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
  • F16H15/00—Gearings for conveying rotary motion with variable gear ratio, or for reversing rotary motion, by friction between rotary members
  • F16H15/02—Gearings for conveying rotary motion with variable gear ratio, or for reversing rotary motion, by friction between rotary members without members having orbital motion
  • F16H15/04—Gearings providing a continuous range of gear ratios
  • F16H15/06—Gearings providing a continuous range of gear ratios in which a member A of uniform effective diameter mounted on a shaft may co-operate with different parts of a member B
  • F16H15/32—Gearings providing a continuous range of gear ratios in which a member A of uniform effective diameter mounted on a shaft may co-operate with different parts of a member B in which the member B has a curved friction surface formed as a surface of a body of revolution generated by a curve which is neither a circular arc centered on its axis of revolution nor a straight line
  • F16H15/36—Gearings providing a continuous range of gear ratios in which a member A of uniform effective diameter mounted on a shaft may co-operate with different parts of a member B in which the member B has a curved friction surface formed as a surface of a body of revolution generated by a curve which is neither a circular arc centered on its axis of revolution nor a straight line with concave friction surface, e.g. a hollow toroid surface
  • F16H15/38—Gearings providing a continuous range of gear ratios in which a member A of uniform effective diameter mounted on a shaft may co-operate with different parts of a member B in which the member B has a curved friction surface formed as a surface of a body of revolution generated by a curve which is neither a circular arc centered on its axis of revolution nor a straight line with concave friction surface, e.g. a hollow toroid surface with two members B having hollow toroid surfaces opposite to each other, the member or members A being adjustably mounted between the surfaces
• • B—PERFORMING OPERATIONS; TRANSPORTING
  • B62—LAND VEHICLES FOR TRAVELLING OTHERWISE THAN ON RAILS
  • B62M—RIDER PROPULSION OF WHEELED VEHICLES OR SLEDGES; POWERED PROPULSION OF SLEDGES OR SINGLE-TRACK CYCLES; TRANSMISSIONS SPECIALLY ADAPTED FOR SUCH VEHICLES
  • B62M9/00—Transmissions characterised by use of an endless chain, belt, or the like
  • B62M9/04—Transmissions characterised by use of an endless chain, belt, or the like of changeable ratio
  • B62M9/06—Transmissions characterised by use of an endless chain, belt, or the like of changeable ratio using a single chain, belt, or the like
• • 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
  • F16H15/00—Gearings for conveying rotary motion with variable gear ratio, or for reversing rotary motion, by friction between rotary members
  • F16H15/48—Gearings for conveying rotary motion with variable gear ratio, or for reversing rotary motion, by friction between rotary members with members having orbital motion
  • F16H15/50—Gearings providing a continuous range of gear ratios
• • 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
  • F16H15/00—Gearings for conveying rotary motion with variable gear ratio, or for reversing rotary motion, by friction between rotary members
  • F16H15/02—Gearings for conveying rotary motion with variable gear ratio, or for reversing rotary motion, by friction between rotary members without members having orbital motion
  • F16H15/04—Gearings providing a continuous range of gear ratios
  • F16H15/06—Gearings providing a continuous range of gear ratios in which a member A of uniform effective diameter mounted on a shaft may co-operate with different parts of a member B
  • F16H15/26—Gearings providing a continuous range of gear ratios in which a member A of uniform effective diameter mounted on a shaft may co-operate with different parts of a member B in which the member B has a spherical friction surface centered on its axis of revolution
  • F16H15/30—Gearings providing a continuous range of gear ratios in which a member A of uniform effective diameter mounted on a shaft may co-operate with different parts of a member B in which the member B has a spherical friction surface centered on its axis of revolution with internal friction surface
• • 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
  • F16H15/00—Gearings for conveying rotary motion with variable gear ratio, or for reversing rotary motion, by friction between rotary members
  • F16H15/02—Gearings for conveying rotary motion with variable gear ratio, or for reversing rotary motion, by friction between rotary members without members having orbital motion
  • F16H15/04—Gearings providing a continuous range of gear ratios
  • F16H15/42—Gearings providing a continuous range of gear ratios in which two members co-operate by means of rings or by means of parts of endless flexible members pressed between the first mentioned members
• • 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
  • F16H15/00—Gearings for conveying rotary motion with variable gear ratio, or for reversing rotary motion, by friction between rotary members
  • F16H15/48—Gearings for conveying rotary motion with variable gear ratio, or for reversing rotary motion, by friction between rotary members with members having orbital motion
  • F16H15/50—Gearings providing a continuous range of gear ratios
  • F16H15/52—Gearings providing a continuous range of gear ratios in which a member of uniform effective diameter mounted on a shaft may co-operate with different parts of another member

Definitions

• the invention relates to a device for continuously variable transmission of a rotational movement.
• Such a device can, for example, be used in the motor or pump industry as well as in the automotive field or, more generally, in the field of mobility.
• continuously variable transmission devices sometimes called “drives” or “CVT” (continuously variable transmission) bring the particular advantage of being able to continuously control the rotational speed of an output shaft, which has an advantage over speed boxes whose reduction ratios are fixed.
• DE-A-10 2006 016 955 and FR-A-2 173 528 disclose variable speed drives in which two bells cooperate with a satellite which bears against the internal surfaces of these bells and whose angular position around a perpendicular and non-secant axis with the axis of rotation of the bells makes it possible to adjust the transmission ratio of this variator.
• the range of forward transmission ratio of the device DE-A-10 2006 016 955 is relatively limited because it corresponds to only half of the possible travel of the satellite on the inner surface of the driving bell.
• the position of the satellite relative to the inner surfaces of the bells is controlled by means of a shaft which must be supported by an outer casing and which must go through a space between the two bells.
• This is relatively complex to implement and the space, which must be provided between the two bells for the passage of the shaft, can limit the angular amplitude of displacement of the satellite on the inner surface of the driving bell, which further reduces the possibilities of variation of the transmission ratio of this device.
• the invention relates to a device for continuously variable transmission of a rotational movement comprising a rotating driving bell around a first axis, a rotating driven bell around a second axis aligned with the first axis and a satellite provided with a first band in contact with an inner surface of the driving bell and a second band in contact with an inner surface of the driven bell, areas of contact between these bands and the inner surfaces of the bells being defined in a same radial first plane relative to the first axis, while the satellite is rotating about a third axis included in the first radial plane and whose angular orientation relative to the first axis defines the transmission ratio of the device and while the satellite is pivoted about a fourth axis perpendicular to the first radial plane and non-intersecting with the first axis.
• the two bells are rotatably mounted on the same fixed shaft whose longitudinal axis is parallel to the first axis
• the satellite is pivotally mounted on the shaft, around the fourth axis
• position control means angular of the satellite around the fourth axis extend in an internal volume of the device, defined between the inner surfaces of the bells, and open out of this device through a volume provided for this purpose in the shaft or between the tree and one of the bells.
• the fixed shaft supports both driving and led bells and the satellite, while facilitating the positioning of the control means of the angular position of the satellite without inducing the creation of a space of large width between the leading and led bells.
• the possibilities of adjusting the angular position of the satellite relative to the inner surfaces of the driving and driven bells remain optimal.
• such a device may incorporate one or more of the following features taken in any technically permissible combination:
• the longitudinal axis of the shaft is aligned with the first axis and shifted relative to the third axis, when the longitudinal axis and the third axis are parallel.
• the longitudinal axis of the shaft is shifted relative to the first axis and aligned with the third axis, when the longitudinal axis and the third axis are parallel.
• the control means act directly on the satellite by rotating about the fourth axis in the first radial plane.
• the satellite is free to rotate about a fifth axis parallel to the first radial plane and perpendicular to the first axis.
• the control means act on the satellite by pivoting it around a fifth axis parallel to the first radial plane and perpendicular to the third axis, orienting the satellite bands with respect to the inner surfaces of the bells by a primary rocking inducing a tilting; secondary satellite around the fourth axis.
• the satellite is free to rotate about the fourth axis and a fifth axis parallel to the first radial plane and perpendicular to the third axis, while a differential torque created between the driving bell and the led bell acts on the satellite while doing so pivoting about the fifth axis, orienting the satellite bands relative to the inner surfaces of the bells by a movement that induces a pivoting of the satellite about the fourth axis.
• the shaft carries a ball on which is articulated the satellite with possibility of pivoting at least about the fourth axis and another axis perpendicular to the fourth axis.
• the satellite carries an indexing member subjected to the action of the control means.
• the indexing member is movable in the first radial plane.
• the indexing member is movable in a second radial plane perpendicular to the first radial plane.
• the control means comprise at least one cable secured to the indexing member and which passes through a housing in the shaft or between the shaft and one of the bells.
• the control means comprise a movable member parallel to the longitudinal axis of the fixed axis shaft, the movable member modifying by its axial displacement the stiffness constant of an elastically deformable element exerting an elastic force on the body of indexing.
• the satellite is bipartite, the first and second bands are respectively integral with a first part and a second part of the satellite and in that the first and second parts of the satellite are movable relative to each other the along the third axis, under the action of a preload mechanism adapted to adjust the contact force between the first and second strips, on the one hand, and the inner surfaces of the bells, on the other hand, depending on the resisting torque of the bell conducted relative to the leading bell.
• the prestressing mechanism comprises a single series of rolling elements arranged between the two parts of the satellite and engaged in the housing of varying depth depending on the circumference of the satellite.
• FIG. 1 is an axial section of a transmission device according to the invention in a first configuration of use
• FIG. 2 is a section on the plane ll-ll in Figure 1; the cutting plane of FIG. 1 is indicated therein;
• Figures 3 and 4 are sections similar respectively to Figures 1 and 2 in a second configuration of use of the device; the corresponding sectional planes have been indicated in III-III and IV-IV;
• Figures 5 and 6 are sections similar respectively to Figures 1 and 2 in a third configuration of use of the device; in V-V and VI-VI the corresponding sectional planes have been indicated;
• FIG. 7 is an exploded section of the device of Figures 1 to 6, in the plane of Figure 1;
• FIG. 8 is a perspective view of part of the satellite of the device of FIGS. 1 to 7;
• Figure 9 is a section similar to Figure 1 for a device according to a second embodiment of the invention.
• FIG. 10 is a section along the plane X-X in Figure 9; IX-IX is indicated therein the sectional plane of FIG. 9.
• Figures 1 1 and 12 are sections similar respectively to Figures 9 and 10, in a second configuration of use of the device, it is indicated in XI-XI and XII-XII corresponding sectional planes. ;
• Figures 13 and 14 are sections similar respectively to Figures 9 and 10 in a third configuration of use of the device; in XIII-XIII and XIV-XIV the corresponding sectional planes have been indicated;
• Figure 15 is a section similar to Figure 1 for a device according to a third embodiment of the invention.
• FIG. 16 is a section on the plane XVI-XVI in Figure 15; the XV-XV sectional plan is shown in Figure 15 and - Figure 17 is a view similar to Figure 5 for a device according to a fourth embodiment of the invention.
• the continuously variable transmission device 2 shown in FIGS. 1 to 8 is intended to transmit a rotational movement between a driving bell 4 and a driven bell 6.
• the driving bell is rotationally integral with a pinion 8 intended to to mesh with a chain not shown
• the led bell 6 is provided with two outer flanges 62 and 64 provided with orifices 66 for hooking the spokes of a cycle wheel.
• the device 2 can be used to drive the rear wheel of a cycle, by means of a chain engaged with the pinion 8.
• X4 is the axis of rotation of the bell 4 and X6 the axis of rotation of the bell 6.
• the X4 and X6 axes are parallel and aligned.
• the bells 4 and 6 are rotatably mounted about a fixed shaft 10, a longitudinal and central axis X10 is parallel to the axes X4 and X6.
• the axis X10 is an axis of symmetry of the shaft 10. In practice, the axes X4, X6 and X10 are merged.
• Bearings 12, 14 and 16 can support the bells 4 and 6 on the shaft 10 with the possibility of rotation.
• a bearing 18 is mounted between the outer surface of the bell 4 and the inner surface of the bell 6, allowing a differentiated rotational movement of these bells, respectively about the axes X4 and X6.
• S4 and S6 respectively denote the interior surfaces of the bells 4 and 6, these surfaces being respectively centered on the X4 and X6 axes.
• the device 2 also comprises a satellite 20 mounted on the shaft 10 with the possibility of rotation about an axis X20.
• the axis X20 and X10 are parallel, the axis X20 is shifted relative to the axis X10 in a direction radial with respect to the axis X10, by a distance d1 which is not zero.
• the satellite 20 comprises two rings 204 and 206 respectively disposed in the internal volume V4 or V6 of a bell 4 or 6 and each provided with a band 205 or 207 intended to be in contact with the inner surface S4 or S6 of the bell adjacent.
• a first contact zone Z4 is defined between the strip 205 and the surface S4, whereas a second contact zone Z6 is defined. in this same plane, between the band 207 and the surface S6.
• the speed transmission ratio of the device 2 depends on the ratio of the distance between the zone Z4 and the axis X10, on the one hand, and the distance between the zone Z6 and the axis X10, on the other hand. The higher this ratio, that is, the further the zone Z4 is from the axis X10, the higher the speed transmission ratio.
• the band 207 is immobilized on the ring 206 by means of pins 208. Similar pins, not visible in the figures, are used to fasten the elements 204 and 205 in rotation. , the elements 207 and 206 and respectively the elements 204 and 205 may be monoblock.
• a bearing 209 is engaged in the inner volume of the rings 204 and 206.
• Note 214 and 216 respectively the surfaces of the rings 204 and 206 which are radial with respect to the axis X20 and oriented towards the other ring.
• the surface 216 is provided with hollow recesses 217, visible in particular in FIG. 8 and in which are partially received balls 218 and springs 219.
• the surface 214 is also provided with recessed housing 220 for partial reception of the balls 218.
• the balls are disposed between the surfaces 214 and 216 and partially engaged in the housings 217 and 220.
• Springs 219 are arranged in the vicinity of the balls 218 and received in housings 221 adjacent the housing 217.
• the relative angular position of the rings 204 and 206 around the axis X20 may vary, in a direction such that the balls 218 move in the housings 217 in the direction of the springs 219.
• this relative angular displacement of the rings 204 and 206 has the effect of axially expanding the satellite 20 , that is to say axially apart the rings 204 and 206 from one another and to increase the intensity of the contact force between the strip 205 and the surface S4 and between the strip 207 and the surface S6.
• the springs 219 exert a return force in the opposite direction of the relative angular displacement between the rings 204 and 206.
• the elements 217 to 220 constitute a preloading mechanism which allows adjusting the contact force between the strips 205 and 207 and the inner surfaces of the bells, as a function of the resistant torque of the driven bell 6 relative to the driving bell 4.
• the balls 218 can be replaced by other rolling elements, such as rollers or needles.
• the geometry of the housings 217 and the position of the springs 218 are adapted.
• the satellite 20 also comprises a jacket 222 arranged radially inside the needle cage 209 and a first portion of a ball 223 immobilized inside the jacket 222. Furthermore, a second portion of ball 123 is immobilized on the shaft 10 by means of a screw 124.
• a needle cage is the bearing 209 which is rolling body and allows the rotation of the satellite 20 about the axis X20, while the shaft 10 and the ball are fixed in rotation relative to the axis X10.
• the offset between the X10 and X20 axes comes from the geometry of the inner portion 123 of the ball which, in the plane of Figure 1, is not symmetrical with respect to the axis X10.
• the outer portion 223 of the ball joint consists of two half-shells which are attached around the portion 123 once it has been immobilized on the shaft 10 by the screw 124. The two half-shells are then held in place by the shirt 222 which plays the role of a hoop.
• the portion 123 is provided with a notch 125 in which opens a pin 30 whose tail 302 is immobilized in the part 223 of the ball, for example screwed in this part.
• a spring 40 is hooked, by a first end 402, into the bore 306 and, by a second end 404, onto the shaft 10. This spring forms an elastically deformable element for returning the pin 30 to its position.
• a cable 50 is hooked, by a first end 502, in the bore 306 and extends to the outside of the device 2.
• the cable 50 passes through a groove 102 formed in the outer surface of the shaft 10, in a direction parallel to the axis X10.
• the cable 50 passes through the groove 102 between the internal volume of the device 2, that is to say the sum of the volumes V4 and V6, and the outside.
• the representation of the cable 50 is interrupted to allow the groove 102 to be viewed.
• This groove is disposed radially inside the bearings 12 and 14, which allows the cable 10 to open out of the device. 2.
• the cable 50 passes through a plug 60 through an orifice 602 which opens radially towards the outside of the device 2.
• the pin 30 is subjected to two opposing forces, namely an elastic traction force E40 exerted by the spring 40, which tends to move it to the left in Figure 1, and a traction force E50 transmitted by the cable 50 when we shoot at it.
• the efforts E40 and E50 are exerted along the main directions of the spring and the cable, in the vicinity of their ends 402 and 502.
• the arrows representing these forces are shifted laterally to Figures 1 and 5.
• the traction force E50 is increased, which has the effect of sliding the head 304 of the pin 30 in the slot 125 to the right in Figure 3, tilting the satellite 20 around the Y20 axis to reach a configuration where the zone Z4 is closer radially to the axis X4 than the zone Z6 is close to the axis X6.
• the reduction ratio of the device 2 is minimum.
• the bell 6 rotates slower than the bell 4.
• the speed transmission ratio of the rotational movement between the bells 4 and 6 is less than 1
• the axis X20 forms with the axis X10 a non-zero angle ⁇ in the plane of FIG. 3.
• the intensity of the effort E50 is greatly reduced, or the cable 50 is released.
• the tensile force E40 tilts the satellite 20 in the opposite direction to the configuration of FIGS. 3 and 4.
• the axis X20 forms with the axis X10 an angle ⁇ oriented in the opposite direction with respect to the angle a and having almost the same value.
• the zone Z4 is radially further from the axis X4 than the zone Z6 is away from the axis X6, so that the transmission ratio of the device 2 is greater than 1, in practice maximum in the configuration shown in Figures 5 and 6.
• the bell 6 rotates faster than the bell 4.
• the position of the satellite 20 with respect to the driving and driven bells 4 and 6 is controlled not in the plane of FIGS. 9, 11 and 13 which contains the contact zones Z4 and Z6 between this satellite and these bells, but in a perpendicular plane shown in Figures 10, 12 and 14.
• the pin 30 of this embodiment has a head 304 engaged in a notch 125 of the inner portion 123 of the ball which extends parallel to the plane of Figures 10, 12 and 14.
• the traction force E50 exerted via the cable 50 balances the elastic traction force E40 exerted by the spring 40 stretched between the head 304 and the fixed shaft 10. Satellite 20 does not tend to change position relative to bells 4 and 6. In other words, the position of zones Z4 and Z6 with respect to axes X4 and X6 is stable.
• the elastic force E40 overcomes the tensile force E50, which creates a pivoting or primary tilting of the satellite 20 in the trigonometric direction as represented by the arrow F1 in the plane of the figure 12 around the axis Z20 defined as in the first embodiment.
• the satellite 20 is maintained in the configuration of FIG. 14 to the point that the secondary tilting of the satellite 20 around the axis Y20 continues in the direction of the arrow F3.
• a driving mode similar to that of the second embodiment is used for the continuously variable transmission device 2, with an action in a radial plane perpendicular to a radial plane containing the contact areas Z4 and Z6 between the satellite 20 and the leading and driven bells 4 and 6.
• This embodiment differs from the previous one in that the axes of rotation X10 and X20 coincide when they are parallel, while the axes of rotation X4 and X6 are axially offset with respect to the X10 and X20 axes by a radial distance d2 that is not zero.
• a direct control, in the plane of the contact zones Z4 and Z6 can be used in a device where the axes of rotation X4 and X6 of the driving and driven bells are radially offset by relative to the longitudinal axis X10 of the fixed shaft 10. The approaches of the first and third embodiments are then combined.
• the cable 50 passes between the shaft and the bell 4.
• this cable can pass between the shaft and the bell 6.
• the cable 50 can pass inside the shaft. tree 10.
• no cable is used to control the positioning of the satellite 20 in the interior volumes V4 and V6 of the bells 4 and 6.
• the pivoting control of the satellite 20, for adjusting the transmission ratio of the continuously variable transmission device 2 is performed in a radial plane containing contact zones Z4 and Z6 respectively defined between the bands 205 and 207 of the satellite 20 and the internal surfaces S4 and S6 of the bells 4 and 6. This control mode is therefore comparable to that of the first embodiment on this aspect.
• An elastically deformable element namely a helical spring 40, is fixed between the head 304 of the pin 30, to which it is fixed by a first end 402, and an axially movable member 70, to which it is fixed by a second end 404.
• the spring 40 thus exerts on the pin 30 an elastic force E40 comparable to that mentioned for the first three embodiments.
• the part 70 is received inside a housing 104 of the fixed shaft 10 which it passes axially, this housing being centered on the axis X10.
• This housing allows translation along the axis X10 of the part 70 but blocks its rotation around X10.
• a control rod 72 connects the part 70 by a helical link to a crank 74 located outside the internal volume of the device 2 which is the sum of the internal volumes V4 and V6 of the bells 4 and 6. It is thus possible, in rotating the crank 74 about the axis X10, as represented by the double arrow F5, axially moving the workpiece 70 along the axis X10. This movement makes it possible to vary the stiffness constant of the spring 40 and, consequently, the intensity of the force E40.
• the satellite 20 is rotatably mounted around the axes Y20 and Z20 defined as in the first embodiment.
• the user wishes to decrease the transmission ratio of the device 2, it increases the driving torque of the driving bell 4.
• the input torque on the driving bell 4 is higher than the output torque on the led bell 6.
• a differential torque is thus created between the bells 4 and 6.
• the satellite is no longer statically balanced.
• the tangential contact force between the band 205 and the surface S4 is greater than the tangential force between the band 207 and the surface S6.
• a moment around the axis Z20 is created, which switches the satellite 20 clockwise around the axis Z20, in the direction of the arrow F6 in FIG. 17. This primary changeover induces, as in FIG.
• the transmission ratio of the device 2 decreases.
• the satellite 20 is in another configuration, in particular a configuration where the transmission ratio is minimal, it is possible to increase this transmission ratio by an inverse phenomenon, by reducing the torque exerted on the driving bell 4.
• the secondary tilting mentioned above takes place against the elastic force E40. It is possible to modify the value of the differential torque from which this tilting can take place, by acting on the stiffness constant of the spring 40, that is to say by moving the part 70 along the axis X10, inside the housing 104.
• the crank 74, the connecting rod 72 and the part 70 thus constitute, with the spring 40, means for controlling the angular position of the satellite 20 around the axis Y20, in the volume internal device 2 constituted by the respective internal volumes V4 and V6 of the bells 4 and 6.
• the invention is explained above and shown in the context of its use in the field of the cycle. However, it is applicable in other fields, in particular those of engines or pumps as well as in the automotive field and, more generally, in the field of mobility.

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

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• 2012
  • 2012-06-21 FR FR1255867A patent/FR2992390B1/fr not_active Expired - Fee Related
• 2013
  • 2013-06-20 US US14/408,412 patent/US9534673B2/en not_active Expired - Fee Related
  • 2013-06-20 CN CN201380040402.8A patent/CN104520611A/zh active Pending
  • 2013-06-20 CA CA2877077A patent/CA2877077A1/fr not_active Abandoned
  • 2013-06-20 CA CA2877076A patent/CA2877076A1/fr not_active Abandoned
  • 2013-06-20 JP JP2015517775A patent/JP2015521721A/ja active Pending
  • 2013-06-20 IN IN10914DEN2014 patent/IN2014DN10914A/en unknown
  • 2013-06-20 EP EP13729764.4A patent/EP2864670A1/fr not_active Withdrawn
  • 2013-06-20 CN CN201380040448.XA patent/CN104508328A/zh active Pending
  • 2013-06-20 WO PCT/EP2013/062849 patent/WO2013190028A1/fr active Application Filing
  • 2013-06-20 EP EP13729969.9A patent/EP2864671A1/fr not_active Withdrawn
  • 2013-06-20 WO PCT/EP2013/062939 patent/WO2013190067A1/fr active Application Filing

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