EP1735544A1

EP1735544A1 - Motor vehicle gearbox, in particular a twin-clutch gearbox

Info

Publication number: EP1735544A1
Application number: EP05739523A
Authority: EP
Inventors: Roumen Antonov
Original assignee: Antonov Automotive Technologies BV; Antonov Automotive Europe BV
Current assignee: Antonov Automotive Technologies BV; Antonov Automotive Europe BV
Priority date: 2004-03-24
Filing date: 2005-03-11
Publication date: 2006-12-27
Also published as: AR048920A1; WO2005103525A1; US20070180942A1; TW200540035A; CN1957193A; FR2868141B1; FR2868141A1; KR20070009636A; JP2007530881A

Abstract

The inventive gearbox device (200) comprises rotary members (1,2,4,5,15) provided with toothed elements (E2, E4-E7, S12, S34, S57-S7, D1-D3, DC, FC, F6, FR, ST), wherein at least one toothed gear (ST, E2, E4) for transmitting motion between two other rotary members (1, 5; 15, 4), thereby producing a gear ratio, can be selectively connected to a rotary member (4; 2) in order to produce another gear ratio.

Description

"Transmission for the automobile, in particular with double clutch"

The present invention relates to a gearbox for a motor vehicle, in particular but not limited to the type comprising two rotary input means, for example two input shafts, coaxial, and controlled by a double clutch used to select one either of the input trees. Conventionally, a manual or robotic gearbox comprises a row of pairs of pinions carried by two shafts. The transmission ratio is defined by that of the torques which is activated by means of a coupler which is typically a synchronizer. With the current trend of gearboxes with at least six gears, these gearboxes become heavy and very bulky in length. Gearboxes comprising two input shafts exist, in particular for obtaining successive gear changes by limiting the drop in transmitted power. For example, an existing gearbox, for the automobile, comprises two input shafts selected between them by a double clutch and two output shafts each meshing with the two input shafts by several couples selectively activated by mounted couplers on the two output shafts. Such an arrangement requires a distribution device, making it possible to transmit the movement to the wheels, whatever the active output shaft, which considerably increases the gearbox. On the other hand, one of the input shafts is tubular and surrounds the other input shaft which carries its pinions beyond the end of the tubular shaft. This means that the output shafts must also be extended, so that the central input shaft can mesh with the two output shafts; therefore, the box is extended accordingly, which increases its size, weight and price. Such a gearbox cannot be installed in a small vehicle. The object of the invention is to provide a gearbox, compact and light in relation to the number of reports offered. Another object of the invention is to propose a gearbox of reduced axial length. Yet another object of the invention is to propose a double clutch gearbox satisfying at least one of the above aims. An additional aim is to provide a double clutch gearbox that is easy to install in a four-wheel drive vehicle. According to the invention, such a device comprises rotary members carrying toothed members, and is characterized in that at least one toothed reference, among the toothed members, which has a function of movement reference between two rotary members for the production of a transmission ratio, can be selectively coupled with another rotary member for the production of another transmission ratio. The rotary members can be solid or hollow shafts, bells or any other member capable of carrying toothed members. The toothed members can be pinions or crowns or any other member capable of meshing with one another. In the sense of the present invention, the expression "movement reference" means that the movement of a first rotary member rotating around a first axis, is transmitted for gear to the toothed reference member, or "toothed reference" , rotating around a second axis then transmitted by gear through the toothed gear to another rotary member rotating around a third axis which is generally, but not limited to, different from the first axis. In other words, the toothed reference serves as a movement transmission relay, to reverse the direction of movement and / or to allow or facilitate a transmission of movement between two rotary members which are for example relatively distant from one another. Such a toothed gear can be carried by a rotary output member or a rotary input member, to which it is selectively coupled for the production of a transmission ratio. A toothed gear has a function for returning the movement, for example between a rotary input member and an intermediate rotary member or between two intermediate rotary members or between an intermediate rotary member and an output member. The term intermediate rotary member means a rotary member which is neither a rotary input member nor a rotary output member. It can be provided to avoid certain impossibilities of movement, that in its return function, the toothed return is decoupled from the rotary member which carries it. To form a reverse gear, a toothed gear which has a gear function for a gear ratio causing a direction of rotation of a rotary output member, has further, for another gear, a function of reverser for the direction of rotation of said rotary output member. This avoids using an additional pinion having only a reversing function. In particular to gain a degree of freedom in the choice of the staggering of the successive transmission ratios, a toothed gear can comprise a stage pinion having two teeth each meshing with a teeth linked to one of said rotary members. Advantageously, the toothed reference and several other output toothed members are mounted on a rotary output member and each mesh with a respective input toothed member mounted on at least one rotary input member and with a respective intermediate toothed member mounted on an intermediate rotary member, coupling means being provided for carrying out the transmission of the at least one rotary inlet member to the rotary outlet member, directly or selectively via the toothed gear and the intermediate rotary member. Thus, the toothed reference allows a report to be made and the several other output toothed members make it possible to each carry out two reports. The gearbox is significantly shortened. To limit the length of the rotary members, and therefore of the gearbox, two intermediate rotary members can be used. Thus, the at least one toothed reference can comprise a second toothed reference mounted on a rotary input member between an output toothed member and an intermediate toothed member mounted on a second intermediate rotary member driven from the rotary member d 'Entrance. At least one of the toothed members which can be selectively coupled with a rotary member for the production of a transmission ratio is a toothed transfer member which can have a proportional transfer function for the transmission ratios to a rotary member of transmission. transfer used for transmitting movement to at least one axle. Thus, it is possible to position a gearbox output pinion on a shaft which is better disposed relative to the engine, in particular allowing easier two-axle transmission for a four-wheel drive transmission. Thus, one of the input toothed members which forms part of the at least one toothed reference can either be coupled to the at least one rotary input member to produce a direct relationship between the rotary member of input and the rotary transfer member, or be decoupled to return the movement of the rotary output member to the rotary transfer member. One of the toothed input members can belong to the at least one toothed reference which can either be coupled to the at least one rotary input member to produce a direct relationship between the rotary input member and the rotary output member, or be decoupled to return the movement between an intermediate rotary member and the rotary output member. The input rotary member and an intermediate rotary member can be connected by another pair of teeth, intermeshed and capable of being selectively activated. Advantageously, there can be a direct gear between a toothed member on an intermediate rotary member and a toothed member on the rotary output member for a reverse gear ratio. Advantageously, to limit the reductions in power during gear changes, the at least one rotary input member can comprise two rotary input members which can be alternately and selectively coupled to a motor, one of the rotary members d input causing the toothed return carried by the rotary output member, the other carrying input toothed members which define relationships which alternate with those defined by the intermediate toothed members. For the same purpose, the at least one rotary input member may comprise two rotary input members which can be selectively engaged with the same motor, the change from a transmission ratio to a neighboring transmission ratio comprising an action for engaging at least one of the rotary input members and for disengaging the other rotary input member. The input rotary members can be coaxial. A rotary input member may comprise only a single toothed member meshing with a toothed gear and / or carrying a toothed gear. Advantageously, a device according to the invention may comprise only a single rotary output member, in order to limit the complexity of means for transmitting power at the output of the gearbox. In a particular embodiment, the device according to the invention can comprise: - two direct reports each produced by direct gearing of a first input member with a toothed outlet member, - two first indirect reports produced by a cascade d '' meshes passing through a first toothed gear carried by the rotary output member, - two second indirect reports produced by a cascade of meshes passing through at least one second toothed gear carried by a rotary input body, and, - A ratio produced by direct gearing between the first rotary input member and the first toothed gear coupled with the rotary output member. It may also include an additional ratio produced by direct gear between a rotary input member and the rotary output member, with the same coupler as that used to couple the first toothed gear with the output member. It can comprise two toothed members and a double coupler, that is to say allowing to couple a toothed member or none among the two toothed members, on the at least one rotary input member, on the rotary output member and on each of the two intermediate rotary members. Thus, it suffices to produce eight transmission ratios, for example seven forward and one reverse, of four couplers installed along four axes which are substantially side by side. The axial length of such a box is particularly reduced especially if we consider its large number of reports. In a case where the device comprises two concentric input members, one may be provided meshing with the first intermediate rotary member and carrying the first two toothed members, the other meshing with the first toothed gear and preferably meshing with a another pair of teeth with the rotary output member. Thus, the use of the same toothed member, for example a pinion or a toothed crown, for the production of several reports makes it possible to reduce the number of toothed members necessary for the production of all the reports. Other features and advantages of the invention will emerge from the description below, relating to nonlimiting examples. In the accompanying drawings: FIG. 1 is a schematic representation of a first embodiment for a gearbox device according to the invention, comprising 7 forward gears, mounted on an input shaft, an output shaft and an intermediate shaft; - Figures 2 to 8 schematically represent the operation of the device of Figure 1, for each of the seven reports; - Figure 9 is a schematic representation of a second embodiment, where the seventh forward gear is replaced by a reverse gear, in its operating mode in reverse; - Figure 1 0 schematically shows a third embodiment of the gearbox according to the invention, suitable for a four-wheel drive transmission and where a seventh forward gear is added to the device of Figure 9; - Figures 1 1 and 1 2 illustrate the operation of the device of Figure 10, respectively in the seventh forward gear and in the reverse gear; - Figure 1 3 illustrates another embodiment of the invention, further comprising a second intermediate shaft; - Figure 14 is a view along XIV of the device of Figure 1 3, showing the arrangement of the trees between them and in particular the meshes to form a reverse gear; and, - Figure 1 5 illustrates a variant of the device of Figure 1 3. Figure 1 shows a device 1 00 gearbox comprising two coaxial input shafts, namely a first central shaft 1, and a second shaft xibular 2 mounted free to rotate around the central shaft 1. Each input shaft comprises an input clutch disc 6 of which it is integral in rotation. The discs 6 are mounted in opposition to each other. A drive shaft 3, coaxial with the input shafts 1, 2, comprises a selection disc 7, mounted between the two input discs 6. The selection disc is mounted movable coaxially relative to the input shafts. Thus, the double clutch 8 comprising the three discs can take three positions, a first position (shown in Figure 1, as in Figure 1 0), in which the clutch is disengaged and none of the discs 6,7 , is not in contact with the other, a second position in which the drive shaft 3 is engaged with the first input shaft 1 (illustrated in FIGS. 2, 4 and 6) while being disengaged from the second input shaft 2, and a third position in which the drive shaft 3 is engaged with the second input shaft 2 (shown in FIGS. 3, 5, 7, 8, 9, 1 1 and 1 2) while being disengaged from the first shaft d 'entry 1. The device 1 00 further comprises an output shaft 4 and an intermediate shaft 5 rotatably mounted parallel to the input shafts 1, 2. The output shaft 4 is functionally located between the input shafts 1, 2 d ' on the one hand and the intermediate shaft 5 on the other. The four shafts 1, 2, 4, 5 rotate in fixed positions with respect to each other in a casing, not shown. The output shaft 4 has, relative to the input shafts 1, 2 a center distance h41 smaller than its center distance h45 with the intermediate shaft 5. In the figures, the trees are shown to be coplanar for reasons of clarity. However, to limit and adapt to the space available the size of such a gearbox, the actual arrangement can be "folded" along the axis of the output shaft 4. In the following, we will call "proximal" the side of the gearbox where the clutch 8 is located, therefore the left side in the representation chosen for the figures, and "distal" the opposite side, therefore the right side. The output shaft 4 carries, in order from the proximal side to the distal side: a common transfer pinion TC which meshes with a common intermediate pinion DC secured to the intermediate shaft 5; a sixth gear output gear S6 meshing with a sixth gear input gear E6 secured to the tubular input shaft 2; a third and fourth gear output gear S34 meshing with a third gear input gear E3 carried by the central input shaft 1 beyond the distal end of the tubular input shaft 2, and with an intermediate gear of fourth gear D4 carried by the intermediate shaft 5; a first and second gear output pinion S1 2 meshing with a first gear input pinion E1 carried by the central input shaft 1 beyond the distal end of the tubular input shaft 2, and with a second gear intermediate gear D2 carried by the intermediate shaft 5; a fifth and seventh gear output gear S57 meshing with a fifth gear input gear E5 carried by the central input shaft 1 beyond the distal end of the tubular input shaft 2, and with an intermediate gear of seventh gear D7 carried by the intermediate shaft 5; The common transfer pinion TC and the sixth gear output pinion S6 are integral with each other, have a different number of teeth and a diameter, and together form a stage pinion ST which is selectively free to rotate on the output shaft 4 or coupled thereto by a coupler C6, for example a synchronizer or a dog clutch, mounted on the output shaft 4 on the proximal side of the stage pinion. It would have been possible to use a single pinion such as S6 meshing with both an input pinion such as E6 and with the common intermediate pinion DC, but the use of a stage pinion allows the tiering to be freely chosen. gearbox reports. Alternatively, any of the output pinions S34, S1 2, S57 could have been replaced by a stepped pinion. With the current solution, we freely choose the first six ratios, there is a certain dependence between the fifth and the seventh ratio but it is acceptable because the sixth ratio between the fifth and the seventh is positioned at will. The seven gears can be made completely independent by using two stepped gears on the output shaft instead of just one. The input gears of third gear E3 and of first gear E1 are selectively, either both free to rotate, independently of one another, on the input shaft 1, or one coupled to the input shaft 1 and the other uncoupled from the input shaft 1 by a double C1 coupler 3 mounted between them on the input shaft 1. The fourth gear D4 and second gear D2 intermediate gears are selectively, either both free to rotate independently of one another on the intermediate shaft 5, or one coupled to the intermediate shaft 5 and the other uncoupled from the intermediate shaft 5 by a double coupler C24 mounted between them on the intermediate shaft 5. The output pinions S34, S1 2 and S57 are rotatably integral with the output shaft 4. The pinion d input E5 is selectively free to rotate on the central input shaft 1 or coupled thereto by a coupler C5 mounted on the central input shaft 1 on the distal side of the pinion E5. The intermediate pinion D7 is selectively free to rotate on the intermediate shaft 5 or coupled thereto by a coupler C7 mounted on the intermediate shaft 5 on the distal side of the pinion D7. A gearbox output pinion SB with helical teeth, secured to the output shaft 4, is mounted between the output pinions S34 and S1 2 to drive at least indirectly the input of a differential (not shown) causing it even wheel shafts, not shown. In FIGS. 2 to 8, illustrating the operation of the device in FIG. 1 for each of the ratios, the couplers are only shown when they are in the coupling state and transmit power. AT these figures, the elements participating in the production of the report concerned are shown in bold lines. As illustrated in FIG. 2, to form the first gear, the first gear input gear E1 is coupled with the first input shaft 1 thanks to the coupler C1 3 and the drive shaft 3 is engaged with the first shaft d 'entry 1. The first gear input gear therefore drives the first and second gear output gear S1 2 and therefore the output shaft 4 on which the latter is fixed. The couplers C5, C6 are in the decoupling position. The coupler C24 can be put in the coupling position of the intermediate pinion D2. When this is done, the second gear is effectively formed, by reversing the input clutch 8 to engage the drive shaft 3 with the second input shaft 2. The stage transfer pinion ST, free to rotate around the 'output shaft 4, returns the movement of the input shaft 2 to the intermediate shaft 5. The intermediate gear of second gear D2 therefore drives the output gear of first and second gear S1 2 and therefore the shaft of outlet 4 on which the latter pinion is fixed. The coupler C1 3 can be left in the coupling position of the pinion E1 so that the box is ready to return to first gear, or put in the coupling position of the input pinion E3 to prepare for the change to third gear. In the latter case, as illustrated in FIG. 4, the third gear is effectively formed, simply by reversing the clutch 8 again to engage the drive shaft 3 with the first input shaft 1. The third gear input gear E3 therefore drives the third and fourth gear output gear S34 and therefore the output shaft 4 on which the latter gear is fixed. During this time, the coupler C24 can be left in the pinion coupling position D2 to prepare the gearbox for ironing in second gear by simply reversing the clutch 8, or the coupler C24 can be moved to the pinion coupling position. intermediate D4. In the latter case, as illustrated in FIG. 5, to effectively form the fourth gear, the clutch 8 is again reversed to engage the drive shaft 3 with the second input shaft 2. The stage return gear ST, free to rotate around the output shaft 4, returns the rotational movement of the second input shaft 2 to the intermediate shaft 5 via the common intermediate pinion DC which is fixed to the intermediate shaft 5. This movement is transmitted with an appropriate speed ratio to the output gear of the third and fourth gear S34 via the intermediate gear of fourth gear D4, coupled with the intermediate shaft 5. During this time, the coupler C1 3 can be left in the coupling position of the input pinion E3 in preparation for a return to operation at third speed by reversing the clutch 8, or else putting the coupler C1 3 in neutral position, that is to say decoupling the Pigno ns E1 and E3, and put the coupler C5 in the coupling position of the input pinion E5. In the latter case, as illustrated in FIG. 6, the fifth gear is then formed, simply by reversing the clutch 8 to engage the drive shaft 3 with the first input shaft 1. The fifth gear input pinion E5, integral with the first input shaft 1, therefore drives the fifth and seventh gear output pinion S57 and therefore the output shaft 4 of which it is integral. During this time, the coupler C24 can be left in the coupling position of the intermediate pinion D4 to prepare for a return to operation in fourth gear by reversing the clutch 8, or else put the coupler C24 in the neutral position and the coupler C6 in the position for coupling the toothed gear ST with the output shaft 4. In the latter case, as illustrated in FIG. 7, the sixth gear is then formed, by reversing the clutch 8 to engage the drive shaft 3 with the second shaft input 2. The sixth gear input gear E6, fixed on the second input shaft 2, therefore drives the sixth gear output gear S6 and therefore the output shaft 4 with which the latter report is coupled. During this time, the coupler C5 can be left in the coupling position of the input pinion E5 with the input shaft 1, in preparation for a return to operation in fifth gear by reversing the clutch 8, or else the coupler C5 is put in the decoupling position. In the latter case, as illustrated in FIG. 8, the seventh gear is effectively formed, by putting the clutch 8 in the neutral position, by putting the coupler C6 in the decoupling position and the coupler C7 in the coupling position, then by engaging the drive shaft 3 with the second input shaft 2. The sixth gear input gear E6, fixed on the second input shaft 2, therefore drives the return gear ST which transmits a rotational movement of the second input shaft 2 to the intermediate shaft 5 via the common intermediate pinion DC which is fixed on the intermediate shaft 5 and meshes with the return pinion ST. This movement is transmitted to the output gear of the fifth and seventh gear S57 via the intermediate gear of the seventh gear D7, coupled with the intermediate shaft 5. Thus, the toothed gear ST has the dual function of producing one of the reports (the sixth in the example) by direct gear between the entry and the exit, and to return the movement of the second entry shaft 2 to the intermediate shaft 5, which carries intermediate pinions which are in fact pinions "outsourced" input. The axial length of the gearbox is greatly reduced given its number of reports. The number of pinions is also reduced since three output pinions S1 2, S34, S57 are active for two different ratios. Four out of seven reports are produced by a single gear, the other three by three successive meshes, which makes an average significantly less than 2, which is remarkable for a double clutch box and would even be excellent for a conventional single clutch box. . As the two input shafts remain independent, the device comprises, as we have seen, six successive transmission ratios, from the first to sixth, among which a report is always made by engaging an input shaft different from the tree used to make an immediately adjacent transmission report. Thus, during a shift to the higher report it is possible to prepare the second report while using the first report, to prepare the third report while using the second report, to prepare the fourth report while use the third report, prepare the fifth report while using the fourth report and prepare the sixth report while using the fifth report. Thus, it suffices to tilt the clutch 8 from one of its clutch positions to the other to ascend from a ratio to that immediately above. This allows for these reports a fast, flexible change of speed and with an imperceptible drop in power. The same is true for a decreasing gear change. The prepared but not activated report rotates the input shaft 1 or 2 which is disengaged at a speed different from that of the motor 3, but this is without disadvantage. In the embodiment illustrated in FIG. 9, the seventh forward gear has been replaced by a reverse gear. For this purpose, the seventh intermediate gear D7 has been eliminated and replaced by an intermediate reverse gear DR. In the example illustrated, so that this intermediate reverse gear DR has a sufficient diameter it is offset relative to the fifth output gear and reverse S5R. A PI reversing pinion permanently meshes with the intermediate reverse gear and with the fifth gear and reverse gear. As in the case of FIG. 8, the intermediate shaft 5 is driven by gear of the return pinion ST with the input pinion of sixth gear and with the common intermediate pinion DC. The intermediate reverse gear DR being coupled with the intermediate shaft 5 by the coupler CR, it drives, via the reverse gear PI, the output gear of the fifth and reverse gear S5R. In the embodiment illustrated in FIG. 10, described for its differences from that of FIG. 9, a seventh forward gear was added, the reverse gear being retained. For this purpose a seventh gear input gear E7 has been added free in rotation on the first input shaft 1, on the distal side, and a seventh gear output gear S7 fixed in rotation on the output shaft 4 , permanently meshes with the input pinion E7. The coupler C5 has become a double coupler C57 adapted to be able to independently couple one or the other or none among the input gears of fifth and seventh ratios E5, E7. Whatever the transmission ratio actually established, the neighboring report or, where applicable, any one of the two neighboring reports, can be prepared in masked time, after which the change of report is effected by reversing the clutch 8. This is true even for the first gear-reverse neighborhood. In addition, the gearbox output pinion SB is mounted fixed in rotation no longer on the output shaft 4, but on a transfer shaft 10. A transfer pinion R fixedly mounted on the transfer shaft, permanently meshes with the input gear of the third gear E3. Thus, the transfer gear introduces a coefficient at the speed of rotation of the output shaft 4. The third gear is produced by direct gear of the transfer gear R with the input gear E3 secured to the first input shaft 1 by the coupler C1 3, without the power passing through the output shaft 4. The other reports are produced as described above, except that the movement of the output shaft 4 is transmitted to the transfer shaft 1 0 via the third gear input gear E3 which, in the decoupled state of the input shaft, constitutes a toothed gear according to the invention between the output shaft 4 and the transfer shaft 1 0. The output gear S4 is an output gear, in the sense used so far, only for the fourth gear. For reports other than the third and fourth, it serves as power transfer pinion to the transfer shaft 1 0 via the pinion E3 forming a toothed gear. For use on a vehicle having two driving axles, the engine, therefore the transfer shaft, being transverse, the transfer shaft 10 further comprises a bevel gear RC allowing the drive of a longitudinal transmission shaft 1 1. In practice, it is advantageous that the transfer shaft 10 is below the input shafts 1 and 2, and the shafts 4 and 5 above the input shafts 1 and 2. In other words, the figure 1 0 of 1 80 ° in its own plan. The transfer shaft 1 0 is then relatively low in the vehicle, which is particularly suitable for a four-wheel drive transmission, in particular because the drive shafts are generally arranged below the engine. Furthermore, this allows the gearbox output pinion SB to be positioned more freely relative to the gearbox device than when this pinion is carried by a shaft, such as the shaft 4, located at the heart of the gearbox. On the other hand, the helical toothing of the gearbox output pinion SB generates significant axial forces on the shaft which carries it, especially since this pinion is generally of small diameter. It is thus possible to provide a transfer shaft 10, and bearings for this shaft, better suited than when the gearbox output pinion is mounted directly on the output shaft of the gearbox. For example, for the embodiments of Figures 1 -1 2, the pinions have the following diameters, in millimeters: E6: 1 1 7 E3: 81 E1: 45 E5: 1 07 S6: 84 TC: 1 01 S4 or S34: 1 20 S1 2: 1 56 S5R or S57: 94 DC: 1 1 9 D4: 64 D7: 1 26 DR: 1 30 E7: 1 23 S7: 78 The reports thus obtained are as follows: first report 3 , 47 second gear 2.08 third gear 1, 48 fourth gear 1, 02 fifth gear 0.88 sixth gear 0.72 seventh gear 0.63 reverse gear: 2.95 In the gearbox 200 in the figure 13, which will be described for its differences from that of FIG. 1, the role of the first and of the second input shaft are reversed. More specifically, the toothed gear ST is now mounted at the distal end of the output shaft 4 and its fifth gear output pinion S5 meshes with an input pinion E5 which is rigidly fixed with the first input shaft 1 beyond the distal end of the tubular shaft 2. The intermediate shaft 5 is therefore now driven by the first input shaft 1 and no longer by the second input shaft 2, still via the toothed gear ST mounted on the output shaft 4. The output pinions S12 and S34 now located on the proximal side of the toothed gear ST, mesh respectively with intermediate pinions D1 and D3 mounted free in rotation on the intermediate shaft 5, on either side of a coupler C1 3 which makes it possible to couple one or the other or none of them with the shaft 5. The pinions S 1 2 and S34 still mesh, respectively, with input pinions E2 and E4 which are mounted to rotate freely on the second input shaft 2 (and no longer on the first shaft 1) on either side of the coupler C24 which makes it possible to couple one or the other, or none of them, with the shaft 2. The sixth gear input gear E6, fixed to the shaft 2 on the proximal side with respect to E2 and E4, drives a second intermediate shaft

1 5 by meshing with a common pinion FC secured to the shaft 1 5. The coaxial input shafts 1 and 2 are therefore functionally mounted between the output shaft 4 and the second intermediate shaft 1 5. A sixth intermediate gear F6 and an intermediate reverse gear FR are mounted to rotate freely on the second intermediate shaft 1 5 on either side of a double coupler C6R which makes it possible to couple one or the other or none of F6 and FR to the shaft 1 5. The pinion F6 meshes with the input gear of fourth gear E4. As indicated by a dotted arrow 1 6, the intermediate reverse gear FR engages directly with the common transfer gear TC by bypassing the line of input shafts 1 and 2. This is possible because the embodiment shown in the form plane is actually "folded" along the axis of the input shafts (see Figure 1 4). The engagement of each of the first five reports is obtained by processes similar to those described for the 2 ^nd , 1 ^st , 4 ^th , 3 ^rd and 6 ^th reports respectively, in Figure 1, except that the role of the two trees d input 1 and 2 are inverted. For the sixth gear, the coupler C24 being in the neutral position and the coupler C6R coupling the intermediate gear of the sixth gear F6 with the shaft 1 5, the power is transmitted from the second input shaft 2 to the output shaft 4 by the E6-FC and F6-E4-S34 meshes. The input pinion E4 decoupled from the input shaft 2 serves as a toothed return between the second intermediate shaft 1 5 and the output shaft 4. During this time, the coupler C5R can couple the output pinion S5, that is to say the toothed gear ST with the output shaft 4 to prepare a return in fifth gear operation by simply reversing the dual input clutch, not shown. For reverse operation, the coupler C6R secures the reverse reverse intermediate gear FR with the second intermediate shaft 1 5, the coupler C5R releases the common transfer gear TC from the output shaft 4, that is to say say the toothed reference ST, and the coupler C1 3 secures the pinion D1 with the intermediate shaft 5. Figure 14 is a view in a plane perpendicular to the trees. As illustrated, the projections of the trees in the plane of Figure 14 form a quadrilateral. Thus, the gearbox is compact. FIG. 14 also illustrates the successive meshes of the pinions E6 and FC, FR and TC, TC and DC, D1 and S1 2 necessary for the formation of the reverse gear ratio. For example, for the embodiment of FIGS. 1 3-14, the pinions have the following diameters, in millimeters: E6: 1 1 8 E4: 1 04 E2: 70 E5: 1 1 2 FC: 86 F6: 100 FR: 1 40 S34: 1 00 S1 2: 1 34 S5: 92 TC: 74 DC: 1 02 D1: 42 D3: 76 The ratios thus obtained are as follows: first gear 3.61 second gear 1.91 third gear 1.49 fourth gear 0.96 fifth gear 0.82 sixth gear 0.73 reverse gear: 1.69 In the embodiment of Figure 1 5, which will be described only in its differences from that of Figure 1 3, the intermediate reverse gear FR engages with a reversing pinion PI mounted idly on an additional shaft, this pinion reverse gear itself meshing with the second gear input gear E2. Thus, the first and second gear output gear S1 2 serves as an output gear for the reverse gear. By way of example, for the embodiment of FIG. 1 5, the intermediate gear of reverse gear FR has a diameter of 42 millimeters and the reverse gear thus obtained is 2.33. Thanks to this arrangement, the larger diameter pinion is reduced to 1 34 millimeters for the output pinion of first and second gear S1 2. The compactness of the gearbox is further increased. The device of Figure 1 5 further comprises a seventh transmission speed ratio formed by a seventh gear input gear E7 fixedly mounted on the first input shaft 1 and meshing with a seventh gear output gear S7 which can be selectively coupled with the output shaft 4, using the same coupler C57 as the output gear of the fifth gear S5, that is to say the toothed gear ST. This embodiment is particularly advantageous because it produces eight reports (seven forward + reverse) with only four double couplers, only one of which is in the position of coupling for each report, which simplifies the commands, and for each report it is possible to prepare in hidden time the neighboring report or, as the case may be, any of the two neighboring reports, to then operate the change of report by simple inversion of the dual input clutch, not shown. The four couplers are mounted on four different axes, so that the axial dimensions of the couplers are absolutely not added. Of the seven forward gears, four involve only one gear under load, the other three each involve three gears, the average number of gears under load therefore being only around 1.85, with in addition to the advantage that the seventh report only involves one. In this embodiment, the second gear input gear E2 also exerts a toothed return function when it is decoupled, for operation in reverse. The gearbox output pinion, not shown, can be integral with the output shaft 4. Of course, the invention is not limited to the examples which have just been described and numerous modifications can be made to these examples without departing from the scope of the invention. In the embodiment of FIGS. 10-1 2, rather than with the third input pinion, it is also possible to mesh the transfer pinion with another of the pinions among those E1, E2, E4 mounted free in rotation on the input shafts 1, 2, and intermediate 5, and meshing with one of the pinions fixedly mounted on the output shaft 4. it is also possible to make it mesh with one of the pinions S1, S3 fixedly mounted on the output shaft 4. In the example of FIGS. 1 to 8, the center distance h41 could be larger than the center distance h45, so that the input pinions are, from proximal to distal, a seventh gear fixed to the shaft 2 and three fourth, second and sixth gear mounted on tree 1. Then on the intermediate shaft, from proximal to distal from the DC pinion: third, first and fifth gear gears. With this arrangement, all the passages, including between the sixth and the seventh report, can be prepared by positioning the couplers in masked time then effective establishment of the new report by simple reversing of the clutch 8. In all the embodiments, the two input shafts 1, 2 can be replaced by a single shaft, and the double clutch 8 by a conventional clutch which selectively engages or disengages the single input shaft relative to the motor shaft 3. In this case , only the coupler (s) necessary for establishing the effective transmission ratio is (are) in the coupling position. To change gears, the input clutch is disengaged, the position of the couplers is changed, then the input clutch is re-engaged. In the example of FIG. 1 0, an eighth gear could be created by placing an intermediate gear of free eighth gear in rotation at the distal end of the intermediate shaft 5 and in gear with the gear S7, and by replacing the CR coupler for a double coupler. The gearboxes according to the invention can be automated. A pilot automaton, by a pre-established logic, with or without the possibility of intervention by the driver of the vehicle, actuations of the couplers and of the input clutch, and prohibits or delays the execution of any dangerous commands from the driver, such as for example shifting into reverse when the vehicle is moving in forward gear, or engaging in inappropriate gear, dangerous for the engine and / or the gearbox and / or for controlling the path of the vehicle or its braking. In the example of FIG. 1 0, the improvement relating to the deferred output is independent of the other improvements described under FIGS. 9 and 10. Still in the example of FIG. 10, one can make the input pinions E5 and E7 integral with the central input shaft 1, and place a double coupler between the output pinions S5R and S7 to selectively couple the one or neither of them to the output shaft 4. However, the coupler must then transmit the high reverse torque. The examples of FIGS. 13 to 15 can be arranged to transfer the gearbox output pinion such as BS to a transfer shaft such as 10 installed for example behind the plane of FIGS. 13 and 15.

Claims

1. Gearbox device (1 00,200) comprising rotary members (1, 2,4,5,1 5) carrying toothed members (E1 -E7, S1 2, S34, S5, S57, S6, S7, D1 -D4 , D7, DC, FC, F6, FR, ST, SB), characterized in that at least one toothed reference (ST, E2, E3, E4) among the toothed members, which has a function of movement reference between two rotary members for producing a transmission ratio, can be selectively coupled with another rotary member for producing another transmission ratio.

2. Device according to claim 1, characterized in that the toothed gear (ST) is carried by a rotary outlet member (4) to which it can be coupled for the production of said other transmission ratio.

3. Device according to claim 1 or 2, characterized in that the toothed gear (E2, E3, E4) is carried by a rotary input member to which it can be coupled for the production of said other transmission ratio.

4. Device according to one of claims 1 to 3, characterized in that at least one toothed return (ST) has a function of return of the movement between a rotary input member (1, 2) and an intermediate rotary member (5).

5. Device according to one of claims 1 to 4, characterized in that at least one toothed gear (E2, E4) has a function of returning the movement between an intermediate rotary member (1 5) and a rotary output member ( 4).

6. Device according to one of claims 1 to 5, characterized in that in its return function, the toothed return is decoupled from the rotary member which carries it.

7. Device according to one of claims 1 to 6, characterized in that at least one toothed reference (ST) which for a transmission ratio causes a direction of rotation of a rotary output member (4), has further , for another transmission ratio, an inverter function for the direction of rotation of said rotary output member.

8. Device according to one of claims 1 to 7, characterized in that the at least one toothed gear comprises a stage pinion (ST) having two teeth (S5, TC) each meshing with a teeth linked to one of said rotary organs between which it returns the movement.

9. Device according to one of claims 1 to 8, characterized in that the toothed gear (ST) and several other toothed members (S1 2 - S34) output die are mounted on a rotary output member (4) and each mesh with a respective input toothed member (E1 -E4) mounted on at least one rotary input member (1, 2), and with a respective intermediate toothed member (DC, D1 -D4) mounted on an intermediate rotary member ( 5), coupling means (C1 3, C6, C24) being provided for carrying out the transmission of the at least one rotary input member (1, 2) to the rotary output member (4), directly or selectively via the toothed gear (ST) and the intermediate rotary member (5).

10. Device according to one of claims 1 to 9, characterized in that at least one of the toothed members (E3) which can be selectively coupled with another rotary member (1) for the production of a transmission ratio is a transfer member which has a proportional transfer function for transmission ratios to a rotary transfer member (1 0) used for the transmission of movement to at least one wheel shaft.

1 1. Device according to claim 10, characterized in that one of the input toothed members (E3) belongs to the at least one toothed reference and can either be coupled to the at least one rotary member of input to make a direct relationship between the rotary input member (1) and the rotary transfer member (10), or be decoupled to return the movement of the rotary output member (4) to the rotary member carryforward (1 0).

12. Device according to claim 5, characterized in that one of the input toothed members (E2, E4) belongs to the at least one toothed reference and can either be coupled to the at least one rotary member d 'inlet (2) to make a direct relationship between the rotary input member (2) and the member rotary output (4), or be decoupled to return the movement between an intermediate rotary member (1 5) and the rotary output member (4).

13. Device according to claim 1 2, characterized in that the rotary input member (1) and the intermediate rotary member (1 5) are connected by another pair of teeth (E6-FC), meshed together .

14. Device according to claim 1 2 or 1 3, characterized in that there is a direct gear between a toothed member (FR) on an intermediate rotary member (1 5) and a toothed member (TC) on the rotary member output (4) for a reverse gear.

15. Device according to claim 9, characterized in that the at least one toothed gear comprises a second toothed gear (E2, E4) mounted on a rotary inlet member (1) between a toothed outlet member (4) and an intermediate toothed member (F6, FR) mounted on a second intermediate rotary member (1 5) carrying at least one common toothed member (DC) meshing with a toothed input member (E6).

16. Device according to one of claims 9 to 1 5, characterized in that the at least one rotary input member comprises two rotary input members (1, 2) which can be alternately and selectively coupled to a shaft motor (3), one of the rotary input members (2,1) driving the toothed gear (ST) carried by the rotary output member (4), the other (1, 2) carrying toothed members (E1, E3, E2, E4) input which define relationships which alternate with those defined via the intermediate toothed organs (D2, D4, D1, D3).

17. Device according to one of claims 1 to 1 5, characterized in that the at least one rotary input member comprises two rotary input members (1, 2) which can be selectively engaged with the same motor, the transition from a transmission ratio to a neighboring transmission ratio comprising an action of clutching at least one of the rotary input members (1, 2) and disengaging the other rotary input member.

18. Device according to claim 1 6 or 1 7, characterized in that the rotary input members (1, 2) are coaxial.

19. Device according to one of claims 1 6 to 1 8 characterized in that a rotary input member comprises only a single toothed member (E5, E6) meshing with the at least one toothed reference (ST) .

20. Device according to one of claims 1 to 1 9, characterized in that it comprises a single rotary outlet member (4).

21. Device according to claim 1, characterized in that it comprises: - two direct reports each produced by direct gearing of a first toothed input member (E2, E4) with a toothed output member (S2, S4). - two first indirect reports produced by a cascade of gears passing through a first toothed gear (ST) carried by the rotary output member (4), - two second indirect reports produced by a cascade of gears passing through at least one second toothed gear carried by a rotary input member (E4, E2), and, - a ratio (E5-S5) produced by direct gear between the first rotary input member (1) and the first toothed gear (ST) coupled with the rotary output member (4).

22. Device according to claim 21, characterized in that it comprises an additional ratio (E7-S7) produced by direct gear between a rotary input member (1) and the rotary output member (4), with a same coupler (C57) as that used to couple the first toothed gear (ST) with the output member (4).

23. Device according to claim 21 or 22, characterized in that it comprises two intermediate rotary members (5, 1 5) and in that it comprises a double coupler (C24) on the at least one rotary member inlet (1, 2), a double coupler (C57) on the rotary output member (4) and a double coupler (C6R, C1 3) on each of the intermediate rotary members (5, 1 5).

24. Device according to one of claims 21 to 23, characterized in that it comprises two concentric input members (1, 2), one (2) meshing with the first intermediate rotary member (15) and carrying the first two toothed members (E2, E4), the other meshing with the second toothed gear (ST) and preferably meshing with another pair of teeth (E7, S7) with the rotary outlet member (4).

25. Use of a device according to one of the preceding claims for the transmission of a vehicle to at least two drive trains.