WO2000008357A1 - Technique et dispositif permettant de commander l'engrenement et le desengrenement de roues d'engrenage - Google Patents

Technique et dispositif permettant de commander l'engrenement et le desengrenement de roues d'engrenage Download PDF

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Publication number
WO2000008357A1
WO2000008357A1 PCT/AU1999/000630 AU9900630W WO0008357A1 WO 2000008357 A1 WO2000008357 A1 WO 2000008357A1 AU 9900630 W AU9900630 W AU 9900630W WO 0008357 A1 WO0008357 A1 WO 0008357A1
Authority
WO
WIPO (PCT)
Prior art keywords
rotational direction
actuable engagement
engagement
counter
actuable
Prior art date
Application number
PCT/AU1999/000630
Other languages
English (en)
Inventor
William Wesley Martin
Original Assignee
Preload International Limited
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 AUPP5034A external-priority patent/AUPP503498A0/en
Priority claimed from AUPQ1482A external-priority patent/AUPQ148299A0/en
Application filed by Preload International Limited filed Critical Preload International Limited
Priority to AU51415/99A priority Critical patent/AU5141599A/en
Publication of WO2000008357A1 publication Critical patent/WO2000008357A1/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
    • 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
    • F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
    • F16D41/00—Freewheels or freewheel clutches
    • F16D41/12—Freewheels or freewheel clutches with hinged pawl co-operating with teeth, cogs, or the like
    • F16D41/14—Freewheels or freewheel clutches with hinged pawl co-operating with teeth, cogs, or the like the effective stroke of the pawl being adjustable
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • 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
    • 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
    • F16H63/08—Multiple final output mechanisms being moved by a single common final actuating mechanism
    • F16H63/16—Multiple final output mechanisms being moved by a single common final actuating mechanism the final output mechanisms being successively actuated by progressive movement of the final actuating mechanism
    • F16H63/18—Multiple final output mechanisms being moved by a single common final actuating mechanism the final output mechanisms being successively actuated by progressive movement of the final actuating mechanism the final actuating mechanism comprising cams

Definitions

  • the present invention relates to a method and apparatus for controlling the engagement and disengagement of gear wheels with or from a shaft about which they are provided. More particularly, the method and apparatus of the present invention relates to a substantially mechanical means for controlling the engagement and disengagement of gear wheels with or from a shaft about which they are provided, where the gear wheels are provided with means for actuable engagement in both the rotational and counter-rotational directions.
  • the mechanical means controlling the actuation and deactuation of the or each means for actuable engagement in the rotational direction and the or each means for actuable engagement in the counter-rotational direction comprises a means for the retention of the or each means for actuable engagement in the rotational direction and the or each means for actuable engagement in the counter-rotational direction in a deactuated condition, and a positioning means by which the or each means for actuable engagement in the rotational direction and the or each means for actuable engagement in the counter-rotational direction may be deployed or rendered deployable.
  • the mechanical means for the maintenance of the or each means for actuable engagement in the rotational direction and the or each means for actuable engagement in the counter rotational direction in a deactuated condition is provided in the form of one or more cam rods, the or each cam rod being provided within a hollow shaft about which the gear wheels are arranged.
  • the cam rods rotate in conjunction with the shaft and engage cam rings attached to the means for actuable engagement in the rotational direction and the means for actuable engagement in the counter rotational direction, such that a linear portion of each of the cam rods engages a cam ring attached to one of said means for actuable engagement in the rotational direction or one of said means for actuable engagement in the counter rotational direction and maintains that means in a deactuated position.
  • each cam rod is provided with a positioning means in the form of a ramp portion, the alignment of which with the cam ring causes the means for actuable engagement in the rotational direction or the means for actuable engagement in the counter rotational direction to be actuated.
  • each cam rod is provided with a positioning means in the form of an arcuate recess, the alignment of which with the cam ring renders the means for actuable engagement in the rotational direction or the means for actuable engagement in the counter rotational direction deployable.
  • each cam rod is provided with a positioning means in the form of a ramp portion, the alignment of which with the cam ring causes the means for actuable engagement to be deployed.
  • each gear wheel has provided therewith a number of means for actuable engagement in the rotational direction and/or a number of means for actuable engagement in the counter rotational direction
  • the cam rods associated with the means for actuable engagement in the rotational direction are linked, and the cam rods associated with the means for actuable engagement in the counter rotational direction are linked such that the actuation and deactuation of the means for actuable engagement in the rotational direction is synchronised, as is the actuation and deactuation of the means for actuable engagement in the counter- rotational direction.
  • the cam rings are positioned about an inner circumference of the hollow shaft leaving an axial region thereof vacant.
  • the mechanical means for the maintenance of means for actuable engagement in the rotational direction and the means for actuable engagement in the counter rotational direction in a deactuated condition is provided in the form of a platform portion, the platform portion being provided about a positioning means, the platform portion engaging control arms attached to the means for actuable engagement in the rotational direction and the means for actuable engagement in the counter rotational direction, such that the action of the platform portion on the control arms maintains the means for actuable engagement in the rotational direction and the means for actuable engagement in the counter rotational direction in a deactuated position.
  • the positioning means is provided in the form of the cam rod.
  • the diameter of the cam rod is such that it does not interfere with the control arm.
  • the positioning means is provided in the form of a cam rod
  • the cam rod preferably does not rotate in conjunction with the shaft but is axially movable therealong.
  • each platform portion is rotatably provided about each cam rod.
  • a bearing assembly is provided between each platform portion and cam rod.
  • a ramp portion is provided about each cam rod, adjacent the platform portion.
  • the ramp portion increases in diameter from that of the cam rod, to that of the platform adjacent thereto.
  • the positioning means is provided in the form of a cam rod, where more than one cam rod is provided, the cam rods are arranged telescopically, being deployed and controlled from a single end of the shaft.
  • control arms of the means for actuable engagement in the rotational direction are substantially axially aligned, and the control arms of the means for actuable engagement in the counter-rotational direction are substantially axially aligned, and a single cam rod is provided for each such set of control arms.
  • the mechanical means is provided in the form of a bullet portion of a roving bullet and magnet assembly, said assembly being adapted to traverse at least a portion of the length of the hollow shaft, wherein each means for actuable engagement in the rotational direction or means for actuable engagement in the counter rotational direction has connected thereto a projection which extends radially into the hollow shaft, the action of the bullet portion upon which causes the means for actuable engagement in the rotational direction or means for actuable engagement in the counter rotational direction to be maintained in a deactuated position.
  • the positioning means is provided in the form of a magnet portion of the roving bullet and magnet assembly, wherein the diameter of the magnet portion of the roving bullet and magnet assembly is such that that the projections of the means for actuable engagement in the rotational direction or means for actuable engagement in the counter rotational direction aligned therewith may extend radially into the shaft.
  • each means for actuable engagement in the rotational direction or means for actuable engagement in the counter rotational direction has associated therewith one or more permanent magnets, the action of the magnet portion of the bullet and magnet assembly on which causes the means for actuable engagement in the rotational direction or means for actuable engagement in the counter rotational direction to be deployed.
  • the magnet portion of the bullet and magnet assembly is interposed between first and second bullet portions thereof.
  • the projections associated with the means for actuable engagement in the rotational direction are axially offset relative to the projections associated with the means for actuable engagement in the counter rotational direction.
  • the projections associated with the means for actuable engagement in the rotational direction are located towards the higher gears of a gear box containing the gear wheels relative to the projections associated with the means for actuable engagement in the counter rotational direction.
  • the axial distribution of the means for actuable engagement in the rotational direction and the means for actuable engagement in the counter- rotational direction along the shaft is such that the spacing between the means for actuable engagement in the rotational direction and the means for actuable engagement in the counter-rotational direction of one gear wheel is equal to the spacing between the means for actuable engagement in the counter-rotational direction of a gear wheel and the means for actuable engagement in the riotataional direction of an adjacent higher gear wheel.
  • the magnet portion of the permanent magnet assembly is of such an axial length that only two adjacent means for actuable engagement in the rotational direction or means for actuable engagement in the counter-rotational direction, may be actuated at any particular time.
  • the mechanical means for the maintenance of means for actuable engagement in the rotational direction and/or means for actuable engagement in the counter-rotational direction in a deactuated position is provided in the form of a barrel assembly provided coaxially within the hollow shaft, the barrel assembly typically spinning in conjunction with the shaft and acting on the means for actuable engagement in the rotational direction and/or means for actuable engagement in the counter-rotational direction to retain such in a retracted state
  • the positioning means is provided in the form of one or more rebates provided in the barrel, which by momentarily retarding or advancing the barrel relative to the shaft, may be positioned to deploy, or at least render deployable, the means for actuable engagement in the rotational direction and/or means for actuable engagement in the counter-rotational direction.
  • the barrel acts on the means for actuable engagement in the rotational direction and/or means for actuable engagement in the counter-rotational direction by way of control arms connected to the means for actuable engagement in the rotational direction and/or means for actuable engagement in the counter- rotational direction.
  • control arms of each means for actuable engagement in the rotational direction and the control arms of each means for actuable engagement in the counter-rotational direction are substantially axially aligned, and a set of corresponding rebates provided in the barrel, thereby ensuring the simultaneous deployment and retraction of the means for actuable engagement in the rotational direction and/or means for actuable engagement in the counter-rotational direction.
  • the depth of the or each rebate is such that the barrel does not interfere with the control arm when aligned with one of said rebates.
  • the rotation of the barrel within the shaft may be retarded or advanced by mechanical means. In an alternate form of the invention, the rotation of the barrel within the shaft may be retarded or advanced by hydraulic means.
  • the means for actuable engagement in the rotational direction may be provided in the form of one or more forward pawl members, and the means for actuable engagement in the counter-rotational direction in the form of one or more reverse pawl members, wherein the or each forward pawl member is adapted to engage a leading surface of a substantially complimentary recess in an opposed surface positively during rotation of that opposed surface with respect to the pawl member, and the or each reverse pawl member is adapted to engage a trailing surface of a substantially complimentary recess in an opposed surface positively during rotation of that opposed surface with respect to the pawl member.
  • the means for actuable engagement in the rotational direction is provided in the form of one or more forward pawl members
  • the means for actuable engagement in the counter-rotational direction is provided in the form of one or more reverse pawl members
  • the or each forward pawl member is adapted to engage a leading surface of a substantially complimentary recess in an opposed surface positively during rotation of that opposed surface with respect to the pawl member
  • the or each reverse pawl member is adapted to engage a trailing surface of a substantially complimentary recess in an opposed surface positively during rotation of that opposed surface with respect to the pawl member
  • the positioning means is provided in the form of a cam rod, characterised in that each pawl member is pivotally attached to the shaft by way of a first end of said pawl, each control arm is attached to a second end of said pawl.
  • each control arm extends beneath and rearwardly of said pawl such that contact of the control arm with the platform portion maintains the pawl in the retracted position.
  • the or each rebate is shaped to facilitate the gradual deployment and retraction of the pawls.
  • the or each rebate is of gradually increasing depth in a radial direction, to a maximum depth which allows complete deployment of the pawls.
  • the or each means for actuable engagement in the rotational direction, and the or each means for actuable engagement in the counter-rotational direction are provided in the form of a bi-directional roller-clutch.
  • the or each means for actuable engagement in the rotational direction, and the or each means for actuable engagement in the counter-rotational direction are provided in the form of a bi-directional ratchet arrangement.
  • a method for the control of the engagement and disengagement of gear wheels by way of the apparatus having a mechanical means for the maintainence of means for actuable engagement in a deactuated position described herein comprising the steps of: maintaining means for actuable engagement in the rotational direction and/or means for actuable engagement in the counter-rotational direction associated with a particular gear wheel in a position in which they are disengaged or retracted by mechanical means; and
  • Figure 1 is a representation of an axial cross section of an apparatus for controlling the engagement and disengagement of pawl gear wheels in accordance with the present invention, showing in particular the arrangement of active cam rods through a hollow central bore in a shaft;
  • Figure 2 is a representation of a transverse cross section of the apparatus for controlling the engagement and disengagement of pawl gear wheels of Figure 1 , showing in particular forward and reverse pawls alternated about the outer circumference of the shaft, attached to cam rings distributed about the inner circumference thereof;
  • Figure 3a is a representation of a portion of an axial cross section of n apparatus for controlling the engagement and disengagement of pawl gear wheels of Figure 1 , showing in particular the maintenance in a retracted position of a selected pawl by the action of a linear portion of an active cam rod on a cam ring;
  • Figure 3b is a representation of a portion of an axial cross section of the apparatus for controlling the engagement and disengagement of pawl gear wheels of Figure 1 , showing in particular the engagement of a selected pawl by the action of a ramp portion of an active cam rod on a cam ring;
  • Figure 4a is a representation of a portion of an axial cross section of an apparatus for controlling the engagement and disengagement of pawl gear wheels in accordance with a second embodiment of the present invention, showing in particular the maintenance in a retracted position of a selected pawl by the action of a linear portion of a passive cam rod on a cam ring;
  • Figure 4b is a representation of a portion of an axial cross section the apparatus for controlling the engagement and disengagement of pawl gear of Figure 4a, showing in particular the manner in which a particular pawl may be rendered deployable by the positioning of a selected pawl by the positioning of an arcuate recess of a passive cam rod relative to a cam ring;
  • Figure 4c is a representation of a portion of an axial cross section of the apparatus for controlling the engagement and disengagement of pawl gear wheels of Figure 4a, showing in particular a pawl in a deployed position;
  • Figure 5 is a representation of a portion of a transverse cross section of an apparatus for controlling the engagement and disengagement of pawl gear wheels in accordance with a third embodiment of the present invention, showing in particular an actuating member incorporating two permanent magnets pivotally attached to a flange on the inner circumference of a shaft;
  • Figure 6 is a simplified diagrammatic representation of an axial cross section of the apparatus for controlling the engagement and disengagement of pawl gear wheels of Figure 5, depicting only radially opposed forward and reverse pawls, and showing in particular a roving actuating assembly comprising a permanent magnet housing interposed between two bullets adapted to axially traverse a hollow bore through the shaft;
  • Figure 7 is an exploded partial perspective view of an apparatus for controlling the engagement and disengagement of pawl gear wheels in accordance with a fourth embodiment of the present invention, showing in particular a pawl gear wheel provided about a shaft, pivotally provided about which are a set of reverse pawls and a set of forward pawls;
  • Figure 8 is a partial perspective view of an apparatus for controlling the engagement and disengagement of pawl gear wheels in accordance with a fifth embodiment of the present invention.
  • Figure 9 is a is a simplified diagrammatic representation of an axial cross section of an apparatus for controlling the engagement and disengagement of pawl gear wheels in accordance with a sixth embodiment of the present invention, showing in particular a rebate provided within a rotating barrel in turn provided within a shaft; and
  • Figure 10 is a partial radial cross-section of the rebate of Figure 9.
  • FIGS 1 to 3 there is shown an apparatus for controlling the engagement and disengagement of pawl gear wheels 10, comprising a rotatable shaft 12 having a hollow central bore 14. A series of pawl gear wheels 16 are provided about the shaft, such that these pawl gear wheels 16 may rotate freely and independently thereabout.
  • each pawl gear wheel 16 is provided within the shaft 12 and spaced equidistantly about the circumference thereof.
  • a number of forward pawls 18, corresponding to three per pawl gear wheel 16 are interposed between the forward pawls 18 about the circumference of the shaft 12 .
  • the reverse pawls 20 are oriented in the opposite manner to the forward pawls.
  • the forward and reverse pawls 18 and 20 are pivotally attached to the shaft 12 by known means.
  • Provided in the inner surface 22 of each pawl gear wheel 16 are a series of three arcuate recesses 24, each adapted to receive a forward pawl 18.
  • each actuator rod 28 Connected to each of the forward and reverse pawls 18 and 20 are actuator rods 28, each actuator rod 28 extending radially into the hollow bore 14 of the shaft 12 and terminating with a circular cam ring 30. Through each cam ring 30 extends an active cam rod 32, as can best be seen in Figure 1.
  • the active cam rods 32 are substantially cylindrical in cross section, and of diameter smaller than the inner diameter of the cam rings 30 such that the active cam rods 32 may freely pass through the cam rings 30 but such that the active cam rods 32 determine the position of the cam rings 30, and thereby the position of the actuator rods 28 and the forward and reverse pawls 18 and 20.
  • Each active cam rod 32 is largely linear in profile, save for a ramp portion 34.
  • the active cam rods 32 are located within the central bore 14 of the shaft 12 such that a linear portion 36 of each active cam rod 32 passes through a cam ring 30, fixing the position of the cam ring 30 and causing the forward or reverse pawl 18 or 20 to which the cam ring 30 is connected by way of the actuator rod 28 to be held in the retracted position, and such that the ramp portion 34 of the active cam rod 32 is oriented radially outward relative to the shaft 12, as can best be seen in Figure 3a.
  • the forward or reverse pawls 18 or 20 of a particular pawl gear wheel 16 may be deployed by axial movement or the appropriate active cam rods 32 such that the ramp portions 34 thereof become aligned with the associated cam rings 30, thereby causing the cam rings 30 and actuator rods 28 to move radially outward, acting on and causing the deployment of the desired forward or reverse pawls 18 or 20, as best illustrated by Figure 3b.
  • the relevant forward or reverse pawls 18 or 20 engage the corresponding arcuate recesses 24 or 26 in the inner surface 22 of the pawl gear wheel 16, causing such to rotate in conjunction with the shaft 12.
  • the forward or reverse pawls 18 or 20 may be returned to a retracted position by further axial movement of the appropriate active cam rods 32 such that the linear portions 36 thereof become aligned with the cam rings 30, thereby causing the cam rings 30 and actuator rods 28 to move radially inward, acting on and causing the retraction of the desired forward or reverse pawls 18 or 20.
  • the cam rings 30 may be positioned about the circumference 38 of the central bore 14 of the shaft, such that the axial region 40 of the bore remains vacant. It is envisaged that an alternative system for controlling the engagement and disengagement of pawl gear wheels may be situated in this axial region 40, such as that described in our co-pending International Application titled METHOD AND APPARATUS FOR ENGAGING AND DISENGAGING PAWL GEARS, filed contemporaneously with this application and the content of which is herein incorporated by reference, and that the present embodiment may act as an alternative or backup means for controlling the engagement and disengagement of pawl gear wheels.
  • FIG. 4a to 4c there is shown an apparatus for controlling the engagement and disengagement of pawl gear wheels 42 in accordance with a second embodiment of the present invention.
  • the apparatus for controlling the engagement and disengagement of pawl gear wheels 42 is substantially similar to the apparatus for controlling the engagement and disengagement of pawl gear wheels 10 hereinbefore described and like numerals denote like parts, however, the active cam rods 32 are replaced by passive cam rods 44, and the axial region of the central bore 14 of the shaft 12 is occupied by a known apparatus for initiating the deployment and retraction of forward and reverse pawls (not shown), such as that described in our co-pending International Application titled METHOD AND APPARATUS FOR ENGAGING AND DISENGAGING PAWL GEARS, referred to hereinabove.
  • the passive cam rods 44 are substantially cylindrical in cross section, linear in profile, and of diameter smaller than the inner diameter of the cam rings 30 such that the passive cam rods 44 may freely pass through the cam rings 30 but such that the passive cam rods 44 determine the position of the cam rings 30, and thereby the position of the actuator rods 28 and the forward and reverse pawls 18 and 20.
  • the ramp portion 34 of the active cam rods 32 of the apparatus for controlling the engagement and disengagement of pawl gear wheels 10 is replaced by an arcuate recess 46 in the passive cam rods 44 of the apparatus for controlling the engagement and disengagement of pawl gear wheels 42.
  • the passive cam rods 44 are located within the central bore 14 of the shaft 12 such that a linear portion 36 of each passive cam rod 44 passes through a cam ring 30, fixing the position of the cam ring 30 and causing the forward or reverse pawl 18 or 20 to which the cam ring 30 is connected by way of the actuator rod 28 to be held in the retracted position, and such that the arcuate recess 46 of the passive cam rod 44 is oriented radially inward relative to the shaft 12, as can best be seen in Figure 4a.
  • the forward or reverse pawls 18 or 20 of a particular pawl gear wheel 16 may be rendered deployable by axial movement or the appropriate passive cam rods 44 such that the arcuate recesses 46 thereof become aligned with the associated cam rings 30, thereby allowing the cam rings 30 and actuator rods 28 to move radially outward, as can best be seen in Figure 4b.
  • the known apparatus for initiating the deployment and retraction of forward and reverse pawls can then cause the deployment of the desired forward or reverse pawls 18 or 20 by known means, such that they engage the corresponding arcuate recesses 24 or 26 in the inner surface 22 of the pawl gear wheel 16, causing such to rotate in conjunction with the shaft 12, as illustrated by Figure 4c.
  • the forward or reverse pawls 18 or 20 may be retracted, or secured in a retracted position if already retracted by the known means for initiating the deployment and retraction of forward and reverse pawls, by further axial movement of the appropriate passive cam rods 44 such that the linear portions 36 thereof become aligned with the cam rings 30.
  • the cam rings 30 and actuator rods 28 are caused to move radially inward, acting on and causing the retraction of the desired forward or reverse pawls 18 or 20, or if the pawls are already retracted, they are secured in such a position.
  • FIG. 5 and 6 there is shown an apparatus for controlling the engagement and disengagement of pawl gear wheels 48 in accordance with a third embodiment of the present invention.
  • the apparatus for controlling the engagement and disengagement of pawl gear wheels 48 is substantially similar to the apparatus for controlling the engagement and disengagement of pawl gear wheels 10 and 42 hereinbefore described, and like numerals denote like parts.
  • each forward and reverse pawl 18 and 20, and integral with the shaft 12 is an internal flange 50, pivotally attached to which is an actuating member 52, having first and second ends 54 and 56 either side of the point of attachment to the internal flange 50.
  • the flange 50 and actuating member 52 assembly is oriented transversely to the axis of the shaft 12.
  • each actuating member 52 Provided about the first end 54 of each actuating member 52 is a first permanent magnet 58, and provided about the second end 56 of each actuating member 52 is a second permanent magnet 60.
  • the first and second permanent magnets 58 and 60 are arranged about the actuating member 52 such that the magnetic dipole moments are parallel but of opposite direction.
  • the magnets are contained within a magnet housing portion 61 of each actuating member.
  • a projection 62 oriented radially inward relative to the shaft 12.
  • the projection 62 is axially displaced relative to the first and second permanent magnets 58 and 60 within each actuating member 52. As can best be seen in Figure 6, the projections 62 are on the low gear side of the reverse pawls 20, and the high gear side of the forward pawls 18 of each pawl gear wheel 16. The magnet housing portions 61 of the actuating members 62 are situated on the high gear side of the reverse pawls 20 and the low gear side of the forward pawls 18.
  • Th e apparatus for controlling the engagement and disengagement of pawl gear wheels 48 further comprises a roving actuator assembly 66, adapted to traverse the length of the hollow central bore 14 of the shaft 12.
  • the roving actuator assembly 66 in turn comprises high end and low end bullets 68 and 70, interposed between which is a permanent magnet housing 71 , containing a permanent magnet 72.
  • the permanent magnet 72 is fixed within the roving actuator assembly such that its magnetic dipole moment is substantially parallel to the magnetic dipole moments of the first and second permanent magnets 58 and 60 of the actuating member 52, and such that the direction of the magnetic dipole moment is opposite to that of the first permanent magnet 58, and the same as that of the second permanent magnet 60.
  • Both the high end and low end bullets 68 and 70 are substantially circular in transverse cross section, although not of constant diameter. In the intermediate regions 74 of the high end and low end bullets 68 and 70, they are of constant diameter such that the projections 62 on the first ends 54 of the actuating members 52 aligned therewith are forced radially outward, thereby causing the actuating members 52 to draw the relevant forward or reverse pawls 18 or 20 into a retracted position by way of the connector rods 64.
  • the magnet housing portions 61 of each actuating member 52 are proportioned such that whether the actuating member 52 is in a position corresponding to deployed or retracted pawls 18 or 20, the bullets 68 and 70 may freely pass.
  • each of the bullets 68 and 70 are slightly tapered, although the taper occurs over less than the width of an actuating member 52.
  • the diameter of the permanent magnet housing 71 is such that a projection 62 of an actuating member 52 is readily accommodated within the hollow central bore 14, and the axial length of the permanent magnet housing 71 is such that it may encompass the projections 62 of the actuating members 52 associated with the forward and reverse pawls 18 and 20 of a particular gear wheel 16, and the projections 62 of the actuating members 52 associated with either the reverse pawls 20 of an adjacent higher gear wheel, or the forward pawls 18 of an adjacent lower gear wheel.
  • the projections 62 of the actuating members 52 associated with the forward and reverse pawls 18 and 20 of the respective pawl gear wheels are axially distributed along the shaft 12 such that it is possible to position the roving actuator assembly 66 such that only the projections 62 of the actuating members 52 associated with the forward and reverse pawls 18 and 20 of one particular gear wheel are aligned with the permanent magnet housing 71 at a given time.
  • the roving actuator assembly 66 is positioned such that the permanent magnet housing 71 is aligned with the actuating members corresponding to the forward and reverse pawls 18 and 20 of the selected pawl gear wheel 16.
  • the first permanent magnets 58 are attracted to the permanent magnet 72, whilst the second permanent magnets 60 are repelled therefrom, causing the actuating members 52 to pivot about the point of attachment to the internal flanges 50, acting on the connector rods 64 and causing the deployment of the forward and reverse pawls 18 and 20 of the selected pawl gear wheel 16.
  • All other pawl gear wheels 16 are maintained in a disengaged state by the action of the intermediate regions 74 of the high end and low end bullets 68 and 70 on the projections 62 of the actuating members 52 attached to their respective forward and reverse pawls 18 and 20.
  • the roving actuator assembly 66 is moved axially along the hollow central bore 14 toward the selected pawl gear wheel 78. As the roving actuator assembly 66 so moves, the tapered terminus 76 of the low end bullet 70 acts on the projection 62 associated with the reverse pawls 20 of the presently engaged pawl gear wheel 16, causing the gradual retraction of the forward pawl as the intermediate region 74 of the low end bullet 70 is aligned therewith.
  • the forward pawls 18 of the presently engaged pawl gear wheel 16 are unaffected as the intermediate region 74 of the low end bullet 70 may freely pass the magnet housing portion 61 of the actuating member 62 associated with the forward pawls 18 of the presently engaged gear.
  • the forward and reverse pawls 18 and 20 of the selected pawl gear wheel 78 are rendered deployable as the projections 62 associated therewith become aligned with the permanent magnet housing 71.
  • the permanent magnet 72 acts on the first and second permanent magnets 58 and 60 of the actuating member 52 associated with the forward pawls 18 of the selected pawl gear wheel 78, causing the engagement thereof, whilst the bullet 70 acts on the projections 62 associated with the forward pawls 18 of the initially engaged pawl gear wheel 16, causing the retraction thereof.
  • the permanent magnet 72 acts on the first and second permanent magnets 58 and 60 of the actuating member 52 associated with the reverse pawls 20 of the selected pawl gear wheel 78, causing the engagement thereof.
  • FIG. 7 there is shown an apparatus 80 for controlling the engagement and disengagement of pawl gear wheels, in accordance with a fourth embodiment of the present invention.
  • the apparatus 80 is substantially identical to the apparatus 10 and 42 hereinbefore described, and like numerals denote like parts.
  • the apparatus 80 comprises a rotatable shaft 12 having a hollow central bore 14.
  • Pawl gear wheels 16 are provided about the shaft 12, such that the pawl gear wheels 16 may rotate freely and independently thereabout.
  • each pawl gear wheel 16 Provided partially within the shaft 12 and spaced equidistant about the circumference thereof are a number of forward pawls 18, corresponding to three per pawl gear wheel 16. Interposed between the forward pawls 18 about the circumference of the shaft 12 are a number of reverse pawls 20, also corresponding to three per pawl gear wheel 16. The reverse pawls 20 are oriented in the opposite manner to the forward pawls.
  • the forward and reverse pawls 18 and 20 are pivotally attached to the shaft 12 by way of pins 82, provided about first ends 84 thereof.
  • Provided in the inner surface 22 of each pawl gear wheel 16 are a series of three arcuate recesses 24, each adapted to receive a forward pawl 18. Interposed between the arcuate recesses 24 in the inner surface 22 of each pawl gear wheel 18 are three further arcuate recesses 26, each adapted to receive a reverse pawl 20.
  • first and second cam rods 86 and 88 which do not rotate in conjunction with the shaft, but are adapted to move axially therealong.
  • Each cam rod 86 or 88 has rotatably provided thereabout a platform portion 90.
  • bearing assemblies 92 Interposed between the platform portions 90 and the cam rods 86 and 88 are bearing assemblies 92.
  • each cam rod 86 or 88 is a ramp portion 94 of diameter increasing from that of the cam rod 86 or 88 about which it is provided, to that of the platform portion 90.
  • each control arm 96 Connected to each of the forward and reverse pawls 18 and 20 are control arms 96, each control arm 96 extending beneath and rearwardly of second ends 98 of each of the forward and reverse pawls 18 and 20, such that contact of the control arm 96 with the platform portion 90 maintains the pawl 18 or 20 in the retracted position.
  • the diameter of the cam rods 86 and 88 is such that they do not interfere with the control arms 96.
  • control arms 96 of the forward pawls 18 are axially aligned, as are the control arms 96 of the reverse pawls 20.
  • the platform portion 90 of the first cam rod 86 is typically axially aligned with the control arms 96 of the forward pawls 18, the action of the platform portion 90 on the control arms 96 keeping the forward pawls 18 in a retracted state.
  • the platform portion 90 of the second cam rod 88 is typically axially aligned with the control arms 96 of the reverse pawls 20, the action of the platform portion 90 on the control arms 96 keeping the reverse pawls 20 in a retracted state. Accordingly, the pawl gear wheel 16 is able to rotate freely and independently about the shaft 12.
  • the first cam rod 86 When it is desirable to engage, for example, the forward pawls 18 with the pawl gear wheel 16, and thus the pawl gear wheel 16 with the shaft 12, the first cam rod 86 is moved axially along the shaft 12 such that the control arms 96 of the forward pawls come into contact with the ramp portion 94. As the control arms 96 travel along the decreasing diameter of the ramp portion 94, centrifugal forces associated with the rotation of the shaft 12 drive the forward pawls 18 radially outward, enabling such to engage the recesses 24 in the pawl gear wheel 16.
  • the reverse pawls 20 may be selectively deployed by analogous means by way of the second cam rod 88.
  • the first cam rod is again moved axially along the shaft 12, such that the ramp portion 94, then the platform portion 90 act on the control arms 96 thereof, forcing the forward pawls 18 into a retracted position.
  • FIG 8 there is shown an apparatus 100 for controlling the engagement and disengagement of pawl gear wheels, in accordance with a fourth embodiment of the present invention.
  • the apparatus 80 is substantially identical to the apparatus 10, 42 and 80 hereinbefore described, and like numerals denote like parts.
  • the shaft 12 and pawl gear wheels 16 have been omitted from Figure 8 for clarity.
  • Figure 8 shows first, second and third sets 102, 104 and 106 of pawls 18 and 20, each set 102, 104 or 106 corresponding to a pawl gear wheel (not shown).
  • Associated with each set 102, 104 or 106 of pawls 18 and 20 are two cam rods 108, one corresponding to the forward pawls 18 of each set 102, 104 or 106 and one the reverse pawls 18.
  • the cam rods 108 are coaxially arranged within the shaft, being telescopingly provided within one another, such that axial movement thereof is possible.
  • the apparatus 100 is substantially identical to the apparatus 80, with movement of individual cam rods 108 enabling the selective engagement of the forward 18 and/or reverse 20 pawls of each set 102, 104 or 106.
  • cam rods 86, 88 and 108 may be governed by mechanical or hydraulic means or a combination thereof.
  • FIGS 9 and 10 there is shown an apparatus 110 for the engagement and disengagement of pawl gear wheels.
  • the apparatus 110 is substantially similar to the apparatus 10, 42, 48, 80 and 100 and like numbers denote like parts.
  • the hollow central bore 14 of the shaft 12 of the apparatus 110 is largely occupied by a barrel member 112, having provided therein a series of rebates 1 14 adapted to receive the control arms 96 of the forward and reverse pawls 18 and 20, as represented by Figure 9.
  • each pawl 18 or 20 is pivotally attached to the shaft 12 by way of the first end 84 thereof, whilst the control arm 96 is attached to the second end 98 thereof and extends beneath and rearwardly of the pawl 18 or 20, such that outward pressure on the control arms 96 causes the pawl 18 or 20 to be retained in a retraced state.
  • Each rebate 114 comprises a ramp portion 116, as can best be seen in Figure 10, and the maximum depth of each rebate 1 14 is such that the barrel member 112 does not interfere with the control arms 96 when aligned with one of said rebates 114.
  • the forward or reverse pawls 18 or 20 are maintained in a retracted position by way of the action of the barrel member 112 on their respective control arms 96, as the barrel member 112 rotates in conjunction with the shaft 12.
  • momentary retardation or advancement of the barrel member 112 relative to the shaft 12 brings the rebates 114 into alignment with the control arms 96 of the pawls 18 and 20, allowing centrifugal forces to deploy such.
  • Further momentary retardation or advancement of the barrel member 112 causes the ramp portions 1 16 of the rebates 1 14 to act on the control arms 96, causing the retraction of the pawls 18 or 20.
  • rotation of the barrel within the shaft may be retarded or advanced by mechanical or hydraulic means.

Abstract

Cette invention a trait à un dispositif (80) permettant de commander l'engrènement et le désengrènement de roues d'engrenage (16), ces roues (16) étant pourvues toutes deux d'un ou de plusieurs mécanismes (18) permettant un engrènement dans le sens de la rotation et d'un ou de plusieurs mécanismes (20) permettant un engrènement dans le sens inverse de la rotation. Ce dispositif (80) se caractérise par l'existence d'un ou de plusieurs mécanismes mécaniques (86, 88) commandant l'activation et la désactivation des mécanismes (18) d'engrènement dans le sens de la rotation et des mécanismes (20) d'engrènement dans le sens inverse de la rotation.
PCT/AU1999/000630 1998-08-04 1999-08-04 Technique et dispositif permettant de commander l'engrenement et le desengrenement de roues d'engrenage WO2000008357A1 (fr)

Priority Applications (1)

Application Number Priority Date Filing Date Title
AU51415/99A AU5141599A (en) 1998-08-04 1999-08-04 Method and apparatus for controlling the engagement and disengagement of gear wheels

Applications Claiming Priority (4)

Application Number Priority Date Filing Date Title
AUPP5034A AUPP503498A0 (en) 1998-08-04 1998-08-04 Method and apparatus for controlling the engagement and disengagement of gear wheels
AUPP5034 1998-08-04
AUPQ1482 1999-07-07
AUPQ1482A AUPQ148299A0 (en) 1999-07-07 1999-07-07 Method and apparatus for controlling the engagement and disengagement of gear wheels

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Cited By (18)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2000071909A1 (fr) * 1999-05-24 2000-11-30 Select Design Technologies Limited Une transmission
FR2806143A1 (fr) * 2000-03-13 2001-09-14 Valeo Dispositif de transmission automatisee a transfert de couple, en particulier pour vehicule automobile
WO2002036979A1 (fr) * 2000-11-03 2002-05-10 Select Design Technologies Limited Selecteur de tambour et ensemble de transmission associe
WO2002075179A1 (fr) * 2001-03-15 2002-09-26 Valeo Dispositif de transmission automatisee a transfert de couple, en particulier pour vehicule automobile
WO2002099313A1 (fr) * 2001-06-05 2002-12-12 Valeo Dispositif de verrouillage des pignons de transmission
EP1439327A1 (fr) * 2003-01-14 2004-07-21 Raffaele Capuano Boíte de vitesses pour camion
AU2002213666B2 (en) * 2000-11-03 2005-07-07 Select Design Technologies Limited Drum selector and associated transmission assembly
EP2039965A3 (fr) * 2007-09-21 2009-06-10 Honda Motor Co., Ltd. Transmission
EP2169265A3 (fr) * 2008-09-25 2010-04-14 Honda Motor Co., Ltd Transmission à rapports multiples
EP2177786A1 (fr) * 2008-09-25 2010-04-21 Honda Motor Co., Ltd. Transmission à plusieurs étages
EP2258965A1 (fr) * 2008-03-31 2010-12-08 Honda Motor Co., Ltd. Transmission multi-étages
EP2261532A1 (fr) * 2008-03-31 2010-12-15 Honda Motor Co., Ltd. Transmission multi-etages
EP2270367A1 (fr) * 2008-03-31 2011-01-05 Honda Motor Co., Ltd. Transmission multi-etages
DE102010002304B4 (de) * 2009-02-27 2012-10-04 Honda Motor Co., Ltd. Anordnungsstruktur eines Schaltaktuators eines an einem Kraftrad anzubringenden Verbrennungsmotors
DE102010002302B4 (de) * 2009-02-27 2012-10-18 Honda Motor Co., Ltd. Schaltantriebsmechanismus für ein Mehrganggetriebe
US8474346B2 (en) 2008-03-31 2013-07-02 Honda Motor Co., Ltd. Multi-stage transmission
US8549944B2 (en) 2008-03-31 2013-10-08 Honda Motor Co., Ltd. Multi-stage transmission
WO2022074230A1 (fr) * 2020-10-09 2022-04-14 Vcst Industrial Products Bv Actionneur électrique linéaire pour un mécanisme de changement de vitesse

Citations (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US1410347A (en) * 1920-05-03 1922-03-21 George F Pope Change-speed gearing
EP0508967A1 (fr) * 1991-04-12 1992-10-14 MORBIDELLI S.p.A. Dispositif desmodromique de changement de vitesse

Patent Citations (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US1410347A (en) * 1920-05-03 1922-03-21 George F Pope Change-speed gearing
EP0508967A1 (fr) * 1991-04-12 1992-10-14 MORBIDELLI S.p.A. Dispositif desmodromique de changement de vitesse

Cited By (29)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2000071909A1 (fr) * 1999-05-24 2000-11-30 Select Design Technologies Limited Une transmission
FR2806143A1 (fr) * 2000-03-13 2001-09-14 Valeo Dispositif de transmission automatisee a transfert de couple, en particulier pour vehicule automobile
WO2002036979A1 (fr) * 2000-11-03 2002-05-10 Select Design Technologies Limited Selecteur de tambour et ensemble de transmission associe
AU2002213666B2 (en) * 2000-11-03 2005-07-07 Select Design Technologies Limited Drum selector and associated transmission assembly
WO2002075179A1 (fr) * 2001-03-15 2002-09-26 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
WO2002099313A1 (fr) * 2001-06-05 2002-12-12 Valeo Dispositif de verrouillage des pignons de transmission
US6931956B2 (en) 2001-06-05 2005-08-23 Valeo Locking device with transmission gears
EP1439327A1 (fr) * 2003-01-14 2004-07-21 Raffaele Capuano Boíte de vitesses pour camion
EP2039965A3 (fr) * 2007-09-21 2009-06-10 Honda Motor Co., Ltd. Transmission
EP2261532A1 (fr) * 2008-03-31 2010-12-15 Honda Motor Co., Ltd. Transmission multi-etages
EP2261532A4 (fr) * 2008-03-31 2011-06-01 Honda Motor Co Ltd Transmission multi-etages
US8561492B2 (en) 2008-03-31 2013-10-22 Honda Motor Co., Ltd. Multi-stage transmission
EP2258965A1 (fr) * 2008-03-31 2010-12-08 Honda Motor Co., Ltd. Transmission multi-étages
US8549941B2 (en) 2008-03-31 2013-10-08 Honda Motor Co., Ltd. Multi-stage transmission
EP2270367A1 (fr) * 2008-03-31 2011-01-05 Honda Motor Co., Ltd. Transmission multi-etages
CN101981345A (zh) * 2008-03-31 2011-02-23 本田技研工业株式会社 多级变速器
EP2270367A4 (fr) * 2008-03-31 2011-06-01 Honda Motor Co Ltd Transmission multi-etages
EP2258965A4 (fr) * 2008-03-31 2011-06-01 Honda Motor Co Ltd Transmission multi-étages
US8549944B2 (en) 2008-03-31 2013-10-08 Honda Motor Co., Ltd. Multi-stage transmission
US8549942B2 (en) 2008-03-31 2013-10-08 Honda Motor Co., Ltd. Multi-stage transmission
US8474346B2 (en) 2008-03-31 2013-07-02 Honda Motor Co., Ltd. Multi-stage transmission
US8302501B2 (en) 2008-09-25 2012-11-06 Honda Motor Co., Ltd. Multistage transmission
EP2177786A1 (fr) * 2008-09-25 2010-04-21 Honda Motor Co., Ltd. Transmission à plusieurs étages
EP2169265A3 (fr) * 2008-09-25 2010-04-14 Honda Motor Co., Ltd Transmission à rapports multiples
EP2233784A1 (fr) * 2008-09-25 2010-09-29 Honda Motor Co., Ltd. Transmission à rapports multiples
DE102010002302B4 (de) * 2009-02-27 2012-10-18 Honda Motor Co., Ltd. Schaltantriebsmechanismus für ein Mehrganggetriebe
DE102010002304B4 (de) * 2009-02-27 2012-10-04 Honda Motor Co., Ltd. Anordnungsstruktur eines Schaltaktuators eines an einem Kraftrad anzubringenden Verbrennungsmotors
WO2022074230A1 (fr) * 2020-10-09 2022-04-14 Vcst Industrial Products Bv Actionneur électrique linéaire pour un mécanisme de changement de vitesse

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