Classifications

• • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
  • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
  • F16H—GEARING
  • 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
  • F16H2200/00—Transmissions for multiple ratios
  • F16H2200/003—Transmissions for multiple ratios characterised by the number of forward speeds
  • F16H2200/0047—Transmissions for multiple ratios characterised by the number of forward speeds the gear ratios comprising five 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
  • F16H2200/00—Transmissions for multiple ratios
  • F16H2200/003—Transmissions for multiple ratios characterised by the number of forward speeds
  • F16H2200/0052—Transmissions for multiple ratios characterised by the number of forward speeds the gear ratios comprising six 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
  • 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
• • 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
  • Y10T74/19233—Plurality of counter shafts

Definitions

• the present invention relates to a gearbox, particularly for a motor vehicle, of the type comprising two input shafts, controlled by two clutches for selecting one or the other of the input shafts.
• 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 couples which is activated by means of a coupler which is typically a synchronizer.
• Gearboxes comprising two input shafts exist, in particular to obtain successive gear shifts by limiting the drop in power transmitted.
• an existing gearbox for the automobile comprises two input shafts selected from each other by a double clutch and two output shafts each meshing with the two input shafts by several couples selectively activated by couplers. mounted on the two output shafts.
• Such an arrangement requires a distribution device, to transmit the movement to the wheels, regardless of the active output shaft, which significantly increases the gearbox.
• one of the input shafts is tubular and surrounds the other input shaft, which carries its gears beyond the end of the tubular shaft.
• the object of the invention is to provide a gearbox, compact and lightweight relative to the number of reports offered.
• Another object of the invention is to provide a gearbox of reduced axial length.
• Yet another object of the invention is to provide a dual clutch transmission satisfying at least one of the above purposes.
• An additional goal is to provide a dual clutch gearbox easy to implement in a four-wheel drive vehicle.
• the gearbox device comprising two input clutches for selectively coupling one or the other of two input shafts with a motor shaft, is characterized in that:
• the two input shafts are arranged at a distance from one another, each coaxially with one of the input clutches,
• the two input clutches each have their own driving element in the axis of the associated input shaft
• the incoming movement is distributed. along two axes in the gearbox. This brings several improvements.
• an incoming tree is lighter than an outgoing tree because it transmits a torque that is not yet multiplied by the speed reduction.
• Figure 1 is a schematic representation of a first embodiment for a gearbox device according to the invention, comprising 5 forward gears and a reverse gear;
• Figures 2 to 7 show schematically the operation of the device of Figure 1 for each report;
• Figure 8 is a schematic representation of a second embodiment.
• FIG. 1 represents a transmission device 100 comprising two non-coaxial parallel input shafts 1 and 2, namely a first shaft 1 coaxial with a drive shaft 3, and a second shaft 2 parallel to the shaft 1 and offset laterally to this one.
• Each input shaft 1 and 2 comprises a driven clutch disc 6 which it is integral in rotation.
• the disks 6 are each mounted facing a driving clutch disk 7.
• the driving disks 7 are secured to one of the drive shaft 3, the other of a transfer shaft 5 coaxial with the second input shaft 2.
• the drive shaft 3 and the transfer shaft 5 are connected by a permanent drive mechanical connection 9, comprising in this example a transmission chain 11 meshing with an input pinion 12 integral with the drive shaft 3 and a transfer gear 13 integral with the transfer shaft 5.
• the diameter of the transfer gear 13 is about 1.2 times smaller than the diameter of the gear 12, so that the gear shaft report 5 rotates about 1.2 times faster than input shaft 3.
• the two clutches 8, considered together, can take three states, a first state (shown in Figure 1), in which the two clutches are disengaged and none of the disks 6.7, is in contact with the other, a second state in which the motor shaft 3 is engaged with the first input shaft 1 while the transfer shaft 5 is disengaged from the second input shaft 2, and a third state in which the motor shaft 3 drives the second input shaft via the transfer shaft 5 and the associated clutch 8 while being disengaged from the first input shaft 1.
• the first state decouples the engine relative to the vehicle wheels, especially when the vehicle is when stopped and especially just before the vehicle is started.
• the device 100 further comprises an output shaft 4 rotatably mounted parallel to the input shafts 1, 2.
• the output shaft 4 is located functionally and topographically between the input shafts 1 and 2.
• the three shafts 1, 2, 4 rotate in fixed positions relative to each other in a housing, not shown.
• the output shaft 4 has with respect to the first input shaft 1 a center distance h41 smaller than its center distance h.42 with the second input shaft 2.
• the trees are shown coplanar for reasons of clarity. However, to limit and adapt to the space available the size of such a gearbox, the actual layout can be
• the third report input gearwheels E3 and of first gear El are selectively either 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 coupler C13 mounted between them on the input shaft 1.
• the fourth report E4 and second report E2 input gears are selectively, either free to rotate, independently of one another, on the second input shaft 2, or one coupled to the second shaft 2 and the other uncoupled from the input shaft 2 by a double coupler C24 mounted between them on the input shaft 2.
• the output gears S34, S12 and S5R are integral in rotation with the output shaft 4 ' .
• the input gear E5 is selectively free to rotate on the first input shaft 1 or coupled thereto by a coupler C5 mounted on the input shaft 1 of the distal side of the pinion E5.
• the input gear ER is selectively free to rotate on the second input shaft 2 or coupled thereto by a CR coupler mounted on the input shaft 2 on the distal side of the ER pinion.
• a helical gear box gear SB integral with the output shaft 4, is mounted in this example between the output gears S34 and S12 to at least indirectly drive the input of a differential (not shown) causing itself of the wheel shafts, not shown.
• a gearbox output can also be provided at one and / or the other end of the output shaft 4.
• the first gear El input gear is coupled to the first input shaft 1 by means of the coupler C13 and the motor shaft 3 is engaged with the first gear shaft. input 1.
• the first gear input gear therefore drives the output gear of first and second gear S12 and thus the output shaft 4 on which the latter is fixed.
• the coupler C5 is in the decoupling position.
• the coupler CR can be put in the coupling position of the input gear ER with the shaft 2 or the coupler C24 can be set in the coupling position of the input gear E2.
• the second ratio is effectively formed by inverting the states of the input clutches 8 to connect the motor shaft 3 with the second input shaft 2 via the link 9 and the transfer shaft 5, as As shown in FIG.
• the second ratio input gear E2 thus drives the first and second gear output gear S12 and thus the output shaft 4 on which the latter gear is fixed.
• the coupler C13 can be left in the coupling position of the pinion El so that the box is ready to iron in first gear, or put in the coupling position of the input gear E3 to prepare the passage in third gear.
• the third gear is effectively formed simply by reversing the states of the clutches 8 to engage the drive shaft 3 with the first input shaft 1.
• the input gear Third gear ratio E3 therefore drives the third and fourth gear output gear S34 and thus the output shaft 4 on which the latter gear is fixed.
• the coupler C24 can be left in the coupling position of the pinion E2 to prepare the gearbox to be ironed.
• the fifth gear is then formed simply by reversing the states of the clutches 8 to engage the drive shaft 3 with the first input shaft 1.
• the fifth input gear report ⁇ 5 is then formed simply by reversing the states of the clutches 8 to engage the drive shaft 3 with the first input shaft 1.
• the axial length of the box is very small in view of its number of reports.
• the number of sprockets is also reduced since each of the three output sprockets S12, S34, S5R is active for two different ratios.
• Three out of five forward gears are made by a single meshing, the other two by the link 9 followed by a meshing, which is an average significantly less than 2, which is remarkable for a double-clutch gearbox and would even excellent for a classic box with a simple clutch.
• the two input shafts remaining independent the device comprises, as we have seen, six successive transmission ratios, from the reverse to the fifth forward gear, among which a ratio is always achieved by engaging a gear shaft. different input of the shaft used to achieve an immediately adjacent transmission ratio.
• the device comprises, as we have seen, six successive transmission ratios, from the reverse to the fifth forward gear, among which a ratio is always achieved by engaging a gear shaft. different input of the shaft used to achieve an immediately adjacent transmission ratio.
• 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 report while using the third report, prepare the fifth report while using the fourth report.
• it suffices to reverse the states of the clutches 8 to go up from a report to that immediately above. This allows for these reports a fast gear change, flexible and with an imperceptible power drop. It is the same for a decreasing ratio change.
• the ratio prepared but not activated rotates the input shaft 1 or 2 which is disengaged at a different speed than the motor 3,
• the control of the gearbox is robotized, partially or totally.
• the inversion of the clutches 8 is operated by controlled actuators. It is thus possible to eliminate any interruption in the transmission of power, since a clutch 8 can begin to "lick" when the other is not yet fully disengaged. This is impossible with the state of the art according to which a single mobile disk goes from one fixed disk to another.
• FIG. 8 will only be described for its differences with respect to that of FIGS. 1 to 7.
• the output shaft 4 carries, from its proximal end to its distal end, the following elements:
• a fifth, sixth and reverse gear S56R meshing with a second gear input gear E5 carried by the second input shaft 2, and with a sixth gear input gear E6 carried by the first input shaft 1; an output gear of first gear Sl meshing with an input gear of first gear El secured to the second input shaft 2;
• a seventh gear output gear S7 meshing with a seventh gear input gear E7, also optional, integral with the second input shaft 2.
• the output shaft 4 carries an output pinion SB at its proximal end, and another optional SB 'to its end distills. It is also possible to provide only the pinion SB '. Providing two output gears is convenient because one can drive the front wheels and the other the rear wheels of a four-wheel drive vehicle.
• the first input shaft 1 is placed functionally between the output shaft 4 and an intermediate shaft 15.
• the intermediate shaft 15 is permanently coupled with the first input shaft 1 by a pair of pinions 16, 17.
• the pinion 16 integral with the input shaft 1 has a smaller number of teeth than the pinion 17 integral with the intermediate shaft 15, which therefore rotates less rapidly than the input shaft 1
• the link 9 establishes a ratio 1 between the input shafts 1 and 2.
• the fourth gear ratio gear E4 meshes with a second gear input gear E2 carried by the intermediate shaft 15.
• the sixth gear input gear E6 is in meshing relation with a reverse gear input ER carried by the intermediate shaft 15.
• the aforementioned meshing relationship passes through a reversing gear 24 mounted idly in the crankcase. not shown of the gearbox.
• the offset representation of the pinion 24 means that its axis locates behind or in front of the common plane of the axes of the first input shaft 1 and the intermediate shaft 15.
• a coupler C2R couples one or the other of the input gears E2 and ER, or none of them, with the intermediate shaft 15.
• a coupler C46 couples one or the other of the input gears E4 and E6, or none of them, with the input shaft 1.
• a coupler C35 couples one or the other of the input gears E3 and E5, or none of them, with the input shaft 2.
• a coupler Cl (7) couples one or the other of the input gears S1 and S7, when it is provided, or none of them, with the output shaft 4.
• the gears S234 and S56R are integral with the output shaft 4.
• the reverse drive gear ER is coupled to the intermediate shaft 15 by means of the coupler C2R and the drive shaft 3 is engaged with the first input shaft 1.
• the gear ER input driven by the shaft 3 via the pair of pinions 16, 17 and the shaft 15, drives the output gear S56R via the reversing gear 24 and the input gear E6 driving idler rotating gear on the first input shaft 1 because the coupler C46 is in decoupling state of the two gears E4 and E ⁇ .
• the coupler Cl (7) can be placed in the coupling position of the output gear Sl with the output shaft 4. When this is done, the first transmission ratio is effectively formed by reversing the states of the clutches.
• the first gear ratio input gear El drives the output gear of first gear Sl and therefore the output shaft 4 to which this pinion is coupled.
• the coupler C2R can be left in the coupling position of the pinion ER so that the gearbox is ready to go in reverse, or be put in the coupling position of the input pinion of the second gear E2 to prepare the passage 'in second gear.
• the second report is effectively formed simply by reversing the conditions of the clutches 8 to engage the motor shaft 3 with the first one. input shaft 1.
• the second gear input gear E2 thus drives the output gear of second, third and fourth gear S234, and thus the output shaft 4 on which the latter pinion is fixed.
• the transmission of the movement of the pinion E2 to the output pinion S234 is effected by means of the input pinion of the fourth ratio E4 which turns freely on the first input shaft 1 because the coupler C46 is still in its decoupling state. of the two input pinions E4 and E6 with respect to the first shaft d ⁇ ' ⁇ ent "ree ⁇ T".
• the coupler Cl (7) can be left in the coupling position of the output gear Sl to prepare a return to the first gear, or this coupler can be put in the decoupling position and the coupler C35 can be changed to coupling position of the third gear input gear E3 to prepare for the transition to third gear operation.
• the operations and passages in third, fourth, fifth and sixth gear will not be detailed because they are very similar to the operations in first, second, third and fourth speed of the embodiment of FIG. 1.
• the coupler C35 can be left in the coupling position of the fifth gear ratio gear E5 with the second input shaft 2 to prepare a return to operation in the fifth gear, or, on the contrary, pass the coupler C35 in a state.
• the gearbox is particularly compact, two of the output gears each operate for three different transmission ratios, and despite this the values of all the ratios can be chosen independently of each other while the bulk is particularly reduced, as well as the total number of gears in the gearbox. This is made possible by the particular role of the input gears E4 and E6 which can either serve as a pinion coupled to a drive shaft.
• N ⁇ mBr ⁇ ⁇ ⁇ d ⁇ n ⁇ s of" a ratio of toothing determined, or be uncoupled from this shaft and used as a simple idler gear between the input pinions E2 and ER carried by the intermediate shaft 15, and 4.
• the invention is not limited to the examples described and shown.
• the permanent connection 9 can be made by a cascade of gears and not by a chain.
• FIG. 1a it is possible to obtain a spatially advantageous arrangement by folding the diagram along the axis of the first input shaft 1 and / or along the axis of the output shaft 4 , at will according to the desired implantation.

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• Engineering & Computer Science (AREA)
• General Engineering & Computer Science (AREA)
• Mechanical Engineering (AREA)
• Structure Of Transmissions (AREA)
• Arrangement And Driving Of Transmission Devices (AREA)

Applications Claiming Priority (2)

Publications (1)

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ID=34949676

Family Applications (1)

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• 2004
  • 2004-09-23 FR FR0410085A patent/FR2875567B1/fr not_active Expired - Fee Related
• 2005
  • 2005-09-20 TW TW094132444A patent/TW200613162A/zh unknown
  • 2005-09-21 AR ARP050103971A patent/AR050750A1/es unknown
  • 2005-09-22 EP EP05805792A patent/EP1815163A1/de not_active Withdrawn
  • 2005-09-22 CN CN200580032099.2A patent/CN101052825A/zh active Pending
  • 2005-09-22 WO PCT/FR2005/002348 patent/WO2006032789A1/fr active Application Filing
  • 2005-09-22 JP JP2007532926A patent/JP2008513707A/ja not_active Withdrawn
  • 2005-09-22 US US11/663,710 patent/US20080163710A1/en not_active Abandoned

Non-Patent Citations (1)

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