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
  • F16H2200/0052—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
  • 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
  • F16H3/089—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 all of the meshing gears being supported by a pair of parallel shafts, one being the input shaft and the other the output shaft, there being no countershaft involved
• • 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

Definitions

• the invention relates to a transmission for a vehicle, which is designed as a double clutch transmission, wherein the gears are combined to input shafts and an output shaft gear groups, wherein the gears of the gear groups of the input shafts with the gears of at least one gear group of the output shaft in permanent engagement, and wherein a first input shaft via a first clutch and a second input shaft via a second clutch to a drive shaft of a prime mover is connectable.
• a dual-clutch transmission is known, wherein the gears of the transmission are combined to form gear groups, which act on switching elements.
• the clutches are arranged at different end faces of the transmission and are driven by a single prime mover.
• a switching element for switching between different gears is designed so that it can be passed through the gear groups and thus can act on all gears of a gear group.
• WO 92/04558 Al describes a dual-clutch gear change transmission for motor vehicles, with two simultaneously oppositely controlled clutches.
• One of the higher gear ratios is connected as a gear shift with the one clutch.
• the other gear ratios are connectable to the other clutch.
• the first clutch which is controlled by means of its own switching device, the other gear ratios can be arbitrarily inserted.
• WO 2005/085674 A1 discloses a dual-clutch transmission for a vehicle with rear-wheel drive.
• a drive shaft may alternatively be connected to one of two input shafts, each input shaft having a plurality of first gears.
• On an output shaft a plurality of second gears are arranged, which mesh with the corresponding first gears of the input shafts.
• each second gear can be rotatably connected to the output shaft.
• the disadvantage is that a relatively high space and manufacturing costs are required.
• the object of the invention is to avoid these disadvantages and to achieve short switching times in a space-saving manner in a transmission of the type mentioned. In this case, the production cost should be reduced.
• first primary ratio between the input shaft and the first input shaft and a second primary ratio between the input shaft and the second input shaft, wherein preferably first and second primary ratios have different transmission ratios.
• the first primary ratio with the first clutch on the one hand and the second primary ratio with the second clutch on the other hand are arranged at different end faces of the transmission.
• a space-saving arrangement can be achieved if at least one of the two clutches is arranged coaxially with the drive shaft.
• the first clutch is coaxially arranged with the first input shaft and / or the second clutch coaxially with the second input shaft.
• first and second input shaft are spaced apart and have different axes of rotation, wherein preferably one gear of the gear group of the first input shaft and a gear of the gear group of the second input shaft with the same gear of a arranged on the output shaft output gear group in permanent intervention stands.
• first and second input shaft are arranged coaxially with each other.
• a freely rotatably mounted middle gear which is in permanent engagement with an associated gear of the output shaft, and which is arranged coaxially with the first and second input shaft, via at least one switching element optionally with the first or second input shaft is connectable.
• This design makes it possible to save a gear stage with the same number of gears.
• a switching element is arranged on both sides of the freely rotatable gear, wherein a rotational connection between the freely rotatable gear and the first or the second input shaft can be produced by moving the switching elements.
• the first and second input shafts are formed as a coaxially arranged behind one another hollow shafts, wherein between the two hollow shafts free rotatable gear is arranged, with which a freely rotatably mounted within the two hollow shafts inner shaft is rotatably connected and wherein the inner shaft is selectively rotatably connected via a switching element with the first input shaft or with the second input shaft.
• a switching element is arranged, by means of which either the first input shaft or the second input shaft is rotatably connected to the output shaft. It can be found with a very small number of switching elements Aus GmbH.
• FIGS. show schematically:
• FIG. 4 shows the dual-clutch transmission in a fourth embodiment in an end view.
• Figure 5 shows this dual-clutch transmission in a deployed plan view, with all the axles folded into the drawing plane.
• Fig. 8 the dual clutch transmission in a seventh embodiment.
• Trained as a double clutch transmission 1 has a first input shaft 2 with a first gear group 3 and a second input shaft 4 with a second gear group 5, and an output shaft 6 with corresponding gear groups 7, 8, wherein the gears of the first gear group 3 with gears of the third gear group 7 and the gears of the second gear group 5 with gears of the fourth gear group 8 are engaged.
• Reference numeral 9 denotes a driven wheel.
• the first input shaft 2 can be driven via the first clutch 10, the second input shaft 4 via the second clutch 12 by the drive shaft 11 of the internal combustion engine 15.
• two different primary drives 13, 14 are available for driving the input shafts 2, 4, whereby the primary drives 13, 14 can have different transmission ratios.
• the gears are indicated by G1, G2, G3, G4, G5, G6.
• FIGS. 4 and 5 show a variant embodiment of a transmission 1 in which the first and the second input shafts 2, 4 are not arranged on the same axis of rotation 2 a as provided in FIGS. 1 to 3 but offset from one another.
• the gears of the first gear group 3 and the gears of the second gear group 5 act on the same on the output shaft 6 arranged gears of the output gear group 16 a.
• the clutches 10, 12 may be arranged on the side of the input shafts 2, 4 or else on the side of the drive shaft 11.
• Fig. 6 shows a variant with arranged on a rotation axis 2a first and second input shafts 2, 4.
• switching elements 17, 18 are arranged between each two gears on the output shaft 6 of the third gear group 7 and the fourth gear group.
• the particular feature of this embodiment is that a further switching element 19 between the arranged on the output shaft 6 adjacent inner gears 20, 21 of the third gear group 7 and the fourth gear group 8 is provided.
• the inner shift element 19 can thus be used for shifting, for example, between the third and the sixth gear G3, G6.
• FIGS. 7 and 8 show alternative embodiments in which, between the first and the second gear group 3, 5, a freely rotating middle gear 22 is arranged coaxially with the first and second input shaft 2, 4 and is connected to a corresponding gear wheel 23 on the first gear wheel Output shaft 6 in per- manentem intervention.
• switching elements 24, 25 are arranged in Fig. 7, via which the central gear 22 with the first input shaft 2 or with the second input shaft 4 can be rotatably connected.
• the gears G5 and G6 can be switched by means of the shift elements 24, 25.
• the advantage of this design is that - compared to conventional 6-speed transmissions - a gear stage can be saved. Furthermore, a narrower design of the dual clutch transmission is possible.
• Fig. 8 differs from the embodiment shown in Fig. 7 in that the first and the second input shaft 2, 3 are formed as hollow shafts, within the hollow shafts, an inner shaft 27 is freely rotatably mounted, wherein the inner shaft 27 with the central gear 22 is rotatably connected, and wherein the rotary connection via an axially displaceable shaft-hub connection 26 takes place.
• the inner shaft 27 can be displaced axially between a first and a second position via a switching element 28 designed as a sliding sleeve, the switching element 28 rotating with the first input shaft 2 and being axially displaceable thereon.
• the axial movement of the switching element 28 is transmitted directly to the inner shaft 27, which - depending on the direction of movement - via a shaft-hub connection 29, 30 with the first or second input shaft 2, 4 is rotatably connected and thus the first input shaft 2 or the second input shaft 4 connects to the middle gear 22.
• different translations according to the gear stages G5, G6 can be realized in combination with differently translated primary gears 13, 14.
• the switching elements 17, 18 for switching gear stages Gl, G3, and G2, G4 on the side of the first and second input shaft 2, 4 are arranged.
• the reference numerals 31, 32 denote sliding or roller bearings for supporting the inner shaft 27, and for supporting the first and second input shafts 2, 4.
• the embodiment of FIG. 8 has the advantage that a switching element can be saved and thus an even more compact design of the dual clutch transmission can be realized.

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

Priority Applications (2)

Applications Claiming Priority (2)

Publications (2)

Family

ID=38565648

Family Applications (1)

Country Status (4)

Cited By (4)

Families Citing this family (3)

Citations (8)

Family Cites Families (5)

• 2007
  • 2007-06-28 AT AT0100607A patent/AT503476B1/de not_active IP Right Cessation
• 2008
  • 2008-06-20 CN CN2008800223163A patent/CN101730805B/zh not_active Expired - Fee Related
  • 2008-06-20 WO PCT/EP2008/057827 patent/WO2009000755A2/de active Application Filing
  • 2008-06-20 DE DE112008001725.5T patent/DE112008001725B4/de not_active Expired - Fee Related

Patent Citations (8)

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