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
• • 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
  • 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
  • F16H3/02—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
• • 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
  • F16H2003/0933—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 coaxial countershafts
• • 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
• • 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
• • 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

Definitions

• the invention relates to a motor vehicle gearbox.
• gearbox with parallel shafts and two clutches comprising a solid primary shaft and a concentric hollow primary shaft, and two non-concentric secondary shafts.
• the present invention aims to remedy the drawbacks of this known box.
• the first secondary shaft carry a down pinion directly attacking a crown of differential and that the second secondary shaft the crown by means of a deflection shaft on the first secondary shaft and the same descent pinion.
• the primary shafts have several fixed teeth meshing with idler gears from one or the other of the secondary shafts, including at least two fixed toothing which meshes simultaneously with a idler gear of each secondary shaft and a fixed toothing which meshes simultaneously with a idler gear for forward and with an intermediate gear for reverse gear.
• the bubbling problem of the known box is solved by the fact that the axes of the primary and secondary shafts define a triangle, the angle of which having the apex of the primary shafts is an obtuse angle open upwards.
• FIG. 1 is a schematic sectional view through folded-down planes, along the line in FIG. 4, passing through the axes of the primary and secondary shafts
• FIG. 2 is a schematic sectional view with folded-down planes, along the line in FIG. 4 passing through the axes of the auxiliary secondary shafts, intermediate reverse, primary and primary secondary
• Figure 3 is a schematic sectional view with folded planes, along a line in Figure 4, passing through the axes of the auxiliary secondary shafts, intermediate return and main secondary
• FIG. 4 is a view according to FIG. 2 showing the path of the torque according to the reverse gear
• FIG. 1 shows a schematic view of a gearbox 10 produced according to the invention.
• the gearbox 10 comprises a first solid primary shaft 20 which is mounted coaxially with a second hollow primary shaft 30. These two shafts are rotatably mounted in a casing (not shown) and driven by a motor respectively by the 'through a first clutch 40 and a second clutch 41, which are by way of example, and without limitation, wet multi-plate clutches.
• the gearbox also comprises a first secondary shaft 50 and a second said principal secondary auxiliary shaft 60 is, also mounted rotatably in the housing. These secondary shafts are coaxial.
• the axes of the primary shafts 20, 30 and secondary 50, 60 define a triangle, the angle of which having for apex the axis of the primary shafts 20, 30 is an obtuse angle open upwards.
• the secondary trees thus form a very open V with axes of the primary trees, the apex of which is occupied by the axes of the primary trees.
• Gears are arranged between the primary shafts 20 and 30 and the secondary shafts 50 and 60 so as to transmit the torque of the vehicle to a crown 70 (shown in FIG. 4) of a differential of a bridge (not shown) driving the wheels of a vehicle.
• a crown 70 shown in FIG. 4
• a differential of a bridge not shown
• the main secondary shaft 50 has a lowering pinion 51 which meshes with the crown 70 of the differential and the auxiliary secondary shaft 60 is linked in rotation to the secondary shaft 50 by idler shaft 75 carrying fixed pinions 76 and 77 meshing with fixed pinions 52 and 62 carried respectively by the shafts secondary 50 and 60.
• Gears are made of fixed teeth which are carried by the first and the second input shafts 20 and 30, and which mesh with idler gears which are carried by the secondary shafts 50 and 60.
• the idler gears are capable of being selectively linked in rotation to the first and second secondary shafts 50 and 60 by independent clutch means for producing independent gears selectively corresponding to at least two forward gears and a reverse gear.
• the two clutches 40 of the first primary shaft 20 and 41 of the second primary shaft 30 are moreover capable of being actuated alternately, passing through a state in which they both transmit the torque by sliding of one of them, for allow at least one gear change without discontinuity of torque transmitted to the wheels.
• the first primary shaft 20 has two fixed teeth, from left to right, 21 and 22.
• the first meshes with a single idler gear 81, carried by the first shaft secondary 50, to constitute the first report.
• the second meshes with two idler gears 82 and 83, respectively carried by the first secondary shaft 50 for constitute the fifth report and by the second secondary shaft 60 to constitute the third report.
• the second hollow primary shaft 30 also carries two fixed sets of teeth, from left to right 31 and 32.
• the reverse gear ratio has its own idler pinion 87 carried by the second secondary shaft 60, which meshes with an intermediate gear 90 carried by the intermediate shaft 75, coupled in rotation with the second intermediate gear 91 which meshes with the toothing 32 fixed to the primary shaft 30.
• the intermediate gear 91, 90 rotates on the shaft mad intermediate 75.
• the primary shafts 20, 30 carry several fixed teeth 21, 22, 31, 32 meshing with idler gears (81, 82, 83, 84, 85, 86), from one or the other of the secondary shafts (50, 60), at least two fixed gears 22, 31 meshing simultaneously with an idler gear 82, 83, 84, 85 of each secondary shaft 50, 60 and one fixed gear 32 meshes simultaneously with an idler gear forward 86 and with the intermediate pinion 91 back on.
• This arrangement makes it possible to obtain six forward reports and a reverse report with only two fixed teeth 21 and 22 on the first solid primary shaft 20 for obtain the odd ratios and two fixed toothing 31 and 32 on the second hollow primary shaft 30 to obtain the even ratios and the reverse gear.
• the fixed teeth 22, 31, and 32 each mesh with two pinions, the first with the idler pinions 82 and 83, the second with the idler pinions 84 and 85, the third with the idler pinion 86 and the reverse reverse gear 91 .
• the idler reverse gear 87, the intermediate reverse gear 90 and the idler gears 62 and 76 are arranged in the same axial section as the drive gear 51.
• the gearbox proposed by the invention has the same axial size as a four-speed gearbox, to obtain six forward ratios and one reverse ratio. It is therefore particularly compact.
• the distances between the axes of the primary shafts 20, 30 and the two secondary shafts 60 can be different. However, they will preferably be identical. Indeed, provided also choose identical interconnection devices, it is also possible to use identical idler pinions. According to the invention, the pinions 82 of the fifth gear and 83 of the third gear can therefore be identical, as well as the pinions 84 of the sixth gear and 85 of the fourth gear.
• the toothed wheels 52 of the first secondary shaft 50, 62 of the second secondary shaft 60 and 76, 77 of the idler shaft can thus have appropriate number of teeth ratios. to obtain different ratios from a fixed toothing which meshes with two identical idler gears.
• the first and second clutches 40 and 41 make it possible to selectively link the first solid primary shaft 20 carrying the fixed teeth 21 and 22 of the odd ratios and the second hollow primary shaft 30 which carry the fixed teeth 31 and 32 of the even ratios to the motor.
• all the idler gears can be selectively linked to the secondary shafts which carry them by single or double dog clutch devices.
• the idler gears 81, 82, 84 and 86 can be selectively linked to the secondary shaft 50 which carries them and the idler gears 83, 85 and 87 can be selectively linked to the secondary shaft 60 which carries them.
• a first clutching device 100 allows dual selectively connect in rotation to the secondary shaft 50 the pinion 81 mad to obtain the ratio of the first or the idler gear 82 for the fifth gear ratio.
• a second double clutch device 101 makes it possible to link the idler gear 84 in rotation to the secondary shaft 50 to obtain the sixth gear or the idler gear 86 to obtain the second gear.
• a third double interconnection device 102 makes it possible to selectively link in rotation with the secondary shaft 60 the idler gear 85 to obtain the fourth gear or the idler gear 87 to obtain the reverse gear ratio, finally a single clutch 103 allows to link selectively rotating at the secondary shaft 60 the idler gear 83 to obtain the third gear.
• Figure 4 illustrates the path of the engine torque to the differential gear on the reverse gear.
• the torque is transmitted from the motor to the primary shaft 30 by the clutch 41 closed, then from the fixed toothing 32 to the pinion first intermediate reverse gear 91 linked to the second intermediate gear 90, then from the second intermediate reverse gear 90 to the idler gear 87 in reverse which transmits it to the secondary shaft 60 by means of the double clutch 102 in the clutched position on the pinion 87, then from the secondary shaft 60 to the pinion 62, then to the fixed pinion 76 of the intermediate return shaft 75, then from the intermediate return shaft 75 to the fixed pinion 77 which transmits the movement to the fixed pinion 52 of the main secondary shaft 50 which transmits it, via the drive pinion 51 to crown 70.
• the torque path is similar for the third and fourth ratios since the idler gears 83 and 85 are carried by the auxiliary secondary shaft 60.
• the path of the torque from the engine to the differential ring gear according to the first gear can be as follows.
• the torque is transmitted from the engine to the primary shaft 20 by the closed clutch 40, then from the fixed toothing 21 to the idler gear 81, then from the idler gear 81 to the secondary shaft 50 by the double dog clutch 100 in the dog clutch position.
• the pinion 81 then from the secondary shaft 50 to the fixed pinion 51 which transmits it to the crown 70.
• the torque path is similar for the fifth, sixth and second ratios since the idler gears 82, 84 and 86 are carried by the auxiliary secondary shaft 50.

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• Engineering & Computer Science (AREA)
• General Engineering & Computer Science (AREA)
• Mechanical Engineering (AREA)
• Structure Of Transmissions (AREA)

Applications Claiming Priority (2)

Publications (1)

Family

ID=33396733

Family Applications (1)

Country Status (6)

Families Citing this family (7)

Family Cites Families (6)

• 2003
  • 2003-05-23 FR FR0306266A patent/FR2855229B1/fr not_active Expired - Fee Related
• 2004
  • 2004-05-17 US US10/557,712 patent/US20070056398A1/en not_active Abandoned
  • 2004-05-17 JP JP2006530362A patent/JP2007500832A/ja not_active Withdrawn
  • 2004-05-17 KR KR1020057022207A patent/KR20060013549A/ko not_active Application Discontinuation
  • 2004-05-17 EP EP04742762A patent/EP1627163A1/de not_active Withdrawn
  • 2004-05-17 WO PCT/FR2004/001214 patent/WO2004106774A1/fr not_active Application Discontinuation

Non-Patent Citations (1)

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