EP2920487A1 - Boîte de vitesses à rapports multiples - Google Patents

Boîte de vitesses à rapports multiples

Info

Publication number
EP2920487A1
EP2920487A1 EP13776775.2A EP13776775A EP2920487A1 EP 2920487 A1 EP2920487 A1 EP 2920487A1 EP 13776775 A EP13776775 A EP 13776775A EP 2920487 A1 EP2920487 A1 EP 2920487A1
Authority
EP
European Patent Office
Prior art keywords
shaft
planetary gear
clutch
gear set
gear
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Withdrawn
Application number
EP13776775.2A
Other languages
German (de)
English (en)
Inventor
Stefan Beck
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
ZF Friedrichshafen AG
Original Assignee
ZF Friedrichshafen AG
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by ZF Friedrichshafen AG filed Critical ZF Friedrichshafen AG
Publication of EP2920487A1 publication Critical patent/EP2920487A1/fr
Withdrawn legal-status Critical Current

Links

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
    • F16H3/44—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion using gears having orbital motion
    • F16H3/62—Gearings having three or more central gears
    • F16H3/66—Gearings having three or more central gears composed of a number of gear trains without drive passing from one train to another
    • 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
    • F16H3/44—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion using gears having orbital motion
    • F16H2003/445—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion using gears having orbital motion without permanent connection between the input and the set of orbital gears
    • 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
    • F16H2200/0065—Transmissions for multiple ratios characterised by the number of forward speeds the gear ratios comprising nine 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
    • F16H2200/20—Transmissions using gears with orbital motion
    • F16H2200/2002—Transmissions using gears with orbital motion characterised by the number of sets of orbital gears
    • F16H2200/201—Transmissions using gears with orbital motion characterised by the number of sets of orbital gears with three sets of orbital gears
    • 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
    • F16H2200/20—Transmissions using gears with orbital motion
    • F16H2200/203—Transmissions using gears with orbital motion characterised by the engaging friction means not of the freewheel type, e.g. friction clutches or brakes
    • F16H2200/2046—Transmissions using gears with orbital motion characterised by the engaging friction means not of the freewheel type, e.g. friction clutches or brakes with six engaging means

Definitions

  • the present invention relates to a multistage transmission, in particular an automatic transmission for a motor vehicle, according to the preamble of patent claim 1.
  • Automatic transmissions particularly for motor vehicles, include, in the prior art, planetary gear sets that are switched by means of friction elements, such as clutches and brakes, and usually with a slip element and optionally a lockup clutch, such as a hydrodynamic torque converter or a fluid coupling connected.
  • friction elements such as clutches and brakes
  • slip element such as clutches and brakes
  • lockup clutch such as a hydrodynamic torque converter or a fluid coupling connected.
  • Such automatic transmissions are often described in the prior art and are subject to permanent development and improvement. So these transmissions should have a sufficient number of forward gears and at least one reverse gear and a transmission very well suited for motor vehicles with a high overall spread and favorable increments. Furthermore, these should allow a high starting ratio in the forward direction and contain a direct gear. In addition, automatic transmissions require a low construction cost and a small number of switching elements, with sequential switching mode in each case only one switching element is switched on and a switching element to be switched off.
  • Such an automatic transmission is for example from the
  • a fourth shaft is connected to the sun gear of the first planetary gear set and the sun gear of the second planetary gear set, can be coupled via a first brake to the housing of the transmission and over a first clutch releasably connectable to the drive shaft, wherein the drive shaft via a second clutch with a connected to the ring gear of the second planetary gear seventh shaft and a third clutch with an eighth shaft is releasably connectable, which with the ring gear of the third planetary gear and the web connected to the fourth planetary gear set and can be coupled via a second brake to the housing.
  • the ring gear of the first planetary gear set is connected to a sixth shaft connected to the land of the second planetary gear set and the ring gear of the fourth planetary gear set, with a third shaft connected to the sun gear of the third planetary gear set and the sun gear of the fourth planetary gear set connected and via a third brake to the housing is coupled and wherein the output shaft is connected to the web of the third planetary gear set.
  • DE 10 2009 028 670 A1 is disadvantageously unsuitable for installation as a front-transverse system.
  • DE 10 2010 010 122 A1 discloses a multi-speed hybrid transmission, comprising an input element, an output element, first, second and third planetary gear sets, each having first, second and third elements, the wheelsets being along first and third second axis and a first, second and third outer gear set, which are arranged for transmitting torque between the first and second axis, wherein the first, second and third outer gear set respectively comprise first and second meshing outer wheels.
  • the known transmission comprises a motor / generator operatively connected to the first outer wheel of the second outer gear set and five torque transmitting means for selectively connecting the elements of the planetary gear sets or the first and second outer wheels with each other, with a stationary member, with the input member or with others Elements of the planetary gear sets, wherein the five torque transmitting devices are engaged in combinations of three, to produce at least eight forward gears and at least one reverse gear between the input element and the output element.
  • the present invention has for its object, starting from a transmission according to DE 10 2009 028 670 A1 to provide a multi-step transmission, which axially considered a small space requirement, so that installation of the transmission and optionally enables hybridization of the transmission as a front-transverse system becomes.
  • a multi-stage transmission which has a drive shaft and an output shaft, which are arranged in a housing and parallel to each other.
  • the transmission comprises three planetary gear sets, hereinafter referred to as first, second and third planetary gear set, wherein a planetary gear coaxial with a first axis, which is defined by the drive shaft and two planetary gear coaxial with a second axis, which is arranged parallel to the first axis is defined by the output shaft are arranged, at least ten rotatable shafts - hereinafter referred to as drive shaft, output shaft, third, fourth, fifth, sixth, seventh, eighth, ninth and tenth wave - a first, a second and a third spur and six switching elements, comprising two brakes and four clutches, the selective engagement causes different ratios between the drive shaft and the output shaft, so that preferably nine forward gears and one reverse gear can be realized.
  • the planetary gear sets are preferably designed as negative planetary gear sets.
  • a simple minus planetary gear known to include a sun gear, a ring gear and a ridge on which planet gears are rotatably mounted, each meshing with the sun gear and ring gear. In this way, the ring gear at a fixed web on a sun gear opposite direction of rotation.
  • a simple plus planetary gear includes a sun gear, a ring gear and a web on which inner and outer planet wheels are rotatably mounted, wherein all inner Combining planet gears with the sun gear and all outer planetary gears with the ring gear, wherein each inner planetary gear meshes with an outer planetary gear.
  • the ring gear has the same direction of rotation when the web is held on as the sun gear and there is a positive gear ratio translation.
  • a very short overall length is achieved, so that the transmission can be installed in front-transverse construction.
  • the drive shaft is operatively connected via an eighth and a ninth shaft, a third or fifth clutch and a first spur gear with the ring gear of the second planetary gear set and the web of the third planetary gear set and a first clutch with one with the sun gear the first planetary gear set connected to the third shaft releasably connectable, which is coupled via a first brake to the housing of the transmission and via a fourth or sixth clutch, a fifth and tenth shaft and a third spur gear with the ring gear of the third planetary gear set is operatively connected; Furthermore, the drive shaft via a second clutch with a connected to the ring gear of the first planetary gear set seventh shaft is detachably connectable.
  • a sixth shaft is connected to the bridge of the first planetary gear set and operatively connected via a second spur gear to the tenth shaft connected to the ring gear of the third planetary gear set, wherein the output shaft is connected to the web of the second planetary gear set and a fourth shaft to the sun gear of second planetary gear set and the sun gear of the third planetary gear set and coupled via a second brake to the housing can be coupled.
  • the drive shaft via a third clutch with the eighth wave is releasably connectable, which is operatively connected via a first spur gear with the connected to the ring gear of the second planetary gear set and the third planetary gear set ninth wave.
  • the drive shaft via the first spur gear be operatively connected to the eighth wave, which is releasably connectable via a fifth clutch to the ninth shaft connected to the ring gear of the third planetary and the web of the fourth planetary gear, wherein the third clutch is eliminated.
  • the fourth clutch is arranged coaxially to the second axis, axial space can be saved along the first axis.
  • the third shaft can be detachably connectable via a fourth clutch to the fifth shaft, which is operatively connected via a third spur gear stage to the tenth shaft connected to the ring gear of the third planetary gearset.
  • the third shaft can be operatively connected via the third spur gear to the fifth shaft, which can be detachably connected via a sixth clutch to the tenth shaft connected to the ring gear of the third planetary gear set, wherein the fourth clutch is dispensed with.
  • the sixth clutch is arranged coaxially to the second axis, so that in an advantageous manner axial space can be saved along the first axis.
  • the drive shaft directly connected to the ring gear of the first planetary and not detachably connectable via the second clutch and a seventh shaft, wherein the second clutch is eliminated.
  • the third wave is via a seventh clutch with a connected to the sun gear of the first planetary gear seventh shaft detachably connectable or the sixth shaft is releasably connectable via an eighth clutch with a connected to the web of the first planetary gear seventh shaft.
  • the sixth shaft can be operatively connected via the second spur gear to a seventh shaft, which can be detachably connected via a ninth clutch to the tenth shaft connected to the ring gear of the third planetary gearset.
  • the ratio of the first and second spur gears of the transmission 1, 0.
  • the inventive design of the multi-speed transmission results in particular for passenger cars suitable translations and increased total spread of the multi-speed transmission, whereby an improvement in ride comfort and a significant consumption reduction can be effected.
  • the construction cost is significantly reduced with the multistage transmission according to the invention by a small number of switching elements, which has a positive effect on the weight and the cost.
  • a switching element which is actuated in the first forward gear and in reverse is suitable.
  • Figure 1 is a schematic view of a first preferred embodiment of a multi-speed transmission according to the invention
  • Figure 2 is a schematic view of a second preferred embodiment of a multi-speed transmission according to the invention.
  • FIG. 3 shows an exemplary circuit diagram for a multistage transmission according to FIGS. 1 and 2;
  • FIG. 4 shows a schematic view of a hybridized multistage transmission based on the embodiment according to FIG. 1;
  • FIG. 5 shows a schematic view of a further embodiment of a hybridized multistage transmission based on the embodiment according to FIG. 2;
  • FIG. 6 shows a schematic view of a further preferred embodiment of a multistage transmission according to the invention.
  • FIG. 7 is a schematic view of another preferred embodiment of a multi-speed transmission according to the invention.
  • FIG. 8 shows a schematic view of a further preferred embodiment of a multistage transmission according to the invention.
  • first planetary gearset P1 shows a multistage transmission according to the invention, with a first planetary gearset P1, a second planetary gearset P2 and a third planetary gearset P3, wherein the first planetary gear set P1 coaxial with a first axis, which is defined by the drive shaft 1 and the second and third planetary gear set P2 P3 is arranged coaxially with a second axis arranged parallel to the first axis and defined by the output shaft 2.
  • the planetary gear sets P1, P2, P3 are executed in the example shown as minus planetary gear sets.
  • at least one planetary gear set of the transmission can be designed as a plus planetary gear set, if at the same time the web and Hohlradanulation exchanged and the amount of the stationary gear ratio is increased by 1 compared to the design as a minus planetary gear.
  • the clutches and the brakes of the transmission are preferably designed as friction shift elements or slat lenschaltiata, but can also be designed as a form-locking switching elements.
  • the multi-speed transmission according to the invention has a total of at least ten rotatable shafts, wherein the drive shaft, the first shaft 1 and the output shaft forms the second shaft 2 of the transmission.
  • the drive shaft 1 can be detachably connected via a first clutch 18 to an eighth shaft 8, which is designated by a first spur gear stage S1, whose first spur gear is designated ST1 and whose second spur gear is designated ST2 one connected to the ring gear of the second planetary gear set P2 and the web of the third planetary gear set P3 ninth shaft 9 is operatively connected.
  • the drive shaft 1 is over an ne first clutch 13 with a connected to the sun gear of the first planetary gear set P1 third shaft 3 releasably connectable, wherein the third shaft 3 can be coupled via a first brake 03 to the housing G of the transmission and a fourth clutch 35 with a fifth shaft 5 detachably is connectable, which is operatively connected via a third spur gear S3, the first spur gear with ST5 and the second spur gear with ST6, with a connected to the ring gear of the third planetary gear set P3 tenth shaft 10.
  • the drive shaft 1 via a second clutch 17 with a connected to the ring gear of the first planetary gear set P1 seventh shaft 7 detachably connectable.
  • a sixth shaft 6 is connected to the web of the first planetary gear P1 and a second spur gear S2, the first spur gear ST3 and the second spur gear is denoted by ST4, connected to the ring gear of the third planetary gear set P3 tenth wave 10 operatively connected, wherein the output shaft 2 is connected to the web of the second planetary gear set P2 and a fourth shaft 4 connected to the sun gear of the second planetary gear P2 and the sun gear of the third planetary gear set P3 and can be coupled via a second brake 04 to the housing G.
  • first, second, third and fourth clutches 13, 17, 17, 35 and the first brake 03 are arranged coaxially with the first axis defined by the drive shaft 1.
  • the example shown in Figure 2 differs from the embodiment of Figure 1 for one fact that the drive shaft 1 is operatively connected via the first spur gear S1 with the eighth shaft 8, which via a fifth clutch 89 with the ring gear of the second planetary gear P2 and
  • the ninth shaft 9 connected to the web of the third planetary gear set P3 can be detachably connected, the third clutch 18 being omitted.
  • This arrangement variant in which the fifth clutch 89 is arranged about the second axis, which is defined by the output shaft 2, results in the advantage that along the first axis axial space can be saved.
  • the example shown in FIG. 2 also differs from the embodiment according to FIG.
  • the first and second clutches 13, 17 and the first brake 03 are arranged coaxially with the first axis.
  • FIG. 3 shows an exemplary circuit diagram of a multistage transmission according to FIGS. 1 and 2. For each gear three switching elements are closed.
  • the shift scheme, the respective ratios i of the individual grades and the gear ratios to be determined therefrom or increments ⁇ to the next higher gear are exemplified, the value of 9.002 represents the spread of the transmission.
  • the values for the stationary gear ratios of the planetary gear sets P1, P2, P3 designed as minus planetary gear sets are respectively -2.371, -2.808 and -2.981 in the example shown, wherein the ratios of the first and second spur gear S1, S2 are 1, 000 and the gear ratio the third spur gear is 2.087. From Figure 3 it is seen that in sequential switching mode only one switching element switched on and a switching element must be switched off because two adjacent gear stages use two switching elements together. Furthermore, it will be seen that a large spreading is achieved with small gear jumps.
  • the first forward speed results from closing the second brake 04 and the second and fourth clutches 17, 35, the second forward speed by closing the first and second brakes 03, 04 and the second clutch 17, the third forward speed Close the second brake 04 and the first and second clutch 13, 17, the fourth forward speed by closing the second brake 04 and the second and third clutches 17, 18, which in the example shown executed a direct gear fifth forward gear by closing the first, second and third clutch 13, 17, 18, the sixth forward speed by closing the first brake 03 and the second and third clutches 17, 18, the seventh forward speed by closing the second, third and fourth clutches 17, 18, 35, the eighth forward speed by closing the first brake 03 and the third and fourth clutch 18, 35 and the ninth forward gear is obtained by closing the first, third and fourth clutch 13, 18, 35, wherein the reverse by closing the second brake 04 and the first and fourth clutch 13, 35 results.
  • the fourth forward gear may alternatively by closing the second brake 04 and the third and fourth clutch 18, 35, or by closing the second brake 04 and the first and third clutch 13, 18 or by closing the first and second brake 03, 04 and the third clutch 18 can be realized. These combinations are designated in FIG. 3 with M4 ', M4 "or M4'".
  • the circuit diagram differs from the circuit diagram of Figure 3 only in that the third clutch 18 is replaced by the fifth clutch 89 and that the fourth clutch 35 is replaced by the sixth clutch 15.
  • this switching element can be used as a starting element.
  • FIG. 4 corresponds to the exemplary embodiment according to FIG. 1 with the difference that an electric machine E is used. see which is arranged on the drive shaft 1 of the transmission and is directly connected to the drive shaft 1.
  • a tenth clutch KO be provided, through which the internal combustion engine, not shown, can be decoupled from the transmission, whereby all gears of the transmission can be driven purely electric.
  • the electric machine may be arranged axially parallel to the drive shaft 1 and connected to the drive shaft 1 via a wheel step or a chain drive.
  • This embodiment is the subject of Figure 5.
  • the gear shown here corresponds to the transmission of Figure 1 with the difference that an electric machine E is arranged axially parallel to the drive shaft 1 and connected via a further fourth spur gear S4 to the drive shaft 1.
  • the first spur gear ST1 of the first spur gear stage S1 is used for the third spur gear stage S3, whereby the assembly and cost expenditure is reduced, since only an additional spur gear ST7 is required.
  • a tenth clutch KO is arranged between the internal combustion engine (not shown) and the drive shaft 1 in order to enable purely electric driving.
  • the drive shaft 1 can be detachably connected via a third clutch 18 to an eighth shaft 8, which is designated by a first spur gear stage S1, whose first spur gear is designated ST1 and whose second spur gear is designated ST2, and one with the ring gear the second planetary gear set P2 and the web of the third planetary gear set P3 connected ninth shaft 9 is operatively connected.
  • the drive shaft 1 via a first clutch 13 with a third shaft 3 is releasably connectable, wherein the third shaft 3 is coupled via a first brake 03 to the housing G of the transmission, via a seventh clutch 37 with one with the sun gear of the first planetary gear set P1 connected seventh shaft 7 is detachably connectable and via a fourth clutch 35 with a fifth shaft 5 is detachably connected, which is denoted by a third spur gear S3, the first spur gear with ST5 and the second spur gear with ST6, with one with the ring gear of the third planetary gear set P3 connected tenth shaft 10 is operatively connected.
  • the drive shaft 1 is connected directly to the ring gear of the first planetary gear P1.
  • a sixth shaft 6 is connected to the web of the first planetary gear set P1 and a second spur gear S2, whose first spur gear with ST3 and whose second spur gear is denoted by ST4, connected to the ring gear of the third planetary gear set P3 tenth wave 10 operatively connected, wherein the output shaft 2 is connected to the web of the second planetary gear set P2 and a fourth shaft 4 connected to the sun gear of the second planetary gear P2 and the sun gear of the third planetary gear set P3 and can be coupled via a second brake 04 to the housing G.
  • the example shown in Figure 6 differs from the embodiment of Figure 1 in that the drive shaft 1 is directly connected to the ring gear of the first planetary gear set P1 and that the third shaft 3 is not directly connected to the sun gear of the first planetary P1, but on the seventh shaft 7 and the seventh clutch 37 is releasably connectable.
  • the example shown in Figure 2 can be modified analogously to the embodiment of Figure 6, so that the drive shaft 1 is directly connected to the ring gear of the first planetary gear P1, wherein the third shaft 3 is not directly connected to the sun gear of the first planetary P1, but via the seventh shaft 7 and the seventh clutch 37 is releasably connectable.
  • the drive shaft 1 via a third clutch 18 with an eighth shaft 8 detachably connectable which is designated by a first spur gear S1, the first spur gear with ST1 and the second spur gear with ST2, with one connected to the ring gear of the second planetary gear set P2 and the web of the third planetary gear set P3 ninth shaft 9 is operatively connected.
  • the drive shaft 1 via a first clutch 13 with a connected to the sun gear of the first planetary gear set P1 third shaft 3 is detachably connectable, wherein the third shaft 3 can be coupled via a first brake 03 to the housing G of the transmission and a fourth clutch 35 is releasably connectable to a fifth shaft 5, which is operatively connected via a third spur gear S3, whose first spur gear with ST5 and the second spur gear with ST6, with a tenth shaft 10 connected to the ring gear of the third planetary gear P3.
  • the drive shaft 1 is connected directly to the ring gear of the first planetary gear P1.
  • a sixth shaft 6 is detachably connectable via an eighth clutch 67 to a seventh shaft 7 connected to the web of the first planetary gear set P1 and to a second spur gear S2, whose first spur gear is designated ST3 and whose second spur gear is designated ST4.
  • operatively connected to the tenth shaft 10 connected to the ring gear of the third planetary gear set P3, the output shaft 2 being connected to the land of the second planetary gear set P2, and a fourth shaft 4 being connected to the sun gear of the second planetary gear set P2 and the sun gear of the third planetary gear set P3 and over a second brake 04 can be coupled to the housing G.
  • the example shown in Figure 7 differs from the embodiment of Figure 1 in that the drive shaft 1 is directly connected to the ring gear of the first planetary gear P1 and that the sixth shaft 6 with the web of the first planetary gear set P1 is not directly connected, but on the seventh shaft 7 and the eighth clutch 67 is releasably connectable.
  • the example shown in Figure 2 can be modified analogous to the embodiment according to Figure 7, so that the drive shaft 1 is directly connected to the ring gear of the first planetary gear P1, wherein the sixth shaft 6 is not directly connected to the web of the first planetary gear P1, but via the seventh shaft 7 and the eighth clutch 67 is releasably connectable.
  • the drive shaft 1 via a third clutch 18 with an eighth shaft 8 detachably connectable, which via a first spur gear S1 with a with the ring gear of the second planetary gear P2 and the web of third planetary gear P3 connected ninth shaft 9 is operatively connected. Furthermore, the drive shaft 1 is connected to the sun gear of the first planetary gear via a first clutch 13.
  • tenradsatzes P1 connected third shaft 3 detachably connectable, wherein the third shaft 3 is coupled via a first brake 03 to the housing G of the transmission and via a fourth clutch 35 with a fifth shaft 5 is releasably connectable, which via a third spur gear S3 with a connected to the ring gear of the third planetary gear set P3 tenth shaft 10 is operatively connected.
  • the drive shaft 1 is connected directly to the ring gear of the first planetary gear P1.
  • a connected to the web of the first planetary gear P1 sixth shaft 6 is operatively connected via a second spur gear S2 with a seventh shaft 7 which is releasably connectable via a ninth clutch 107 to the tenth shaft 10 connected to the ring gear of the third planetary gear P3, wherein the output shaft 2 is connected to the bridge of the second planetary gearset P2 and a fourth shaft 4 is connected to the sun gear of the second planetary gear set P2 and the sun gear of the third planetary gear set P3 and can be coupled to the housing G via a second brake 04.
  • the example shown in Figure 8 differs from the embodiment of Figure 1 in that the drive shaft 1 is directly connected to the ring gear of the first planetary P1 and that the sixth shaft 6 with the tenth shaft 10 is not directly connected via the second spur gear S2 operatively connected but via the second spur gear S2, the seventh shaft 7 and the ninth clutch 107 is releasably operatively connected.
  • the example shown in Figure 2 can be modified analogously to the embodiment according to Figure 8, so that the drive shaft 1 is directly connected to the ring gear of the first planetary gear set P1, wherein the sixth shaft 6 with the tenth shaft 10 is not directly operatively connected, but on the second Spur gear S2, the seventh shaft 7 and the ninth clutch 107 is releasably operatively connected.
  • an electrical machine or a further drive source can be arranged on each shaft of the transmission according to the invention.
  • an axle differential and / or a distributor differential can be arranged according to the invention.
  • the drive shaft 1 can be separated by a coupling element from a drive motor as needed, wherein a hydrodynamic converter, a hydraulic clutch, a dry starting clutch, a wet starting clutch, a magnetic powder clutch or a centrifugal clutch can be used as a coupling element. It is also possible to arrange such a starting element in the power flow direction behind the transmission, in which case the drive shaft 1 is constantly connected to the crankshaft of the drive motor.
  • the multi-speed transmission according to the invention also makes it possible to arrange a torsional vibration damper between the drive motor and the transmission.
  • a wear ßMap brake such as a hydraulic or electric retarder or the like, arranged, which is particularly suitable for use in commercial vehicles is of particular importance.
  • a power take-off may be provided to drive additional units on each shaft, preferably on the drive shaft 1 or the output shaft 2.
  • the friction shift elements used can be designed as power shift clutches or brakes.
  • non-positive clutches or brakes such as multi-plate clutches, band brakes and / or cone clutches can be used.
  • the switching elements used can be designed as a form-locking switching elements.

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

Abstract

L'invention concerne une boîte de vitesses à rapports multiples comprenant un arbre primaire (1), un arbre de sortie (2), qui sont disposés parallèlement l'un à l'autre, trois trains planétaires, le premier train planétaire (P1) étant disposé coaxialement par rapport à un premier axe qui est défini par l'arbre primaire (1), et le deuxième et le troisième trains planétaires (P2, P3) étant disposés coaxialement par rapport à un deuxième axe qui est disposé parallèlement au premier axe et qui est défini par l'arbre de sortie (2), l'arbre primaire (1) pouvant être solidarisé de façon débrayable par un premier embrayage (13) avec un troisième arbre (3) solidaire du planétaire du premier train planétaire (P1), lequel peut être solidarisé du carter (G) de la boîte de vitesses par un premier frein (03), l'arbre primaire (1) pouvant être solidarisé de façon débrayable par un deuxième embrayage (17) avec un septième arbre (7) solidaire de la couronne du premier train planétaire (P1) et un sixième arbre (6) étant solidaire du porte-satellite du premier train planétaire (P1) et étant fonctionnellement solidaire par un deuxième train de pignons (S2) du dixième arbre (10), solidaire de la couronne du troisième train planétaire (P3), l'arbre de sortie (2) étant solidaire du porte-satellites du deuxième train planétaire (P2) et un quatrième arbre (4) étant solidaire du planétaire du deuxième train planétaire (P2) et du planétaire du troisième train planétaire (P3) et pouvant être solidarisé avec le carter (G) par un deuxième frein (04), l'arbre primaire (1) pouvant être fonctionnellement solidarisé par l'intermédiaire d'un huitième et d'un neuvième arbre (8, 9), d'un troisième ou d'un cinquième embrayage (18, 89) et par l'intermédiaire d'un premier train de pignons (S1) avec la couronne du deuxième train planétaire (P2) et avec le porte-satellites du troisième train planétaire (P3), et le troisième arbre (3) pouvant être fonctionnellement solidarisé par un quatrième ou un sixième embrayage (35, 15), un cinquième et un dixième arbre (5, 10) et un troisième train de pignons (S3) avec la couronne du troisième train planétaire (P3).
EP13776775.2A 2012-11-19 2013-10-10 Boîte de vitesses à rapports multiples Withdrawn EP2920487A1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102012221073.3A DE102012221073A1 (de) 2012-11-19 2012-11-19 Mehrstufengetriebe
PCT/EP2013/071157 WO2014075851A1 (fr) 2012-11-19 2013-10-10 Boîte de vitesses à rapports multiples

Publications (1)

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CN104813068B (zh) 2017-12-12
US9518635B2 (en) 2016-12-13
WO2014075851A1 (fr) 2014-05-22
DE102012221073A1 (de) 2014-05-22
US20160017959A1 (en) 2016-01-21
CN104813068A (zh) 2015-07-29

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