WO2001027485A1 - Embrayage a galets - Google Patents

Embrayage a galets Download PDF

Info

Publication number
WO2001027485A1
WO2001027485A1 PCT/NZ2000/000200 NZ0000200W WO0127485A1 WO 2001027485 A1 WO2001027485 A1 WO 2001027485A1 NZ 0000200 W NZ0000200 W NZ 0000200W WO 0127485 A1 WO0127485 A1 WO 0127485A1
Authority
WO
WIPO (PCT)
Prior art keywords
improved roller
roller bearing
modulation
engagement
race
Prior art date
Application number
PCT/NZ2000/000200
Other languages
English (en)
Other versions
WO2001027485B1 (fr
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 AUPQ3403A external-priority patent/AUPQ340399A0/en
Priority claimed from AUPQ3669A external-priority patent/AUPQ366999A0/en
Priority claimed from AUPQ5415A external-priority patent/AUPQ541500A0/en
Application filed by Preload International Limited filed Critical Preload International Limited
Priority to AU79740/00A priority Critical patent/AU7974000A/en
Publication of WO2001027485A1 publication Critical patent/WO2001027485A1/fr
Publication of WO2001027485B1 publication Critical patent/WO2001027485B1/fr

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
    • F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
    • F16D41/00—Freewheels or freewheel clutches
    • F16D41/06—Freewheels or freewheel clutches with intermediate wedging coupling members between an inner and an outer surface
    • F16D41/064—Freewheels or freewheel clutches with intermediate wedging coupling members between an inner and an outer surface the intermediate members wedging by rolling and having a circular cross-section, e.g. balls
    • F16D41/066—Freewheels or freewheel clutches with intermediate wedging coupling members between an inner and an outer surface the intermediate members wedging by rolling and having a circular cross-section, e.g. balls all members having the same size and only one of the two surfaces being cylindrical
    • F16D41/067—Freewheels or freewheel clutches with intermediate wedging coupling members between an inner and an outer surface the intermediate members wedging by rolling and having a circular cross-section, e.g. balls all members having the same size and only one of the two surfaces being cylindrical and the members being distributed by a separate cage encircling the axis of rotation
    • 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
    • F16H41/00—Rotary fluid gearing of the hydrokinetic type
    • F16H41/24—Details
    • F16H2041/246—Details relating to one way clutch of the stator

Definitions

  • the present invention relates to an improved roller bearing. More particularly, the improved roller bearing of the present invention is suitable for controlling the engagement of a driven member with an input.
  • Roller bearings or roller clutch bearings including bi-directional roller bearings or roller clutch bearings are known.
  • Bi-directional roller bearings have the advantage over conventional roller bearings of allowing a driven member of a machine to run ahead of an input member, regardless of the relative direction of rotation of the input member to the driven member.
  • the engagement of known roller bearings or roller clutch bearings, including bi-directional roller bearings cannot be controlled or modulated.
  • known roller clutches typically engage to approximately the 80% level very rapidly, with the remaining 20% engagement occurring at a markedly slower rate.
  • an improved roller bearing comprising an inner race, an outer race, a bearing cage, a plurality of bearings, an actuable means for the direct and/or indirect actuable engagement of one or more bearings and/or the bearing cage with the inner and/or outer races and a control means, such that the bearings are rotatably retained by the bearing cage which is interposed between the inner and outer races, the inner and outer races normally rotating independently thereabout, wherein the degree of direct or indirect engagement of the bearings and/or the bearing cage with the inner or outer races by way of the actuable means is controlled by the control means.
  • At least two actuable means for each bearing there are provided at least two actuable means for each bearing.
  • a rotational actuable means for actuable engagement of each bearing with the inner and/or outer race in the direction of rotation of the inner race and a counter-rotational actuable means for actuable engagement of each bearing with the inner and/or outer race in the direction opposite the rotation of the inner race, such that disengagement of both the rotational and counter-rotational actuable means allows the outer race to rotate independently of the inner race and counter-rotate relative to the inner race.
  • engagement of the rotational actuable means and disengagement of the counter rotational actuable means causes the outer race to rotate in conjunction with the inner race and allows the outer race to counter rotate relative to the inner race.
  • engagement of the counter-rotational actuable means and disengagement of the rotational actuable means allows the outer race to rotate relative to the inner race, but prevents the outer race from counter rotating relative to the inner race.
  • the improved roller bearing of the present invention comprises both rotational actuable means, and counter-rotational actuable means.
  • the rotational actuable means and the counter-rotational actuable means are provided in conjunction with alternate bearings.
  • the rotational actuable means are operatively interconnected by way of a synchronising means such that said rotational actuable means move simultaneously.
  • the counter-rotational actuable means are operatively interconnected by way of a synchronising ring such that said counter-rotational actuable means move simultaneously.
  • the or each rotational or counter-rotational actuable means is provided in the form of a pawl, adapted to force the bearing radially outward to engage the outer race.
  • the rotational actuable means comprises a trailing pawl, slidably positioned behind said bearing, relative to the direction of rotation of the inner race and the counter rotational actuable means comprises a leading pawl, slidably positioned in front of said bearing relative to the direction of rotation of the inner race.
  • the synchronising means may be provided in the form of leading and trailing pawl rings, to which the leading and trailing pawls respectively are attached.
  • a circumferential recess is provided about the circumference of the inner race, with the leading and trailing pawls being slidably provided therein.
  • said rings are preferably also slidably provided within the circumferential recess.
  • control means comprises a number of modulation wedges, corresponding to one per pawl, an actuator means and a return means wherein the actuator means actuates the modulation wedges, each of which controls the engagement of one of said leading or trailing pawls with the adjacent bearing, and the return means returns the modulation wedges to an inactive position.
  • control means further comprises a modulation wedge synchronising means by which the movement of the modulating wedges is synchronised.
  • the synchronising means is provided in the form of a synchronising ring to which the modulation wedges are attached.
  • each pawl comprises an engagement surface which extends perpendicularly relative to the circumference of the inner race in which the pawl is provided and at an angle to the axis thereof
  • each modulation wedge has similarly provided an engagement surface which extends perpendicularly relative to the circumference of the inner race in which the pawl is provided and at an angle to the axis thereof said angle being complementary to that of the engagement surface of each pawl, such that movement of the modulation wedge in an axial direction causes the engagement surface thereof to act on the engagement surface of the pawl, thereby causing the pawl to move in a circumferential direction.
  • the engagement surfaces of adjacent leading and trailing pawls are convergent towards the direction of approach of the corresponding modulation wedges, and a resiliently deformable means is provided between adjacent leading and trailing pawls such that, when the engagement surfaces of adjacent modulation wedges act upon the engagement surfaces of adjacent leading and trailing pawls, the resiliently deformable means is compressed, and the pawls are maintained in a retracted position, whilst controlled axial movement of the modulation wedges allows the resiliently deformable means to expand, thereby allowing the pawls to move toward and engage adjacent bearings in a controlled manner.
  • the resiliently deformable means is provided in the form of an arcuate spring plate.
  • the roller bearing In known roller bearings or clutches, once an engagement means comes into contact with a roller bearing, the roller bearing 'grabs' at the engagement means and causes rapid substantial engagement of the bearing or clutch.
  • the control means thereof is adapted to prevent this undesirable characteristic.
  • the engagement surfaces of the modulation wedges prevent a bearing from grabbing at the adjacent leading or trailing pawl and thereby from engaging such to any greater extent than desired.
  • the actuator means comprises an inner shaft, an outer shaft, a roving bullet and at least one actuator rod wherein the inner shaft is provided co-axially within the outer shaft, about which is fixedly provided the inner race, the roving bullet is provided slidably about the inner shaft and is dimensioned to engage the or each actuator rod which extend radially towards the inner shaft through apertures in the outer shaft, the bullet causing the or each actuator rod to move radially outward through the apertures to induce axial movement of the modulation wedges.
  • the actuator means further comprises an actuator ring, wherein the or each actuator rod acts on the actuator ring which in turn induces simultaneous axial movement of the modulation wedges.
  • the actuator ring is of triangular cross section and an outer end of each actuator rod is bevelled in a complementary fashion, such that radial movement of the or each actuator rod induces axial movement of the actuator ring.
  • the actuator ring is of similar outer diameter to the inner race, and is slidably provided about the outer shaft adjacent to said inner race, whilst each modulation wedge is provided with a hook portion, said hook portion being engaged by the actuator ring, causing axial movement of the modulation wedge.
  • the actuator means comprises several actuator rods, equidistantly spaced about the circumference of the outer shaft.
  • the actuation means comprises three actuator rods.
  • both the bullet and an inner end of the or each actuator rod are tapered to facilitate gradual deployment thereof.
  • the bullet may be driven along the inner shaft by wires, or by hydraulic means or similar.
  • the return means comprises a resiliently deformable member that is operatively interconnected with each modulation wedge such that, in the absence of the influence of the actuation means, the modulation wedges retain the pawls in a deactuated position.
  • the resiliently deformable member is provided in the form of a circular spring
  • each modulation wedge further comprises an angled return surface
  • the return means further comprises a plurality of spring seats, each spring seat also comprising an angled return surface, complementary to that of the modulation wedge, wherein the circular spring acts on the spring seats to provide force in a radially inward direction, the angled return surface of each spring seat in turn acting on the angled return surface of each modulation wedge to induce axial movement of such. - 9 - respectively, and the return means returns the modulation wedges to an inactive position.
  • the modulation wedges are distributed about the circumference of the inner race, each modulation wedge being interposed between adjacent pairs of inner and outer lock ramp members.
  • each inner or outer lock ramp member comprises two engagement surfaces, said engagement surfaces extending substantially perpendicularly relative to the circumference of the inner or outer race in which the lock ramp member is provided and at an angle to the axis thereof, and each modulation wedge has provided thereon four engagement surfaces which extend perpendicularly relative to the circumference of the inner and outer races in which the lock ramp members are provided and at an angle to the axis thereof, the angles of the engagement surfaces of each modulation wedge being complementary to those of the four engagement surfaces of the adjacent inner and outer lock ramp members, such that movement of the modulation wedge in an axial direction causes the engagement surfaces thereof to act on the engagement surfaces of the inner and outer lock ramp members, thereby causing the inner and outer lock ramp members to move in a circumferential direction relative to the bearings.
  • each modulation wedge comprises an inner portion and an outer portion, two of the four engagement surfaces being provided on each portion, wherein the two engagement surfaces provided on the inner portion of the modulation wedge are convergent in a first direction and are positioned to engage the engagement surfaces of the inner lock ramp members between which the modulation wedge is interposed, the engagement surfaces of the inner lock ramp members being substantially parallel to the corresponding engagement surface of the inner portion of the modulation wedge, whilst the two engagement surfaces provided on the outer portion of each modulation wedge are convergent in a second direction, substantially opposite to the first direction, and are positioned to engage the engagement surfaces of the outer lock ramp members between which the modulation wedge is interposed, the engagement surfaces of the outer lock - 10 -
  • ramp members being substantially parallel to the corresponding engagement surface of the outer portion of the modulation wedge.
  • each outer lock ramp member are parallel, as are the two engagement surfaces of each inner lock ramp member, whilst the two engagement surfaces of each outer lock ramp member are not parallel to the engagement surfaces of the inner lock ramp member associated with the same bearing, nor parallel to the engagement surfaces of the adjacent outer lock ramp members, but are parallel to the engagement surfaces of the adjacent inner lock ramp members whilst the two engagement surfaces of each inner lock ramp member are parallel to the engagement surfaces of the adjacent outer lock ramp members.
  • the actuator means comprises an inner shaft, an outer shaft, a roving bullet and at least one actuator rod, wherein the inner shaft is provided co-axially within the outer shaft, about which is fixedly provided the inner race, and the roving bullet is provided slidably about the inner shaft and is dimensioned to engage the or each actuator rod which extend radially towards the inner shaft through apertures in the outer shaft, the bullet causing the or each actuator rod to move radially outward through the apertures to induce axial movement of the modulation wedges.
  • the actuator means further comprises an actuator ring, wherein the or each actuator rod acts on the actuator ring which in turn induces simultaneous axial movement of the modulation wedges.
  • radial movement of the or each actuator rod induces axial movement of the actuator ring.
  • the actuator ring is of similar outer diameter to the inner race, and is slidably provided about the outer shaft adjacent to said inner race, whilst each modulation wedge is provided with a hook portion, said hook portion being engaged by the actuator ring, causing axial movement of the modulation wedge.
  • the actuator means comprises several actuator rods, equidistantly spaced about the circumference of the outer shaft.
  • the actuator means comprises three actuator rods.
  • both the bullet and an inner end of the or each actuator rod are tapered to facilitate gradual deployment thereof.
  • the bullet may be driven along the inner shaft by wires, or by hydraulic means or similar.
  • the return means comprises a resiliently deformable member that is operatively interconnected with each modulation wedge such that, in the absence of the influence of the actuation means, the modulation wedges retain the inner and outer lock ramp members in a deactuated position.
  • the resiliently deformable member is provided in the form of a disc spring, provided between the inner or outer race and the actuator ring and attached to the modulation wedges.
  • a transmission system comprising a power input shaft, with a plurality of input gear wheels provided thereabout, a power output shaft, with a plurality of output gear wheels provided thereabout and a plurality of improved roller bearings of the present invention, wherein the input gear wheels are in constant meshed engagement with the output wheels to form one or more gear wheel pairs and the transmission of power between the input shaft and each input gear wheel, or the output shaft and each output gear wheel is mediated by one of said improved roller bearings.
  • the power input shaft of the transmission system is provided in the form of an engine output shaft, with the improved roller bearings mediating the engagement of the input gear wheels therewith. - 12 -
  • Figure 1 is an exploded, partial cutaway view of an improved roller bearing according to a first embodiment
  • Figure 2 is further partial cutaway view of the embodiment of Figure 1 in assembled form
  • Figure 3 is a detailed view of an axial cross section of the embodiment of Figures 1 and 2;
  • Figure 4 is a detailed view of a radial cross section of the embodiment of Figures 1 to 3;
  • Figure 5 is a perspective view of a pawl ring of an improved roller bearing in accordance with a second embodiment of the present invention.
  • Figure 6 is a perspective view of a modulation wedge ring of an improved roller bearing in accordance with a third embodiment of the present invention.
  • Figure 7 is a side cross-sectional view of an improved roller bearing in accordance with a fourth embodiment of the present invention, showing an actuator ring, a plurality of bearings, an inner race, an outer race, a plurality - 13 - of inner lock ramp members, a plurality of outer lock ramp members and a plurality of modulation wedges;
  • Figure 8 is a front view of the plurality of inner and outer lock ramp members, bearings of and modulation wedges of Figure 7, from which other components have been omitted for clarity;
  • Figure 9A is a top view of one of said inner lock ramp members of Figures 7 and 8;
  • Figure 9B is a side view of the inner lock ramp member of Figure 9A;
  • Figure 9C is a side view of one of said outer lock ramp members of Figures 7 and 8;
  • Figure 9D is a top view of the outer lock ramp member of Figure 9C;
  • Figure 10 is a perspective view of the inner and outer lock ramp members, bearings of and modulation wedges of Figure 8;
  • Figure 11A is a front view of the actuator ring of Figure 7;
  • Figure 11 B is a side view of the actuator ring of Figure 11 A;
  • Figure 12A is a side view of a modulation wedge of Figure 7;
  • Figure 12B is a top view of the modulation wedge of Figure 12A;
  • Figure 12C is an end view of the modulation wedge of Figures 12A and B;
  • Figure 12D is a bottom view of the modulation wedge of Figures 12A to C;
  • Figure 13 is a partial cut-away perspective view of a transmission system incorporating an improved roller bearing according to a fifth embodiment of the present invention.
  • Figure 14 is a detailed view of the transmission system of Figure 13.
  • FIGs 1 to 4 there is shown an improved roller bearing 10 comprising an inner race 12, an outer race 14, a bearing cage 16 and a plurality of bearings 18.
  • the bearings 18 are rotatably retained by the bearing cage 16, which is interposed between the inner and outer races 12 and 14, the inner and outer races normally rotating independently thereabout, as shown in Figures 1 and 2.
  • the improved roller bearing 10 further comprises a means for actuable engagement of each bearing 18 with the inner and outer races 12 and 14 in the direction of rotation of the inner race 14, and a means for actuable engagement of each bearing 18 with the inner and outer races 12 and 14 in the direction opposite the rotation of the inner race 14 in the form of trailing and leading pawls 20 and 22 respectively.
  • the improved roller bearing 10 still further comprises a control means in turn comprising a plurality of modulation wedges 21 , an actuation means 24 and a return means 26 wherein the actuation means 24 actuates the modulation wedges 21 , each of which controls the engagement of one of said trailing or leading pawls 20 or 22 with the adjacent bearing 18, and the return means 26 returns the modulation wedges 21 to an inactive position.
  • a control means in turn comprising a plurality of modulation wedges 21 , an actuation means 24 and a return means 26 wherein the actuation means 24 actuates the modulation wedges 21 , each of which controls the engagement of one of said trailing or leading pawls 20 or 22 with the adjacent bearing 18, and the return means 26 returns the modulation wedges 21 to an inactive position.
  • the actuation means 24 comprises an inner shaft 28, an outer shaft 30, a roving bullet 32, three actuator rods 34 and an actuator ring 36.
  • the inner shaft 28 is provided co-axially within the outer shaft 30, about which is fixed the inner race 12.
  • the roving bullet 32 is provided slidably about the inner shaft 28 and is dimensioned to engage inner ends 38 of each of the three actuator rods 34.
  • the actuator rods 34 are equidistantly spaced about the circumference of the outer shaft 30, extending through apertures 40 provided therein radially toward the inner shaft 28. - 1 5 -
  • the roving bullet 32 and the inner ends 38 of each of the actuator rods 34 are tapered, so the coincidence of the roving bullet 32 and the actuator rods 34 causes the latter to move radially outward.
  • the roving bullet 32 of the actuation means 24 may similarly be moved to engage the actuator rods 34 by way of a ball screw, by wires or by hydraulic means.
  • the actuator ring 36 is of substantially identical outer diameter to the inner race 12, and is slidably provided about the outer shaft 30 adjacent to said inner race 12.
  • the actuator ring 36 is of triangular cross section and an outer end 42 of each actuator rod 34 is bevelled in a complementary fashion, such that radial movement of the actuator rods 34 induces axial movement of the actuator ring 36.
  • each modulation wedge 21 is provided with a hook portion 44, said hook portion 44 being engaged by the actuator ring 36, causing simultaneous axial movement of all the modulation wedges 21.
  • each trailing pawl 20 is slidably positioned behind each bearing 18, relative to the direction of rotation of the inner race 12, in a circumferential recess 23 provided in the inner race 14.
  • Each leading pawl 22 is slidably positioned in front of each bearing 18, relative to the direction of rotation of the inner race, in the circumferential recess 23.
  • Each trailing or leading pawl 20 or 22 comprises an engagement surface 46, which extends perpendicularly relative to the circumference of the inner race 12 and at an angle to the axis thereof.
  • Each modulation wedge 21 has similarly provided an engagement surface 48 that extends perpendicularly relative to the circumference of the inner race 2 and at an angle to the axis thereof.
  • the angle of the engagement surface 48 is complementary to that of the engagement surface 46 of each pawl 20 or 22 such that movement of the modulation wedge 21 in an axial direction causes the engagement surface 48 thereof to act on the engagement sur ace 46 of the pawl 20 or 22, thereby causing the pawl 20 or 22 to move in a circumferential direction.
  • the engagement surfaces 46 of adjacent leading and trailing pawls 20 and 18 are convergent towards the direction of approach of the corresponding modulation wedges 21.
  • a resiliently deformable means in the form of a spring plate 50 is provided between adjacent leading and trailing pawls 20 and 18.
  • the spring plate 50 is flattened, and the pawls 20 and 18 are maintained in a retracted position. Controlled axial movement of the modulation wedges 21 , by way of the actuator ring 36 allows the spring plate 50 to resume its arcuate shape, thereby allowing the pawls 20 and 28 to move toward and engage adjacent bearings 18 in a controlled manner.
  • the return means 26 comprises a resiliently deformable member in the form of a circular spring 52, and a plurality of spring seats 54, numbering one spring seat 54 per adjacent pair of trailing and leading pawls 18 and 20.
  • Each spring seat 54 partially receives the circular spring 52, and comprises an angled return surface 56.
  • Each modulation wedge 21 further comprises an angled return surface 58, complementary to that of the spring seat 54 such that the circular spring 52 acts on the spring seats 54 to provide force in a radially inward direction, the angled return surface 56 of each spring seat 54 in turn acting on the angled return surface 58 of each modulation wedge 21 , as can best be seen in Figure 3.
  • Each spring seat 54 further comprises a positioning projection 60, adapted to be located between adjacent leading and trailing pawls 20 and 18, thereby allowing the spring seats 54, and thus the circular spring 52, to move radially whilst rotating in conjunction with the inner race 12.
  • the modulation wedges 21 are maintained in position by the action of the circular spring 52.
  • the circular spring 52 simultaneously bears radially inward on each of the spring seats 54, the angled return surfaces 56 of which act on the angled return surfaces 58 of the modulation wedges 21.
  • the roving bullet 32 When the improved roller bearing 10 is to be engaged, the roving bullet 32 is positioned on the inner shaft 28 to coincide with the inner ends 38 of the actuator rods 34.
  • the roving bullet 32 causes the actuator rods to move radially outward, such that the outer ends 42 thereof act on the actuator ring 36, which in turn acts simultaneously on the hook portions 44 of the modulation wedges 21 , thereby causing their retraction from the trailing and leading pawls 18 and 20. Because the roving bullet 32 is tapered, the degree of radial movement of the actuator rods 34, and thus the degree of axial movement of the actuator ring 36 and modulation wedges 21 can be varied.
  • the spring plate 50 drives such apart, causing such to slide along the circumferential recess 23 in the inner race 12.
  • the trailing 18 or leading 20 pawls will come into contact with their adjacent bearing 16.
  • the trailing pawls 18 engage their adjacent bearings 16.
  • the leading pawls 20 engage their adjacent bearings 16.
  • the modulation wedges 21 are withdrawn, and the pawls 20 or 22 allowed to engage the bearings 16 to an increasing degree, the tendency of the bearings 16 to "grab" the pawls 20 or 22 and completely engage the bi-directional roller bearing 10 is increased.
  • the angled return surfaces 58 thereof act on the angled return surfaces 56 of the spring seats 54, causing such to move radially outward and thereby increasing the tension in the circular spring 52, maintaining the modulation wedges 21 in place.
  • an improved roller bearing (not shown).
  • the improved roller bearing of the second embodiment is substantially similar to the improved roller bearing 10 of the first embodiment, and like numerals denote like parts.
  • each bearing 18 has associated therewith either a trailing pawl 20 or a leading pawl 22 such that adjacent bearings 18 are provided with pawls 20 or 22 of opposite orientation.
  • the trailing pawls 20 are fixed to a trailing pawl ring 62, as can be seen in Figure 5, such that the movement of the trailing pawls 18 is synchronised.
  • the leading pawls 20 are fixed to a leading pawl ring (not shown) such that the movement of the leading pawls is synchronised.
  • the inner race 12 of the improved roller bearing of the second embodiment is split along the circumferential recess 23 to provide first and second inner race portions (not shown).
  • the trailing pawls 20 are provided with a rebate 64 such that they do not interfere with the movement of the leading pawl ring within the circumferential recess 23.
  • the leading pawls 22 are provided with a rebate such that they do not interfere with the movement of the trailing pawl ring 62 within the circumferential recess 23. - 19 -
  • the arrangement of the leading and trailing pawls 20 and 22 of the second embodiment creates pairs of bearings 18 between which are located a pair of leading and trailing pawls 22 and 20, interposed with pairs of bearings 18 between which no pawls are provided.
  • the modulation wedges 21 act on the pairs of pawls as for the improved roller bearing of the first embodiment.
  • an improved roller bearing (not shown).
  • the improved roller bearing of the third embodiment is substantially similar to the improved roller bearing 10 of the first embodiment and the improved roller bearing of the second embodiment, and like numbers denote like parts.
  • each bearing 18 has associated therewith either a trailing pawl 20 or a leading pawl 22 such that adjacent bearings 18 are provided with pawls 20 or 22 of opposite orientation.
  • the arrangement of the leading and trailing pawls 20 and 22 of the third embodiment also creates pairs of bearings 18 between which are located a pair of leading and trailing pawls 22 and 20, interposed with pairs of bearings 18 between which are provided no pawls.
  • the modulation wedges 21 act on the pairs of pawls as for the improved roller bearing of the first embodiment.
  • the pawls 20 and 22 of the improved roller bearing of the third embodiment are not directly interconnected.
  • modulation wedges 21 associated with the trailing pawls 20 are fixed to a trailing wedge ring, such that the movement of the modulation wedges associated with the trailing pawls 18 is synchronised.
  • the modulation wedges 21 associated with the leading pawls 20 are fixed to a leading wedge ring 66 such that the movement of the modulation wedges associated with the leading pawls is synchronised, as can best be seen in Figure 6.
  • the actuator ring 36 is absent from the third embodiment.
  • an improved roller bearing 68 is substantially similar to the improved roller bearing 10 of the first - 20 - embodiment and the improved roller bearings of the second and third embodiments, and like numbers denote like parts.
  • trailing and leading pawls 20 and 22 of the improved roller bearings of the previous embodiments are replaced by a plurality of inner and outer lock ramp members 70 and 72, which comprise the bearing cage 16.
  • a circumferential recess 74 is provided about the inner circumference of the outer race 14.
  • Each outer lock ramp member 72 is partially and slidably received within the circumferential recess 74, being interposed between one of said plurality of bearings 18 and the outer race 14. Further, each inner lock ramp member 70 is partially and slidably received within the recess 23, and is interposed between one of said plurality of bearings 18 and the inner race 12, such that each of said plurality of bearings 18 is interposed between one of said inner lock ramp members 70 and one of said outer lock ramp members 72, as can best be seen in Figure 8.
  • each inner and outer lock ramp member 70 or 72 is provided with a bearing seat 76, adapted to partially receive one of said bearings 18.
  • each bearing seat 76 in turn comprises a ramp portion 78 and a stop portion 80, wherein the stop portion 80 is adapted to limit the circumferential movement of the bearing 18 without causing radial movement of such relative to the lock ramp member 70 or 72, and the ramp portion 78 is adapted to cause the bearing 18 to move radially relative to the lock ramp member 70 or 72.
  • the ramp portion 78 of the bearing seat 76 of each lock ramp member 70 or 72 comprises a sloped portion 82 and a curved portion 84.
  • the sloped portion 82 is interposed between the stop portion 80 and the curved portion 84.
  • the curved portion 84 is of a profile corresponding to a quadrant of a circle of a radius substantially identical to that of the bearings 18. - 21 -
  • the stop portion 80 of the bearing seat 76 of the inner lock ramp member 70 associated with each bearing 18 is substantially aligned with the ramp portion 78 of the outer lock ramp member 72 associated with said bearing.
  • the ramp portion 78 of the bearing seat 76 of the inner lock ramp member 70 associated with each bearing 18 is substantially aligned with the stop portion 80 of the outer lock ramp member 72 associated with said bearing 18. Accordingly, each bearing 18 is retained between the ramp and stop portions 78 and 80 of the bearing seats of the inner and outer lock ramp members associated therewith.
  • the improved roller bearing 68 comprises both means for direct or indirect actuable engagement of a bearing 18 with the inner 12 and/or outer 14 race in the direction of rotation of the inner race 12, and means for direct or indirect actuable engagement of a bearing 18 with the inner 12 and/or outer 14 race in the direction opposite the rotation of the inner race12.
  • a number of the plurality of inner lock ramp members 70 are positioned in the recess 23 such that the ramp portion 78 of the bearing seat 76 is positioned behind the bearing 18, relative to the direction of rotation of the inner race 12 to provide trailing inner lock ramp members 86, as can be seen in Figures 8 and 10.
  • Radially aligned with each trailing inner lock ramp member 86 is one of said plurality of outer lock ramp members 72, positioned in the circumferential recess 74 such that the ramp portion 84 of the bearing seat 76 is positioned in front of the bearing 18 relative to the direction of rotation of the inner race 12 to form a leading outer lock ramp member 88.
  • leading outer lock ramp members 88 and the trailing inner lock ramp members 86 provide a means for the direct or indirect actuable engagement of the bearings 18 with the inner and/or outer races 12 and 14 in the direction of rotation of the inner race 12, as will be discussed subsequently.
  • a number of the plurality of inner lock ramp members 70 are positioned in the recess 23 such that the ramp portion 78 of the bearing seat 76 is positioned in front of the bearing 18, relative to the direction of rotation of the inner race 12 to provide leading inner lock ramp members 90.
  • Radially aligned with each leading - 22 - inner lock ramp member 90 is one of said plurality of outer lock ramp members 72, positioned in the circumferential recess 74 such that the ramp portion 84 of the bearing seat 76 is positioned behind the bearing 18 relative to the direction of rotation of the inner race 12 to form a trailing outer lock ramp member 92.
  • trailing outer lock ramp members 92 and the leading inner lock ramp members 90 provide a means for the direct or indirect actuable engagement of the bearings 18 with the inner and/or outer races 12 and 14 in the direction opposite the rotation of the inner race 12, as will be discussed subsequently.
  • Leading outer lock ramp members 88 are alternated with trailing outer lock ramp members 92 in the recess 74 and, accordingly, trailing inner lock ramp members 86 are alternated with leading inner lock ramp members 90 in the recess 74.
  • control means of the improved roller bearing 58 comprises a number of modulation wedges 21 , corresponding to one per pair of inner and outer lock ramp members 70 and 71.
  • the modulation wedges 21 interposed between adjacent pairs of inner and outer lock ramp members 70 and 72, as can best be seen in Figures 8 and 10.
  • Each inner lock ramp member 70 comprises first and second engagement surfaces 94 and 96, the first engagement surface 94 being located behind the second engagement surface 96 relative to the direction of rotation of the inner race 12.
  • the engagement surfaces 94 and 96 extend substantially perpendicularly relative to the circumference of the inner race 12 in which the inner lock ramp member 70 is provided, and at an angle to the axis thereof, such that the first engagement surface 94 is parallel to the second engagement surface 96.
  • each outer lock ramp member 72 comprises first and second engagement surfaces 98 and 100, the first engagement surface 98 being located behind the second engagement surface 100 relative to the direction of rotation of the inner race 12.
  • the engagement surfaces 98 and 100 extend substantially perpendicularly relative to the circumference of the outer race 12 in which the - 23 - outer lock ramp member 72 is provided, and at an angle to the axis thereof, such that the first engagement surface 98 is parallel to the second engagement surface.
  • the first and second engagement surfaces 98 and 100 of the outer lock ramp member 72 associated with each bearing 18 are not parallel to the first and second engagement surfaces 94 and 96 of the inner lock ramp member 70 associated therewith. Rather, the engagement surfaces 98 and 100 of each outer lock ramp member 72 are parallel to the engagement surfaces 94 and 96 of the inner lock ramp members 70 associated with the bearings 18 adjacent thereto, and the engagement surfaces 94 and 96 of the inner lock ramp member 70 are parallel to the engagement surfaces 98 and 100 of the outer lock ramp members 98 and 100 of the bearings adjacent thereto.
  • Each modulation wedge 21 has provided first, second, third and fourth engagement surfaces 102, 104, 106 and 108, each of which extends perpendicularly relative to the circumference of the inner and outer races 12 and 14 in which the lock ramp members 70 and 72 are provided, and at an angle to the axis thereof.
  • each modulation wedge 21 is positioned to slidably engage the second engagement surface 96 of the inner lock ramp member 72 positioned behind the modulation wedge 21 , relative to the direction of rotation of the inner race 12, and is parallel thereto.
  • each modulation wedge 21 is positioned to slidably engage the first engagement surface 94 of the inner lock ramp member 70 positioned in front of the modulation wedge 21 , relative to the direction of rotation of the inner race 12, and is parallel thereto.
  • each modulation wedge 21 is positioned to slidably engage the second engagement surface 100 of the outer lock ramp member 72 positioned behind the modulation wedge relative to the direction of rotation of the inner race 12, and is parallel thereto. - 24 -
  • each modulation wedge 21 is positioned to slidably engage the first engagement surface 98 of the outer lock ramp member 72 positioned in front of the modulation wedge 21 relative to the direction of rotation of the inner race 12, and is parallel thereto.
  • each modulation wedge 21 of the bi-directional roller bearing 68 comprises a hook portion 44, adapted to engage the actuator ring 36.
  • first and second engagement surfaces 102 and 104 of those modulation wedges 21 positioned immediately in front of one of said leading outer lock ramp members 88 and trailing inner lock ramp members 86 relative to the direction of rotation of the inner race 12 are divergent towards the hook portion 44, whilst the third and fourth engagement surfaces 106 and 108 are convergent towards the hook portion 44.
  • first and second engagement surfaces 102 and 104 of those modulation wedges 21 positioned immediately behind one of said leading outer lock ramp members 88 and one of said trailing inner lock ramp members relative to the direction of rotation of the inner race 12 are convergent towards the hook portion 44, whilst the third and fourth engagement surfaces 106 and 108 are divergent towards the hook portion 44.
  • the return means 26 of the improved roller bearing 68 of the fourth embodiment does not possess a circular spring 52, nor a plurality of spring seats 54. Accordingly, unlike the modulation wedges 21 of the improved roller bearing 10 and the improved roller bearings of the second and third embodiments, the modulation wedges 21 of the improved roller bearing 68 are not provided with an angled return surface 58.
  • the return means 26 comprises a resiliently deformable member in the form of a disc spring 112.
  • the disc spring 112 is interposed between the actuator ring 36 and the outer race 14, and is operatively interconnected with each - 25 - modulation wedge 21 by way of slots 114 provided therein, as can best be seen in Figure 7.
  • the disc spring 112 maintains the improved roller bearing 68 in a freewheeling configuration.
  • the modulation wedges 21 are axially positioned by way of the actuator ring 36 such that the engagement surfaces 102, 104, 106 and 108 bear against the engagement surfaces 94 and 96 of the inner lock ramp members 70, and the engagement surfaces 98 and 100 of the outer lock ramp members 72, to position the ramp portions 78 of the inner and outer lock ramp members 70 and 72 relative to the bearing 18 interposed therebetween in such a manner that the bearing 18 is able to freely rotate.
  • the roving bullet 32 When the improved roller bearing 68 is to be engaged, the roving bullet 32 is positioned on the inner shaft 28 to coincide with the inner ends 38 of the actuator rods 34.
  • the roving bullet 32 causes the actuator rods to move radially outward, such that the outer ends 42 thereof act on the actuator ring 36, which in turn acts simultaneously on the modulation wedges 21 , thereby causing such to move axially relative to the inner and outer lock ramp members 70 and 72.
  • Said axial movement occurs in the direction of the divergence of the first and second engagement surfaces 102 and 104 of the modulation wedges provided immediately in front of the trailing inner lock ramp members 86 relative to the direction of rotation of the inner race 12, and the third and fourth engagement surfaces 106 and 108 of the modulation wedges 21 provided immediately behind the leading outer lock ramp members 88 relative to the direction of rotation of the inner race 12.
  • first and second engagement surfaces 102 and 104 of the modulation wedges 21 provided immediately behind the trailing inner lock ramp members 86 and immediately in front of the leading inner lock ramp members 90, relative to the direction of rotation of the inner race 12, act on the second and first engagement surfaces 96 and 94 thereof respectively, forcing such to move apart within the circumferential recess 23 of the inner race 12.
  • the first and second engagement surfaces 102 and 104 of the modulation wedges 21 provided immediately in front of the trailing inner lock ramp members 86 and immediately behind the leading inner lock ramp members 90, relative to the direction of rotation of the inner race 12, are withdrawn from the second and first engagement surfaces 94 and 96 thereof respectively, allowing the trailing inner lock ramp members 86 and the leading inner lock ramp members 90 to slide towards each other within the circumferential recess 23.
  • the third and fourth engagement surfaces 106 and 108 of the modulation wedges 21 provided immediately in front of the trailing outer lock ramp members 86 and immediately behind the leading outer lock ramp members 90, relative to the direction of rotation of the inner race 12 are withdrawn from the second and first engagement surfaces 96 and 94 thereof respectively, allowing the leading outer lock ramp members 86 and the trailing inner lock ramp members 90 to slide towards each other within the recess 74 of the outer race 14.
  • the third and fourth engagement surfaces 106 and 108 of the modulation wedges 21 act on the second and first engagement surfaces 96 and 94 thereof respectively, forcing such to move apart within the circumferential recess 74 of the outer race 12.
  • the engagement of the improved roller bearing 68 of the present invention may be modulated by controlling the degree of axial movement of the modulation wedges 21.
  • Each bearing 18 first contacts the sloped portion 82 of the ramp portion 78 of each modulation wedge, before encountering the curved portion 84 thereof.
  • the simultaneous actions of the curved portions 84 of the inner and outer lock ramp members 70 and 72 on the bearings 18 drives the inner and outer lock ramp members 70 and 72 radially apart and against the inner and outer races 12 and 14 respectively, increasing the friction load of such until ultimately the outer race 14 rotates in conjunction with the inner race 12.
  • the transmission system 116 comprises a power input shaft, in the form of an engine output shaft 118, a power output shaft 120, seven input gear wheels 122, seven output gear wheels 124 and seven improved roller bearings 68 in accordance with the fourth embodiment
  • the output gear wheels 124 are provided about the power output shaft 120 and are fixed thereto.
  • the output gear wheels 124 are in constant meshed engagement with the input gear wheels 122, which are provided about the engine output shaft 118 such that the transmission of power between each gear wheel 122 and the engine output shaft 118 is mediated by one of said bi-directional roller bearings 68, as is shown in Figure 14.
  • a user controls the engagement of the engine output shaft 118 with the power output shaft 128 by modulating the engagement of the improved roller bearing 68 - 28 - provided in conjunction with the lowest gear. Accordingly, the launch clutch or torque converter of conventional transmission systems are not required. Further the transmission system of the present invention represents a considerable saving of space over conventional systems.

Landscapes

  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Mechanical Operated Clutches (AREA)
  • Rolling Contact Bearings (AREA)

Abstract

Cette invention concerne un embrayage à galets amélioré (10) comprenant un chemin de roulement intérieur (12), un chemin de roulement extérieur (14), une cage de roulement (16), une pluralité de galets (18), un dispositif enclenchable (20) pour l'engagement direct et/ou indirect d'un ou de plusieurs des galets (18) et/ou de la cage de roulement (16) avec les chemins de roulement intérieur et/ou extérieur (12, 14) et des dispositifs de commande (21, 24, 26). Les galets (18) sont maintenus rotatifs dans la cage (16) qui vient s'intercaler entre les chemins de roulement intérieur (12) et extérieur (14). Ces chemins de roulement intérieur (12) et extérieur (14) tournent normalement indépendamment autour des galets (18), cependant que le degré d'engagement direct ou indirect desdits galets (18) et/ou de la cage de roulement (16) avec les chemins de roulement intérieur et extérieur (12, 14) via le dispositif enclenchable (20) est déterminé par les dispositifs de commande (21, 24, 26).
PCT/NZ2000/000200 1999-10-13 2000-10-13 Embrayage a galets WO2001027485A1 (fr)

Priority Applications (1)

Application Number Priority Date Filing Date Title
AU79740/00A AU7974000A (en) 1999-10-13 2000-10-13 Roller clutch

Applications Claiming Priority (6)

Application Number Priority Date Filing Date Title
AUPQ3403A AUPQ340399A0 (en) 1999-10-13 1999-10-13 Improved bi-directional roller bearing
AUPQ3403 1999-10-13
AUPQ3669 1999-10-26
AUPQ3669A AUPQ366999A0 (en) 1999-10-26 1999-10-26 Improved bi-directional roller bearing
AUPQ5415A AUPQ541500A0 (en) 2000-02-03 2000-02-03 Improved bi-directional roller bearing
AUPQ5415 2000-02-03

Publications (2)

Publication Number Publication Date
WO2001027485A1 true WO2001027485A1 (fr) 2001-04-19
WO2001027485B1 WO2001027485B1 (fr) 2001-06-07

Family

ID=27158184

Family Applications (1)

Application Number Title Priority Date Filing Date
PCT/NZ2000/000200 WO2001027485A1 (fr) 1999-10-13 2000-10-13 Embrayage a galets

Country Status (1)

Country Link
WO (1) WO2001027485A1 (fr)

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US10378588B2 (en) 2017-01-19 2019-08-13 Gkn Automotive Limited Retainer for rotating members

Citations (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE2330193A1 (de) * 1973-06-14 1975-01-02 Zahnradfabrik Friedrichshafen Freilaufkupplung
US3972633A (en) * 1975-02-27 1976-08-03 Warn Industries, Inc. Wheel hub assembly
US4817451A (en) * 1987-02-26 1989-04-04 Weismann Peter H Control mechanism for selective engagement of a free wheeling engagement mechanism
GB2245684A (en) * 1990-06-26 1992-01-08 Ford Motor Co Phase change mechanism.
US5145042A (en) * 1989-05-26 1992-09-08 Roger Macpherson Roller clutch
US5178250A (en) * 1990-04-12 1993-01-12 Honda Giken Kogyo Kabushiki Kaisha Roller synchro mechanism
EP0396992B1 (fr) * 1989-05-08 1995-08-23 THK MENT Research Co., LTD. Embrayage du type à contact de roulement

Patent Citations (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE2330193A1 (de) * 1973-06-14 1975-01-02 Zahnradfabrik Friedrichshafen Freilaufkupplung
US3972633A (en) * 1975-02-27 1976-08-03 Warn Industries, Inc. Wheel hub assembly
US4817451A (en) * 1987-02-26 1989-04-04 Weismann Peter H Control mechanism for selective engagement of a free wheeling engagement mechanism
EP0396992B1 (fr) * 1989-05-08 1995-08-23 THK MENT Research Co., LTD. Embrayage du type à contact de roulement
US5145042A (en) * 1989-05-26 1992-09-08 Roger Macpherson Roller clutch
US5178250A (en) * 1990-04-12 1993-01-12 Honda Giken Kogyo Kabushiki Kaisha Roller synchro mechanism
GB2245684A (en) * 1990-06-26 1992-01-08 Ford Motor Co Phase change mechanism.

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US10378588B2 (en) 2017-01-19 2019-08-13 Gkn Automotive Limited Retainer for rotating members

Also Published As

Publication number Publication date
WO2001027485B1 (fr) 2001-06-07

Similar Documents

Publication Publication Date Title
EP0080265B1 (fr) Unité de synchroniseur avec roue dentée pour transmission de couple
US6155395A (en) Transfer case having parallel clutches
US4327821A (en) Automatic locking clutch with sliding clutch ring
US3283611A (en) Positive drive differential
US7779978B2 (en) Selectable mode clutch
US6554113B2 (en) Torque limiting accessory drive assembly
US7036644B2 (en) Torque-transmitting mechanism with latching apparatus
US5103950A (en) Cylindrical roller type two-way clutch
EP0418295B1 (fr) Transmission variable en continu
GB2150239A (en) Freewheel ramp/roller clutch with positive lock-out
US4644824A (en) Epicyclic gear speed change mechanism
JP2022553526A (ja) 電気駆動システムのための２速変速機、およびそのような２速変速機を含む駆動システム
JP6937367B2 (ja) 摩擦クラッチ
DE2723535C3 (de) Überbrückungskupplung fur hydrodynamische Drehmomentwandler
US4557358A (en) Synchronized clutch assembly with selective override for four-wheel drive vehicles
US4645047A (en) Freewheel mechanism
WO2001027485A1 (fr) Embrayage a galets
US3026739A (en) Plural speed driving mechanisms
JPS6160293B2 (fr)
US6024197A (en) Support structure for clutch hub
EP0550971B1 (fr) Engrenages de transmission comportant des éléments de freinage et d'embrayage fixés par une surface ondulée
US6257384B1 (en) Two-way differential clutch
US1846745A (en) Friction clutch device
US3812943A (en) Cam operated friction clutch
GB2253251A (en) Gearbox having friction clutches actuated by rotary camming.

Legal Events

Date Code Title Description
AK Designated states

Kind code of ref document: A1

Designated state(s): AE AG AL AM AT AU AZ BA BB BG BR BY BZ CA CH CN CR CU CZ DE DK DM DZ EE ES FI GB GD GE GH GM HR HU ID IL IN IS JP KE KG KP KR KZ LC LK LR LS LT LU LV MA MD MG MK MN MW MX MZ NO NZ PL PT RO RU SD SE SG SI SK SL TJ TM TR TT TZ UA UG US UZ VN YU ZA ZW

AL Designated countries for regional patents

Kind code of ref document: A1

Designated state(s): GH GM KE LS MW MZ SD SL SZ TZ UG ZW AM AZ BY KG KZ MD RU TJ TM AT BE CH CY DE DK ES FI FR GB GR IE IT LU MC NL PT SE BF BJ CF CG CI CM GA GN GW ML MR NE SN TD TG

AK Designated states

Kind code of ref document: B1

Designated state(s): AE AG AL AM AT AU AZ BA BB BG BR BY BZ CA CH CN CR CU CZ DE DK DM DZ EE ES FI GB GD GE GH GM HR HU ID IL IN IS JP KE KG KP KR KZ LC LK LR LS LT LU LV MA MD MG MK MN MW MX MZ NO NZ PL PT RO RU SD SE SG SI SK SL TJ TM TR TT TZ UA UG US UZ VN YU ZA ZW

AL Designated countries for regional patents

Kind code of ref document: B1

Designated state(s): GH GM KE LS MW MZ SD SL SZ TZ UG ZW AM AZ BY KG KZ MD RU TJ TM AT BE CH CY DE DK ES FI FR GB GR IE IT LU MC NL PT SE BF BJ CF CG CI CM GA GN GW ML MR NE SN TD TG

B Later publication of amended claims
121 Ep: the epo has been informed by wipo that ep was designated in this application
DFPE Request for preliminary examination filed prior to expiration of 19th month from priority date (pct application filed before 20040101)
122 Ep: pct application non-entry in european phase
NENP Non-entry into the national phase

Ref country code: JP