WO2005103525A1 - 'boite de vitesses pour l'automobile, notamment a double embrayage' - Google Patents
'boite de vitesses pour l'automobile, notamment a double embrayage' Download PDFInfo
- Publication number
- WO2005103525A1 WO2005103525A1 PCT/FR2005/000581 FR2005000581W WO2005103525A1 WO 2005103525 A1 WO2005103525 A1 WO 2005103525A1 FR 2005000581 W FR2005000581 W FR 2005000581W WO 2005103525 A1 WO2005103525 A1 WO 2005103525A1
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- WO
- WIPO (PCT)
- Prior art keywords
- rotary
- toothed
- gear
- input
- members
- Prior art date
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Classifications
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16H—GEARING
- F16H3/00—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion
- F16H3/02—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion without gears having orbital motion
- F16H3/08—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion without gears having orbital motion exclusively or essentially with continuously meshing gears, that can be disengaged from their shafts
- F16H3/087—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion without gears having orbital motion exclusively or essentially with continuously meshing gears, that can be disengaged from their shafts characterised by the disposition of the gears
- F16H3/091—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion without gears having orbital motion exclusively or essentially with continuously meshing gears, that can be disengaged from their shafts characterised by the disposition of the gears including a single countershaft
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16H—GEARING
- F16H3/00—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion
- F16H3/006—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion power being selectively transmitted by either one of the parallel flow paths
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16H—GEARING
- F16H3/00—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion
- F16H3/02—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion without gears having orbital motion
- F16H3/08—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion without gears having orbital motion exclusively or essentially with continuously meshing gears, that can be disengaged from their shafts
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16H—GEARING
- F16H3/00—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion
- F16H3/02—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion without gears having orbital motion
- F16H3/08—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion without gears having orbital motion exclusively or essentially with continuously meshing gears, that can be disengaged from their shafts
- F16H2003/0826—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion without gears having orbital motion exclusively or essentially with continuously meshing gears, that can be disengaged from their shafts wherein at least one gear on the input shaft, or on a countershaft is used for two different forward gear ratios
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16H—GEARING
- F16H3/00—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion
- F16H3/02—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion without gears having orbital motion
- F16H3/08—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion without gears having orbital motion exclusively or essentially with continuously meshing gears, that can be disengaged from their shafts
- F16H3/087—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion without gears having orbital motion exclusively or essentially with continuously meshing gears, that can be disengaged from their shafts characterised by the disposition of the gears
- F16H3/093—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion without gears having orbital motion exclusively or essentially with continuously meshing gears, that can be disengaged from their shafts characterised by the disposition of the gears with two or more countershafts
- F16H2003/0938—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion without gears having orbital motion exclusively or essentially with continuously meshing gears, that can be disengaged from their shafts characterised by the disposition of the gears with two or more countershafts with multiple gears on the input shaft directly meshing with respective gears on the output shaft
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- 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
- F16H2200/00—Transmissions for multiple ratios
- F16H2200/003—Transmissions for multiple ratios characterised by the number of forward speeds
- F16H2200/0056—Transmissions for multiple ratios characterised by the number of forward speeds the gear ratios comprising seven forward speeds
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16H—GEARING
- F16H3/00—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion
- F16H3/02—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion without gears having orbital motion
- F16H3/08—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion without gears having orbital motion exclusively or essentially with continuously meshing gears, that can be disengaged from their shafts
- F16H3/087—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion without gears having orbital motion exclusively or essentially with continuously meshing gears, that can be disengaged from their shafts characterised by the disposition of the gears
- F16H3/093—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion without gears having orbital motion exclusively or essentially with continuously meshing gears, that can be disengaged from their shafts characterised by the disposition of the gears with two or more countershafts
-
- Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
- Y10—TECHNICAL SUBJECTS COVERED BY FORMER USPC
- Y10T—TECHNICAL SUBJECTS COVERED BY FORMER US CLASSIFICATION
- Y10T74/00—Machine element or mechanism
- Y10T74/19—Gearing
- Y10T74/19219—Interchangeably locked
- Y10T74/19284—Meshing assisters
- Y10T74/19288—Double clutch and interposed transmission
Definitions
- 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.
- 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.
- gearboxes 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.
- 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.
- 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.
- 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.
- 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.
- 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.
- 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.
- a toothed gear can comprise a stage pinion having two teeth each meshing with a teeth linked to one of said rotary members.
- 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.
- 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.
- 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.
- 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.
- 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.
- 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.
- 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.
- 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.
- 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.
- 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.
- 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.
- 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
- 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.
- 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.
- 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.
- 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 S
- 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.
- FIGS. 2 to 8 illustrating the operation of the device in FIG.
- 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.
- 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.
- 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.
- 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.
- 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.
- 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.
- 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.
- 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.
- 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.
- 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.
- 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.
- 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.
- 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 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.
- the seventh intermediate gear D7 has been eliminated and replaced by an intermediate reverse gear DR.
- 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.
- 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.
- FIG. 10 described for its differences from that of FIG.
- a seventh forward gear was added, the reverse gear being retained.
- 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.
- 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.
- 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.
- 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.
- it serves as power transfer pinion to the transfer shaft 1 0 via the pinion E3 forming a toothed gear.
- the transfer shaft 10 further comprises a bevel gear RC allowing the drive of a longitudinal transmission shaft 1 1.
- 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.
- 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
- 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.
- 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.
- 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.
- the intermediate reverse gear FR engages directly with the common transfer gear TC by bypassing the line of input shafts 1 and 2.
- 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.
- 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.
- 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
- 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.
- 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.
- FIGS. 14 illustrate 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.
- 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
- 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.
- the first and second gear output gear S1 2 serves as an output gear for the reverse gear.
- 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.
- the second gear input gear E2 also exerts a toothed return function when it is decoupled, for operation in reverse.
- the gearbox output pinion can be integral with the output shaft 4.
- 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.
- 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.
- 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.
- 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.
- the double clutch 8 by a conventional clutch which selectively engages or disengages the single input shaft relative to the motor shaft 3.
- the input clutch is disengaged, the position of the couplers is changed, then the input clutch is re-engaged.
- 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.
- 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.
- 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.
Landscapes
- Engineering & Computer Science (AREA)
- General Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- Structure Of Transmissions (AREA)
- Motor Power Transmission Devices (AREA)
- Mechanical Operated Clutches (AREA)
Abstract
Description
Claims
Priority Applications (3)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
JP2007504439A JP2007530881A (ja) | 2004-03-24 | 2005-03-11 | 特にダブルクラッチを備えた自動車ギヤボックス |
US10/593,582 US20070180942A1 (en) | 2004-03-24 | 2005-03-11 | Motor vehicle gearbox, in particular with a double clutch |
EP05739523A EP1735544A1 (fr) | 2004-03-24 | 2005-03-11 | "boite de vitesses pour l'automobile, notamment a double embrayage" |
Applications Claiming Priority (2)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
FR0403015A FR2868141B1 (fr) | 2004-03-24 | 2004-03-24 | Boite de vitesses pour l'automobile, notamment a double embrayage |
FR0403015 | 2004-03-24 |
Publications (1)
Publication Number | Publication Date |
---|---|
WO2005103525A1 true WO2005103525A1 (fr) | 2005-11-03 |
Family
ID=34944497
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
PCT/FR2005/000581 WO2005103525A1 (fr) | 2004-03-24 | 2005-03-11 | 'boite de vitesses pour l'automobile, notamment a double embrayage' |
Country Status (9)
Country | Link |
---|---|
US (1) | US20070180942A1 (fr) |
EP (1) | EP1735544A1 (fr) |
JP (1) | JP2007530881A (fr) |
KR (1) | KR20070009636A (fr) |
CN (1) | CN1957193A (fr) |
AR (1) | AR048920A1 (fr) |
FR (1) | FR2868141B1 (fr) |
TW (1) | TW200540035A (fr) |
WO (1) | WO2005103525A1 (fr) |
Cited By (2)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
WO2010063336A1 (fr) * | 2008-12-03 | 2010-06-10 | Gm Global Technology Operations, Inc. | Boîte de vitesses pour véhicule à moteur |
EP3171053A1 (fr) * | 2015-10-22 | 2017-05-24 | Deere & Company | Boîte de vitesses |
Families Citing this family (22)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US7752934B2 (en) * | 2007-02-20 | 2010-07-13 | Gm Global Technology Operations, Inc. | Multi speed transmission having a countershaft gearing arrangement |
US7610825B2 (en) * | 2007-02-22 | 2009-11-03 | Gm Global Technology Operations, Inc. | Multi-speed transmission with countershaft gearing |
US7703346B2 (en) * | 2007-02-22 | 2010-04-27 | Gm Global Technology Operations, Inc. | Multi-speed transmission with countershaft gearing |
US7640818B2 (en) | 2007-02-23 | 2010-01-05 | Gm Global Technology Operations, Inc. | Multi-speed transmission with a countershaft gearing |
US7644639B2 (en) | 2007-02-23 | 2010-01-12 | Gm Global Technology Operations, Inc. | Multi-speed transmission with countershaft gearing |
AT503476B1 (de) * | 2007-06-28 | 2010-11-15 | Avl List Gmbh | Getriebe für ein fahrzeug |
JP4998728B2 (ja) * | 2007-09-28 | 2012-08-15 | 本田技研工業株式会社 | ツインクラッチ式変速装置 |
DE102007049271B4 (de) * | 2007-10-15 | 2016-10-20 | Zf Friedrichshafen Ag | Doppelkupplungsgetriebe |
DE102008001199B4 (de) * | 2008-04-16 | 2018-12-20 | Zf Friedrichshafen Ag | Verfahren zum Betreiben eines Doppelkupplungsgetriebes |
US7987740B2 (en) * | 2008-09-03 | 2011-08-02 | GM Global Technology Operations LLC | Multi-speed transmission with countershaft gearing arrangement |
US8434380B2 (en) * | 2009-01-23 | 2013-05-07 | GM Global Technology Operations LLC | Dual clutch multi-speed transmission |
US8528431B2 (en) * | 2009-04-28 | 2013-09-10 | GM Global Technology Operations LLC | Dual clutch transmission |
US8443686B2 (en) | 2009-05-12 | 2013-05-21 | GM Global Technology Operations LLC | Seven speed dual clutch transmission |
EP2322821B1 (fr) * | 2009-11-13 | 2013-01-09 | C.R.F. Società Consortile per Azioni | Boîte de vitesses pour transmission à double embrayage de véhicule à moteur |
JP5123283B2 (ja) * | 2009-12-24 | 2013-01-23 | 本田技研工業株式会社 | 変速機 |
GB2476956A (en) * | 2010-01-14 | 2011-07-20 | Gm Global Tech Operations Inc | Dual clutch multi-speed transmission and vehicle having a dual clutch multi-speed transmission |
DE102010008101B4 (de) | 2010-02-15 | 2021-04-22 | Dr. Ing. H.C. F. Porsche Aktiengesellschaft | Doppelkupplungsgetriebe |
DE102011005532A1 (de) * | 2011-03-15 | 2012-09-20 | Zf Friedrichshafen Ag | Hybridantrieb eines Kraftfahrzeugs |
DE102012004721B4 (de) | 2012-03-01 | 2013-10-31 | Getrag Getriebe- Und Zahnradfabrik Hermann Hagenmeyer Gmbh & Cie Kg | Stufenwechselgetriebe |
WO2015121498A1 (fr) * | 2014-02-17 | 2015-08-20 | Engineering Center Steyr Gmbh & Co Kg | Transmission à double embrayage commutable à pleine charge |
DE102016207222B4 (de) * | 2016-04-28 | 2021-02-25 | Zf Friedrichshafen Ag | Doppelkupplungsgetriebe in Vorgelegebauweise |
KR20220086090A (ko) * | 2020-12-16 | 2022-06-23 | 현대자동차주식회사 | 하이브리드 차량용 변속장치 |
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2004
- 2004-03-24 FR FR0403015A patent/FR2868141B1/fr not_active Expired - Fee Related
-
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- 2005-03-11 WO PCT/FR2005/000581 patent/WO2005103525A1/fr not_active Application Discontinuation
- 2005-03-11 CN CNA2005800160809A patent/CN1957193A/zh active Pending
- 2005-03-11 US US10/593,582 patent/US20070180942A1/en not_active Abandoned
- 2005-03-11 TW TW094107408A patent/TW200540035A/zh unknown
- 2005-03-11 KR KR1020067021911A patent/KR20070009636A/ko not_active Application Discontinuation
- 2005-03-11 EP EP05739523A patent/EP1735544A1/fr not_active Withdrawn
- 2005-03-11 JP JP2007504439A patent/JP2007530881A/ja active Pending
- 2005-03-22 AR ARP050101114A patent/AR048920A1/es unknown
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Cited By (4)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
WO2010063336A1 (fr) * | 2008-12-03 | 2010-06-10 | Gm Global Technology Operations, Inc. | Boîte de vitesses pour véhicule à moteur |
GB2478869A (en) * | 2008-12-03 | 2011-09-21 | Gm Global Tech Operations Inc | Gearbox for a motor vehicle |
EP3171053A1 (fr) * | 2015-10-22 | 2017-05-24 | Deere & Company | Boîte de vitesses |
US10352402B2 (en) | 2015-10-22 | 2019-07-16 | Deere & Company | Group manual transmission |
Also Published As
Publication number | Publication date |
---|---|
AR048920A1 (es) | 2006-06-14 |
JP2007530881A (ja) | 2007-11-01 |
TW200540035A (en) | 2005-12-16 |
US20070180942A1 (en) | 2007-08-09 |
CN1957193A (zh) | 2007-05-02 |
FR2868141A1 (fr) | 2005-09-30 |
FR2868141B1 (fr) | 2007-05-25 |
EP1735544A1 (fr) | 2006-12-27 |
KR20070009636A (ko) | 2007-01-18 |
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