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
  • F16H15/48—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
• • 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
  • F16H15/02—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
  • F16H15/06—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
• • 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.
• 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 position of the satellite relative to the inner surfaces of the bells is adjusted by sliding the satellite relative to these surfaces, perpendicular to its direction of rotation.
• the control means of the position of the satellite must overcome a frictional force between the satellite and the internal surfaces of the bells. To avoid overly stressing these control means, it is therefore appropriate that this friction force is relatively low.
• it is important to limit the slip between the input and output elements that is to say to work with a relatively high coefficient of friction between this satellite and these surfaces.
• the invention intends to respond more particularly by proposing a new continuously variable transmission device whose transmission ratio can be adjusted rapidly, with less effort and less wear. that in the known materials, while limiting the number of parts of the 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 satellite is pivotable about a fifth axis parallel to the first radial plane and perpendicular to the third axis.
• the change in the ratio of the input and output speeds of the device can be obtained by a change in the angular position of the satellite resulting not from a direct sliding of the satellite on the inner surfaces of the driving bells. and conducted but its pivoting around the fifth axis.
• the control force required to change the speed ratio of the device according to the invention is less than that required in the known drives of DE-A-10 2006 016 955 and FR-A-2 173 528. Of this In fact, the wear of the device is lower and the speed ratio changes are faster than with these known variators.
• such a device may incorporate one or more of the following features taken in any technically permissible combination:
• the angular position of the satellite around the fourth axis is adjustable by a primary switchover of the satellite around the fifth axis, this primary switching inducing a secondary tilting of the satellite around the fourth axis.
• the secondary tilting of the satellite is induced by its primary tilting creating resulting forces, producing a pivoting torque, and by the fact that the inner surfaces of the bells are left and the bells are rotating.
• Control means of the angular position of the satellite about the fifth axis act on the satellite by pivoting about a fifth axis, orienting the bands of the satellite relative to the inner surfaces of the bells by a primary tilt inducing a tilting secondary satellite around the fourth axis.
• the satellite is free to rotate about the fourth axis and the fifth axis, while a differential torque created between the driving bell and the driven bell acts on the satellite by rotating it around the fifth axis, orienting the bands. of the satellite relative to the inner surfaces of the bells by a primary tilt which induces a secondary tilting of the satellite around the fourth axis.
• the two bells are rotatably mounted on the same fixed shaft whose longitudinal axis is parallel to the first axis, while the satellite is pivotally mounted on the shaft, around the fourth axis.
• the driving bell is integral with a driving shaft
• the driven bell is integral with a driven shaft
• the device comprises a housing for holding and guiding the rotation of the driving bell, the driven bell and the satellite
• the device then advantageously comprises a satellite carrier which defines the position of the third axis and which is pivotally mounted around the fourth axis and around the fifth axis relative to the housing.
• This carrier can be mounted in the housing by a finger joint connection.
• a control finger of the ball joint is driven in translation in a plane perpendicular to the fifth axis and including the third axis.
• the carrier is mounted in the housing by a double pivot connection comprising a first pivot connection around the fourth axis, this first pivot connection being free to rotate, and a second pivot connection around the fifth axis, this second pivot connection. being rotated.
• 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; there is indicated in II the sectional plane of Figure 1; - 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;
• FIG. 5 is a section similar to FIG. 3 when the satellite has reached a position that is offset from that of FIG. 3,
• Figures 6 and 7 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. 8 is a section similar to FIG. 6 when the satellite has reached a position that is offset from that of FIG. 6,
• 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;
• FIGS. 15 and 16 are sections similar respectively to FIGS. 9 and 10 in a fourth configuration of use of the device; in XV-XV and XVI-XVI the corresponding sectional plans were indicated;
• FIGS. 17 and 18 are sections similar respectively to FIGS. 9 and 10 in a fifth configuration of use of the device; in XVII-XVII and XVIII-XVIII the corresponding sectional planes were indicated;
• Figure 19 is a section similar to Figure 1 for a device according to a third embodiment of the invention.
• FIG. 20 is a section along the X-X plane in Figure 19; it was indicated in XIX-XIX the cutting plane of Figure 19 and
• Figure 21 is a view similar to Figure 6 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 integral in rotation with a pinion 8 intended 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 attachment of 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. 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 respectively 214 and 216 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 in which are partially received balls 218 and springs 219.
• the surface 214 is also provided with hollow recesses 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 housing adjacent to 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 dilate the satellite 20, that is to say axially move the rings 204 and 206 away from each other and increase the intensity of the contact force between the strip 205 and the surface S4 and between the web 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 bearing 209 and a first part of a ball joint 223 immobilized inside the jacket 222.
• a second portion of ball 123 is immobilized on the shaft 10 by means of a screw 124.
• a needle cage constitutes the rolling body bearing 209 and allows the rotation of the satellite 20 around the axis X20, while the shaft 10 and the ball are fixed in rotation with respect 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 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 volume.
• internal device 2 that is to say, the sum of volumes V4 and V6. Outside this volume, the cable 50 passes through a plug 60 through an orifice 602 which opens radially outwards.
• 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 2, and a traction force E50 transmitted by the cable 50 when we shoot at it.
• E40 and E50 are exerted along the main directions of the spring and the cable, in the vicinity of their ends 402 and 502. For clarity of the drawing, the arrows representing these forces are shifted laterally to Figures 2, 4 and 7.
• the satellite 20 is free to pivot about an axis Y20 perpendicular to the plane of Figure 1, that is to say a radial plane with respect to the axis X4 which contains the contact areas Z4 and Z6.
• the satellite can take, relative to the bells 4 and 6, the positions respectively shown in Figures 1, 5 and 8.
• the zones Z4 and Z6 extend at the same radial distance from the axes X4 and X6.
• the transmission ratio of the rotational movement between the bells 4 and 6 is equal to 1.
• zone Z4 is further radially from axis X4 than zone Z6 is remote from axis X6.
• the reduction ratio of the device 2 is maximum.
• the bell 6 rotates faster than the bell 4.
• the speed transmission ratio of the rotational movement between the bells 4 and 6 is greater than 1
• the axis X20 forms with the axis X10 a non-zero angle ⁇ in the plane of this figure.
• the satellite 20 switches in the opposite direction to the configuration of FIG. 5.
• the axis X20 forms with the axis X10 an angle ⁇ oriented in opposite direction with respect to the angle ⁇ and practically having the same value.
• the zone Z4 is radially closer to the axis X4 than the zone Z6 is close to the axis X6, so that the transmission ratio of the device 2 is less than 1, in practice at least in the configuration shown in Figure 8.
• the bell 6 rotates slower than the bell 4.
• the satellite 20 is also mobile in rotation, that is to say, pivoting about a fifth axis Z20 which extends, in the plane of Figures 1, 3, 5, 6 and 8, perpendicular to the axis X20.
• the satellite 20 does not tend to change position relative to the bells 4 and 6.
• the position of the zones Z4 and Z6 with respect to the axes X4 and X6 is stable.
• the elastic force E40 overcomes the traction 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 Figure 4 about the axis Z20.
• the satellite 20 remains in the configuration of FIG. 4, to the point where it continues its secondary tilting movement in the direction of the arrow F2, which makes it move from the configuration of Figure 3 to the configuration of Figure 5.
• the driving bell 4 of the continuously variable transmission device 2 is secured to a first shaft 104 which is driven and centered on a first axis X4.
• the led bell 6 is secured to a second shaft 106 centered on a second axis X6.
• the axes X4 and X6 respectively form axes of rotation for the bells 4 and 6.
• a satellite 20 rotates about a third axis X20 included in the plane of FIG. 9, when it is driven by the driving bell 4.
• This satellite 20 comprises two rings 204 and 206 mounted together on a bearing 209
• the rings 204 and 206 may be in one piece.
• a ball portion 223 has a spherical outer surface S223, non-coaxial with the axis X20 which constitutes the central axis of the satellite X20, and a cylindrical internal surface S'223 coaxial with the axis X20.
• the bearing 209 is housed radially inside the surface S'223.
• the bearing 209 and the ball portion 223 together constitute a carrier for the satellite 20 and define the position of the axis X20 with respect to the bells 4 and 6.
• the X4 and X6 axes which are aligned, are offset radially with respect to the axis X20, by a non-zero distance di, as in the first embodiment.
• the rings 204 and 206 bear respectively strips 205 and 207 of contact with the inner surfaces S4 and S6 of the bells 4 and 6.
• a housing 150 is provided around the bells 4 and 6 and the satellite 20.
• This housing 150 consists of two flanges 154 and 156, provided respectively with passage holes of the shafts 104 and 106, and a cylindrical body 158 secured to two flanges.
• a ball portion 153 is immobilized on the internal radial surface of the body 158 and cooperates with the ball portion 223 to allow pivoting of the elements 209 and 223 and the satellite 20 about a fourth axis Y20 perpendicular to the plane of FIGS. 9, 1 1, 13, 15 and 17 and stand with the Y20 axis.
• the elements 209 and 223 and the satellite 20 can also pivot about a fifth axis Z20 included in the plane of Figures 9, 1 1, 13, 15 and 17 and perpendicular to the axis X20.
• the bell 4 is supported by the housing 150 by means of a circular bearing 124 and an axial bearing 134. These bearings are respectively disposed between an outer radial surface 42 of the bell 4 and the cylindrical body 158 and between an axial surface. 44 of the bell 4 and the flange 154.
• the bearings 124 and 134 guide the bell 4 in rotation around the X4 axis.
• two bearings 126 and 136 guide the bell 6 in rotation about the axis X6, with respect to the casing 150.
• the ball formed of the elements 153 and 223 is a finger ball joint. More particularly, this ball comprises a finger or pin 30 engaged in a housing 224 of the portion 223 and which is integral with a piston 42 belonging to a control subassembly 40. There is therefore a free rotation of the elements 153 and 223. relative to each other about the axis Y20, a rotation locked around the axis X20 and a rotation indexed by the finger 30 about the axis Z20. The indexing of the rotation around the axis Z20 is induced by the translation of the finger 30, parallel to the axis X10.
• the control subassembly 40 also comprises a body 44 fixed on the casing 150, in which is disposed the piston 42 and which defines two chambers 46 and 48 each connected to a pipe 52 or 54 supplied with a control fluid, such as oil. Alternatively, air or water may be used as the control fluid.
• a control fluid such as oil. Alternatively, air or water may be used as the control fluid.
• the control subassembly 40 can also be produced by other technical solutions for moving a part in translation such as a rack, a cam, a cable and by other power means such as an electric motor, an electric magnet, a mechanical actuator.
• the piston 42 is in a median position in that in the chambers 46 and 48 have the same volume.
• contact zones Z4 and Z6 defined between the strips 205 and 207, on the one hand, and the inner surfaces S4 and S6 of the bells 4 and 6, on the other hand, are located substantially at the same radial distance from the axes X4 and X6.
• the transmission ratio of the device 2 of this second embodiment is equal to 1.
• the piston 42 When it is necessary to increase the transmission ratio of this device 2, the piston 42 is moved towards the bell 6 in the plane of FIG. 12. This is obtained by feeding the chamber 46 with oil to a pressure greater than that present in the chamber 48. This movement of the piston 42 in the direction of the arrow F1 1 has the effect of driving the finger 30 towards the bell 6, which pivots the part 223 of the ball around of the Z20 axis. This creates a primary pivoting or tilting of the satellite 20 in the trigonometric direction, as represented by the arrow F1, in the plane of FIG. 12 about the axis Z20.
• the secondary tilting of the satellite 20 around the axis Y20 continues as long as the satellite 20 is maintained in the tilted position shown in FIG. 12. This makes it possible to reach the configuration of FIG. 13 where the transmission ratio of the device 2 is maximum, while the satellite 20 is in a stable configuration, pivoting about the axis Y20 because the piston 42 has been brought back to a median configuration, with respect to the body 44 of subassembly 40, by balancing the pressures of oil in the chambers 46 and 48. The satellite 20 remains in this configuration as the piston 42 is not displaced relative to the body 44.
• the axes X20 and X4 define between them a non-zero angle.
• the X20 and X4 axes define between them a non-zero angle ⁇ oriented in the opposite direction to the angle ⁇ and having substantially the same value.
• this second embodiment also, an indirect control of the pivoting of the satellite 20 is obtained, thanks to the fact that this satellite is pivoting around of the Z20 axis and that it is controlled in a plane perpendicular to this axis, by means of the subassembly 40.
• the satellite carrier is formed of a first cradle which is housed the bearing 209. This first cradle is in pivot connection Y20 axis with a second cradle. Rotation around the Y20 axis is free. The second cradle is in axis Z20 pivot connection with the casing 150. The rotation around the Z20 axis is indexed by a control block similar to the subassembly 40.
• the bells 4 and 6 are respectively one-piece with the shafts 104 and 106.
• a driving mode similar to that of the first 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 first 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.
• 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 tree 10.
• no cable or piston 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 defined respectively between the strips 205 and 207 of the satellite 20 and the internal surfaces S4 and S6 of the bells 4 and 6.
• 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 therefore exerts on the pin 30 an elastic force E40 comparable to that mentioned for the first two embodiments.
• the part 70 is received inside a housing 103 of the fixed shaft 10, 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 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 causes the satellite 20 to swing in the clockwise direction about the axis Z20, in the direction of the arrow F6 in FIG.
• This primary tilting induces, as in the second embodiment, a secondary tilting around the axis Y20, in the direction of the arrow F7 in FIG.
• 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 piece 70 along the axis X10, inside the housing 104.
• the crank 74, the rod link 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 internal volume of the 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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• 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
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  • 2013-06-20 CN CN201380040402.8A patent/CN104520611A/zh active Pending
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  • 2013-06-20 JP JP2015517775A patent/JP2015521721A/ja active Pending
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  • 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/de not_active Withdrawn
  • 2013-06-20 WO PCT/EP2013/062939 patent/WO2013190067A1/fr active Application Filing

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