EP0986712A1 - Systeme de roues dentees et engrenages integrant ces dernieres - Google Patents

Systeme de roues dentees et engrenages integrant ces dernieres

Info

Publication number
EP0986712A1
EP0986712A1 EP98914710A EP98914710A EP0986712A1 EP 0986712 A1 EP0986712 A1 EP 0986712A1 EP 98914710 A EP98914710 A EP 98914710A EP 98914710 A EP98914710 A EP 98914710A EP 0986712 A1 EP0986712 A1 EP 0986712A1
Authority
EP
European Patent Office
Prior art keywords
gear wheel
gear
shaft
partially toothed
synchro
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Withdrawn
Application number
EP98914710A
Other languages
German (de)
English (en)
Inventor
William Wesley Martin
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Preload International Ltd
Original Assignee
Preload Gearbox Ltd
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Priority claimed from AUPO6287A external-priority patent/AUPO628797A0/en
Priority claimed from AUPO8430A external-priority patent/AUPO843097A0/en
Priority claimed from AUPP0779A external-priority patent/AUPP077997A0/en
Application filed by Preload Gearbox Ltd filed Critical Preload Gearbox Ltd
Publication of EP0986712A1 publication Critical patent/EP0986712A1/fr
Withdrawn legal-status Critical Current

Links

Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H3/00—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion
    • F16H3/02—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion without gears having orbital motion
    • F16H3/08—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion without gears having orbital motion exclusively or essentially with continuously meshing gears, that can be disengaged from their shafts
    • F16H3/12—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion without gears having orbital motion exclusively or essentially with continuously meshing gears, that can be disengaged from their shafts with means for synchronisation not incorporated in the clutches
    • 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
    • F16H3/00—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion
    • F16H3/02—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion without gears having orbital motion
    • F16H3/08—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion without gears having orbital motion exclusively or essentially with continuously meshing gears, that can be disengaged from their shafts
    • F16H3/083—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion without gears having orbital motion exclusively or essentially with continuously meshing gears, that can be disengaged from their shafts with radially acting and axially controlled clutching members, e.g. sliding keys
    • 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
    • F16H3/00—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion
    • F16H3/02—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion without gears having orbital motion
    • F16H3/08—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion without gears having orbital motion exclusively or essentially with continuously meshing gears, that can be disengaged from their shafts
    • F16H3/10—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion without gears having orbital motion exclusively or essentially with continuously meshing gears, that can be disengaged from their shafts with one or more one-way clutches as an essential feature
    • 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
    • F16H63/00—Control outputs from the control unit to change-speed- or reversing-gearings for conveying rotary motion or to other devices than the final output mechanism
    • F16H63/02—Final output mechanisms therefor; Actuating means for the final output mechanisms
    • F16H63/30—Constructional features of the final output mechanisms
    • F16H2063/3093—Final output elements, i.e. the final elements to establish gear ratio, e.g. dog clutches or other means establishing coupling to shaft
    • F16H2063/3096—Sliding keys as final output elements; Details thereof

Definitions

  • the present invention relates to a gear wheel construction. More particularly, the gear wheel construction of the present invention is intended for use in gear systems adapted to allow changing of gears under load without the need for a traditional clutch and with the substantial minimisation of any momentary reduction in power input to the system.
  • Constant mesh gear boxes generally rely on a means to lock and unlock individual gears with respect to a drive shaft. Unlocking a gear disengages that gear ratio and allows the gear to rotate freely about the shaft. Conversely, locking a gear with respect to the shaft causes that gear ratio to be engaged.
  • gear pairs or ratios are generally in constant mesh aligned along the length of two substantially parallel shafts. One gear pair or ratio is engaged at any one time whilst the remaining gear pairs or ratios rotate freely about the shaft.
  • the gear wheel construction of the present invention has as one object thereof to overcome the above problems associated with the prior art.
  • a gear wheel construction for use in a constant mesh gear box, the gear wheel construction characterised by a single gear wheel provided about a shaft in a rotatable and engageable manner, the gear wheel being divided longitudinally (axially) into two components, the first being a synchro-gear wheel and the second gear being a partially toothed gear wheel, wherein the synchro-gear wheel is provided in constant mesh with a gear wheel forming its gear wheel pair whilst the partially toothed gear wheel is meshed therewith intermittently during rotation, the synchro-gear wheel and the partially toothed gear wheel having provided therebetween at least one biasing means allowing momentary asynchronous rotation therein.
  • the synchro-gear wheel is provided about its shaft in a rotatable manner only, the partially toothed gear wheel alone being able to releasably engage the shaft.
  • the or each biasing means act to draw the partially toothed gear wheel and synchro-gear wheel into synchronous rotation after any momentary asynchronous rotation.
  • the force required to disengage the partially toothed gear wheel from its shaft is preferably greater than the force exerted thereon by the or each biasing means.
  • a gear system characterised by a pair of substantially parallel shafts, each shaft having provided thereabout at least two gear wheels forming gear wheel pairs or ratios with those gear wheels on the other shaft, wherein a rotary force applied to one shaft may be transferred to the other shaft through the gear wheels associated therewith upon that gear wheel pair being engaged with the shaft, wherein at least one of the gear wheel pairs has one gear wheel of that pair divided longitudinally (axially) into two components, the first being a synchro-gear wheel and the second gear being a partially toothed gear wheel, wherein the synchro- gear wheel is provided in constant mesh with a gear wheel forming its gear wheel pair whilst the partially toothed gear wheel is meshed therewith intermittently during rotation, the synchro-gear wheel and the partially toothed gear wheel having provided therebetween at least one biasing means allowing momentary asynchronous rotation therein.
  • the method of the present invention preferably further provides for the partially toothed gear wheel to return to synchronous rotation with the synchro-gear wheel. Such may be achieved through the action of a biasing means provided between the synchro-gear wheel and the partially toothed gear wheel.
  • the method of the present invention may be achieved, in bicycles, through use of a hand controller to cause momentary engagement of the gear wheel incorporating the partially toothed gear wheel.
  • the method of the present invention may be put into effect by way of a form of programmable logic controller, microprocessor, computer, or engine management system.
  • the step of calling for a change in gear may be initiated automatically by the programmable logic controller, microprocessor, computer, or engine management system or may be initiated manually.
  • the gear system of the present invention can be incorporated into a chainless drive shaft between the crank and the rear wheel.
  • the system may be fitted with a dual rear bevel gear and a dual direction rear wheel ratchet/roller clutch to provide power during back pedalling.
  • This arrangement allows step pedalling and allows the rider to power forwards by alternately shifting his weight from one foot to the other whilst standing upon the pedals of the bicycle. This arrangement allows power to be maintained while the rider is negotiating rough or otherwise difficult terrain.
  • the gear system may be provided with a rear foot brake. It is envisaged that a dual ratchet or full lock pawl arrangement for engagement of the gear wheels would be required for step pedalling or rear foot braking. DESCRIPTION OF THE DRAWINGS
  • Figure 1 is a diagrammatic cross-sectional view taken longitudinally
  • Figure 2 is a cross-sectional view through the shafts of the gear system of Figure 1 showing a partially toothed gear wheel in engagement with its shaft, a synchro-gear wheel located therebehind and shown in phantom, and further showing a biasing means in phantom between the partially toothed and synchro-gear wheels; and
  • Figure 3 is a cross-sectional view in accordance with Figure 2, showing the partially toothed gear wheel and synchro-gear wheel moving asynchronously thereby causing the biasing means to extend or flex.
  • FIG. 1 there is shown a gear system 10 suitable for use with a bicycle.
  • the gear system 10 comprises a casing 16, shown in part and in section.
  • a first shaft 18 is mounted in the casing 16 by way of bearing means, for example a single row ball bearings 20 and 22.
  • the ball bearings 20 and 22 are rigidly located in the end portions 24 of the casing 16.
  • the first shaft 18 has a first end 26 received and held within the ball bearing 22.
  • a free or second end 28 of the shaft 18 has rigidly located thereabout a bevel gear wheel 30, such that upon rotation of the bevel gear 30 the first shaft 18 also rotates.
  • the first shaft 18 has provided therein a hollow bore 32.
  • a roving magnet 34 is located within the bore 32 in a manner such that it may travel almost the entire length thereof and the roving magnet 34 is proportioned accordingly.
  • the roving magnet 34 has a guide cable 36 attached thereto and extends through the bore 32 therefrom and further through the second end 28 of the first shaft 18.
  • the guide cable 36 extends to an index member 38 to which it is rigidly but adjustably connected.
  • An annular bush 40 is provided within the bore 32 adjacent the second end 28 and through which the guide cable 36 extends. The bush 40 acts as a seal and aids in the smooth travel of the guide cable 36, thereby preventing wear of the guide cable 36 and the first shaft 18.
  • a series of pawl gear wheels 42 are provided about the first shaft 18 such that these gear wheels 42 may rotate freely and independently about the shaft 18. However, if required these pawl gear wheels 42 may be caused to engage the first shaft 18 and rotate therewith.
  • a further roving magnet 35 is additionally located within the bore 32 in a manner whereby it may travel through only a limited length thereof.
  • the roving magnet 35 is similarly proportioned to the roving magnet 34, allowing each to travel longitudinally or axially within the bore 32.
  • the roving magnets 34 and 35 are arranged such that they cannot pass or overlap one another within the bore 32.
  • the roving magnet 35 has a guide cable 37 attached thereto and extending through the bore 32 therefrom and further through the first end 26 of the first shaft 18.
  • the guide cable 37 extends to an index member 39 to which it is rigidly but adjustably connected.
  • An annular bush 41 is provided within the bore 32 adjacent the first end 26 and through which the guide cable 37 extends. The bush 41 functions similarly to the bush 40.
  • a second shaft 60 is mounted in the casing 16 by way of bearing means, for example single row ball bearing 62 and 64.
  • the ball bearings 62 and 64 are rigidly located in the end portions 24 of the casing 16 and are arranged such that the shafts 18 and 60 are substantially parallel.
  • the second shaft 60 has a first end 66 received and held within the ball bearing 64.
  • a free or second end 68 of the shaft 60 has rigidly located thereabout a bevel gear wheel 70, such that upon rotation of the second shaft 60 the bevel gear 70 also rotates.
  • the second shaft 60 has provided therein a hollow bore.
  • a roving magnet 74 is located within the bore 72 in a manner such that it may travel almost the entire length thereof and the roving magnet 74 is proportioned accordingly.
  • the roving magnet 74 has a guide cable 76 attached thereto and extends through the bore 72 therefrom and through the first end 66 of the second shaft 60.
  • the guide cable 76 extends to the index member 38 to which it is rigidly but adjustably connected.
  • An annular bush 78 is provided within the bore 72 adjacent the second end 66 and projects through a portion of the end portion 24 of the casing 16. The bush 78 acts as a seal and aids in the smooth travel of the guide cable 76, thereby preventing wear of the guide cable 76 and the second shaft 60.
  • a further roving magnet 75 is additionally located within the bore 72 in a manner whereby it may travel through only a limited length thereof.
  • the roving magnet 75 is similarly proportioned to the roving magnet 74, allowing each to travel longitudinally or axially within the bore 72.
  • the roving magnets 34 and 35 are arranged such that they cannot pass or overlap one another within the bore 72.
  • the roving magnet 75 has a guide cable 77 attached thereto and extending through the bore 72 therefrom and further through the second end 68 of the second shaft 60.
  • the guide cable 77 extends to the index member 39 to which it is rigidly but adjustably connected.
  • An annular bush (not shown) is provided within the bore 72 adjacent the second end 68 and through which the guide cable 77 extends. This bush functions similarly to the bush 78.
  • the roving magnets 34, 35, 74 and 75 may be provided in the form of neodymium rare earth magnets although such should not be considered to limit the scope of the present invention.
  • a series of pawl gear wheels 80 are provided about the second shaft 60 such that these gear wheels 80 may rotate freely and independently about the shaft 60. However, if required these pawl gear wheels 80 may be caused to engage the second shaft 60 and rotate therewith.
  • the gear wheels 42 and 80 are housed within the casing 16 in a chamber 84.
  • the chamber is provided with a volume of lubricant (not shown).
  • the casing 16 is arranged on a bicycle such that the bevel gear wheel 30 of the first shaft 18 engages a gear wheel provided on a pedal-crank (not shown). Accordingly, drive imparted by a rider (not shown) through the pedal-crank is transferred to the first shaft 18 which is caused to rotate.
  • the casing 16 preferably covers or encloses the bevel gear wheels 30 and 70.
  • the casing 16 may have appropriate apertures provided therein to allow access thereinto by the gear wheels provided on the pedal-crank and the axle.
  • gear wheels 42 provided on the first shaft 18 engage a complimentary gear wheel 80 on the second shaft 60.
  • a gear wheel pair is comprised of two pawl gear wheels.
  • the relative diameters of the fixed and pawl gear wheels in a pair determine the gear ratio provided by that gear wheel pair. It is envisaged that a number of arrangements with regard to the fixing of the gear wheels relative to their shaft may be utilised. These arrangements are discussed in more detail hereinafter. However, in each arrangement at least one of the gear wheels of each gear wheel pair or ratio is fixedly attached to its shaft whilst the other gear wheel of that pair or ratio is releasably engagable with the shaft about which it is provided.
  • the bevel gear wheel 70 provided on the second end 68 of the second shaft 60 engages a gear wheel provided on an axle of the hub of a rear wheel (not shown). In this manner, drive transferred from the first shaft 18 to the second shaft 60 is in turn transferred to the rear wheel.
  • the engagement of gear wheels 42 and 80 with their shafts 18 and 60 is achieved through positioning of the roving magnets 34 and 74 alongside those gear wheels, which in turn causes pawl members provided in either the shafts 18 and 60, or the gear wheels 42 and 80, to engage, This results in drive from one shaft being transferred through the gear wheels to the other shaft in the chosen gear ratio.
  • the first shaft 18 has provided thereon a gear wheel 100, the gear wheel 100 being divided into a synchro-gear wheel 102 and a partially toothed gear wheel 104.
  • the gear wheel 100 is provided in constant mesh with a complimentary gear wheel 106 provided about the second shaft 60. It is to be understood that whilst only a single gear wheel 100 need be provided, more than one gear wheel 100 may improve efficiency of the gear system 10.
  • the gear wheels 100 and 106 are generally twice the width of gear wheels 42 and 80.
  • the synchro-gear wheel 102 is thinner longitudinally (axially) than the load bearing partially toothed gear wheel 104.
  • the synchro-gear wheel 102 is able to rotate freely about, and with respect to the shaft 18.
  • a biasing means to be discussed hereinafter, is provided between the synchro-gear wheel 102 and the partially toothed gear wheel 104 to facilitate synchronous rotation therein.
  • the partially toothed gear wheel is releasably engageable with the shaft 18 in known manner, as are the gear wheels 42 and 80.
  • the roving magnets 35 and 75 are arranged within the bores 32 and 72 respectively, so as to travel longitudinally (axially) only the length of the gear wheels 100 and 106, respectively, and a short distance into the adjacent end portion 24 of the casing 16.
  • FIGs 2 and 3 there is shown the gear wheels 100 and 106.
  • the partially toothed gear wheel 104 is shown engaged with the shaft 18 and rotating in the direction of arrow A, thereby introducing movement in the direction of arrow B in the gear wheel 106 and shaft 60 to which it is suitably engaged.
  • the synchro-gear wheel 102 is shown behind the partially toothed gear wheel 104 and is held to synchronous rotation therewith by way of a biasing means, for example a spring 108, shown in contracted position in Figure 2 and in extended or flexed position in Figure 3.
  • the spring 108 comprises arms 110 and 112, arm 110 being affixed to the synchro-gear wheel 102 and arm 112 being affixed to the partially toothed gear wheel 104.
  • Both the synchro-gear wheel 102 and gear wheel 106 are provided with regularly spaced constantly meshed teeth, whereas the partially toothed gear wheel 104 has teeth 114 provided thereon at a much greater spacing, thereby not allowing a constant mesh with the teeth of the gear wheel 106.
  • the gear system 10 of the present invention may be provided in a form such that all the gear wheels provided on the driven shaft thereof, for example shaft 60, are fixedly attached thereto and will rotate therewith at all times. It is further envisaged that the two shafts of the gear system 10 may be provided such that half of the gear wheels provided thereabout are fixedly attached thereto and the other half are not. The arrangement would be such that each gear wheel pair has one gear wheel thereof fixedly attached to its shaft at all times. An arrangement of this nature is disclosed in the applicant's co- pending International Patent Application PCT/AU97/00024 (WO 97/26468).
  • the gear wheel pair 100 and 106 are engaged momentarily. Prior to their engagement, the gear wheels 100 and 106 will have been rotating freely with respect to their shafts 18 and 60, respectively. At the moment of engagement the gear wheels 100 and 106 rotate with their shafts 18 and 60, respectively.
  • the synchro-gear wheel 102 and partially toothed gear wheel 104 rotate together in the direction of arrow A through the action of the spring 108 keeping the same asynchronous rotation whilst the tooth 114 of the partially toothed gear wheel 104 is in engagement with the gear wheel 106.
  • the gear wheel 100 rotating to the position shown in Figure 3 in which the tooth 114 of the partially toothed gear wheel 104 is no longer in engagement with the teeth of the gear wheel 106, the partially toothed gear wheel 104 is driven ahead or slips forward, out of sync, with respect to the synchro-gear wheel 102. In this position the spring 108 is flexed or extended.
  • the pawl members 116 associated with the partially toothed gear wheel 104 may disengage thereby allowing the partially toothed gear wheel 104 to return, under the action of the spring 108, to the position shown in Figure 3 and synchronous movement with the synchro-gear wheel 102.
  • gear wheel 100 If only a single gear wheel 100 is provided in a gear system it is required that it be provided at the highest gear ratio in the gear system. If it is not it cannot function to unload all other gear wheel pairs in the gear system as required.
  • a separate activating system may be required for the selection and engagement of the gear wheels 100 and 106.
  • Such separate activating system may be mechanical, magnetic and/or electromagnetic.
  • a programmable logic controller (PLC), computer or engine management system may be utilised to control the appropriate sequence.
  • a mechanism may be provided so as to prevent the gear wheel 104 locking and loading in a toothless region thereof.
  • the locking of the pawl members associated with the partially toothed gear wheel 104 may be provided whereby such are only able to be deployed and engaged with the assistance or synchronisation of the teeth 114 provided thereon. In this manner, the toothless region of the partially toothed gear wheel 104 could not activate locking of the pawl members associated therewith.
  • the appropriate signal whether it be mechanical, magnetic or electromagnetic must be provided and secondly a tooth 114 of the partially toothed gear wheel 104 must be in meshed engagement with the teeth of gear wheel 106.
  • the roving permanent magnets of the gear system 10 described herein previously may be replaced by roving electromagnets or by a series or array of electromagnets. Such electromagnets may be activated to cause engagement of a gear wheel with its shaft as required.
  • the provision of a single electromagnet for each gear wheel, suitably positioned in the shaft or casing, is envisaged as preferable as this results in less moving components.
  • the gear system of the present invention can be incorporated into a chainless drive shaft between the crank and the rear wheel.
  • the system may be fitted with a dual rear bevel gear and a dual direction rear wheel ratchet/roller clutch to provide power during back pedalling.
  • This arrangement allows step pedalling and allows the rider to power forwards by alternately shifting his weight from one foot to the other whilst standing upon the pedals of the bicycle. This arrangement allows power to be maintained while the rider is negotiating rough or otherwise difficult terrain.
  • the gear system may be provided with a rear foot brake.
  • the gear system may be provided with a rear foot brake. It is envisaged that a dual ratchet or full lock pawl arrangement for engagement of the gear wheels would be required for step pedalling or rear foot braking.

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  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Structure Of Transmissions (AREA)

Abstract

L'invention a pour objet un système de roues dentées prévu pour être utilisé dans une boîte de vitesses à prise constante. Ce système se caractérise par une roue dentée unique (100) prévue autour d'un arbre (18) en vue de sa rotation et de sa mise en prise. La roue dentée (100) est divisée dans le sens longitudinal (axial) en deux composants, le premier constituant une roue dentée synchro (102) et le deuxième étant une roue partiellement dentée (104). La roue synchro (102) est en prise constante avec une roue dentée (106) constituant ainsi une paire de roues dentées, tandis que la roue partiellement dentée (104) est en prise avec cette dernière par intermittence au cours de leur rotation. Entre la roue dentée synchro (102) et la roue partiellement dentée (104) au moins un élément de décalage (108) est prévu pour assurer leur rotation asynchrone temporaire.
EP98914710A 1997-04-18 1998-04-17 Systeme de roues dentees et engrenages integrant ces dernieres Withdrawn EP0986712A1 (fr)

Applications Claiming Priority (7)

Application Number Priority Date Filing Date Title
AUPO628797 1997-04-18
AUPO6287A AUPO628797A0 (en) 1997-04-18 1997-04-18 An improved gear system
AUPO8430A AUPO843097A0 (en) 1997-08-05 1997-08-05 Improved gear system
AUPO843097 1997-08-05
AUPP0779A AUPP077997A0 (en) 1997-12-08 1997-12-08 Improvements to gear systems
AUPP077997 1997-12-08
PCT/AU1998/000270 WO1998048199A1 (fr) 1997-04-18 1998-04-17 Systeme de roues dentees et engrenages integrant ces dernieres

Publications (1)

Publication Number Publication Date
EP0986712A1 true EP0986712A1 (fr) 2000-03-22

Family

ID=27157989

Family Applications (1)

Application Number Title Priority Date Filing Date
EP98914710A Withdrawn EP0986712A1 (fr) 1997-04-18 1998-04-17 Systeme de roues dentees et engrenages integrant ces dernieres

Country Status (2)

Country Link
EP (1) EP0986712A1 (fr)
WO (1) WO1998048199A1 (fr)

Families Citing this family (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE19938934A1 (de) * 1999-08-17 2001-04-12 Inst Maschinenelemente Uni Stu Getriebe
FR2806143B1 (fr) * 2000-03-13 2002-06-21 Valeo Dispositif de transmission automatisee a transfert de couple, en particulier pour vehicule automobile
US6978692B2 (en) 2001-03-15 2005-12-27 Valeo Embrayages Automated transmission device with torque transfer, in particular for a motor vehicle
KR100600083B1 (ko) * 2005-03-31 2006-07-18 에이원마린테크 주식회사 동력선용 무단변속기
CN101290043B (zh) * 2008-04-18 2010-06-02 魏家斌 齿轮多级变速装置

Family Cites Families (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CA2137948C (fr) * 1993-12-27 2000-02-01 Eaton Corporation Synchroniseur a auto-amorcage
KR19990077364A (ko) 1996-01-19 1999-10-25 마틴윌리암웨슬리 축과 기어장칙으로 결합하는 기어들을 갖는

Non-Patent Citations (1)

* Cited by examiner, † Cited by third party
Title
See references of WO9848199A1 *

Also Published As

Publication number Publication date
WO1998048199A1 (fr) 1998-10-29

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