachusetts Institute Of Technology Multispeed, shaft-driven vehicle drive
US5577412A (en) * 1992-10-16 1996-11-26 Vasiliev; Gennady V. Apparatus for converting a reciprocating motion into unidirectional rotation

Cited By (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US20210010575A1 (en) * 2019-07-12 2021-01-14 Z-One and Only Technology Inc. Helical drive mechanism and handle mechanism for wheelchair with helical drive
WO2021009560A1 (fr) * 2019-07-12 2021-01-21 Z-One and Only Technology Inc. Mécanisme d'entraînement hélicoïdal et mécanisme de poignée pour fauteuil roulant à entraînement hélicoïdal
US11635124B2 (en) * 2019-07-12 2023-04-25 Z-One and Only Technology Inc. Helical drive mechanism and handle mechanism for wheelchair with helical drive

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