EP2923111A1 - Boîte de vitesses à trains planétaires à 10 rapports - Google Patents

Boîte de vitesses à trains planétaires à 10 rapports

Info

Publication number
EP2923111A1
EP2923111A1 EP13780147.8A EP13780147A EP2923111A1 EP 2923111 A1 EP2923111 A1 EP 2923111A1 EP 13780147 A EP13780147 A EP 13780147A EP 2923111 A1 EP2923111 A1 EP 2923111A1
Authority
EP
European Patent Office
Prior art keywords
clutch
gear
planetary gear
gear set
planetary
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Withdrawn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
EP13780147.8A
Other languages
German (de)
English (en)
Inventor
Stefan Beck
Christian Sibla
Wolfgang Rieger
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 EP2923111A1 publication Critical patent/EP2923111A1/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Withdrawn legal-status Critical Current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
    • F16H2200/00—Transmissions for multiple ratios
    • F16H2200/0008—Transmissions for multiple ratios specially adapted for front-wheel-driven vehicles
    • 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
    • F16H2200/0069—Transmissions for multiple ratios characterised by the number of forward speeds the gear ratios comprising ten 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 transmission, in particular for use in motor vehicles.
  • the switching elements are, for example, clutches or brakes here.
  • DE 10 2008 032 01 5 discloses a power shift transmission with ten forward gears and one reverse gear.
  • the powershift transmission on three planetary gear sets, which are interconnected by six torque transmitting devices, two fixed connections and four clutches in different combinations.
  • a torque is introduced via a drive element in the power shift transmission and transmitted taking into account the respective transmission ratio to an output element.
  • the drive element and the output element are arranged coaxially with each other.
  • the present invention has for its object to provide a transmission of the type mentioned, which has low gear jumps at a high gear spread, is simultaneously optimized with respect to the required space and has a high efficiency.
  • a gear spread is to be understood as the quotient of the gear ratio of the lowest gear and the gear ratio of the highest gear, the lowest gear preferably having the largest gear ratio and the highest gear having the lowest gear ratio.
  • a transmission ratio of i ⁇ 1, 0 is a translation into speed, ie that at the transmission output is applied a higher speed than at the transmission input.
  • the transmission comprises at least a drive shaft, an output shaft, a housing and six switching elements.
  • a torque or a rotational movement of a drive source for example an internal combustion engine, is preferably introduced into the transmission via the drive shaft.
  • a starting element such as a hydrodynamic torque converter or a fluid coupling.
  • a shaft is not to be understood below as meaning, for example, a cylindrical, rotatably mounted machine element for the transmission of torques, but rather are also generally understood to mean connecting elements which connect individual components or elements to one another.
  • the six shifting elements particularly preferably comprise a first brake, a second brake, a first clutch, a second clutch, a third clutch and a fourth clutch.
  • Clutches describe switching elements which, depending on the actuation state, permit a relative movement between two components or constitute a fixed connection for transmitting a torque. Under a relative movement, for example, to understand a rotation of two components, wherein the rotational speed of the first component and the rotational speed of the second component differ from each other. In addition, the rotation of only one of the two components is conceivable while the other component is stationary or rotating in the opposite direction.
  • a non-actuated clutch is understood to mean an opened clutch. This means that a relative movement between the two components is possible. When the clutch is actuated or closed, the two components accordingly rotate at the same speed in the same direction.
  • a brake is to be understood as a switching element which is connected on one side to a stationary element, for example a housing, and on another side to a rotatable element.
  • a non-actuated brake is understood to mean an opened brake. This means that the rotatable component is in free-running, ie that the brake preferably has no influence on the rotational speed of the rotatable component. When the brake is actuated or closed, the rotational speed of the rotatable component is reduced to a standstill, ie a firm connection can be established between the rotatable element and the stationary element.
  • the transmission comprises a first planetary gear set, a second planetary gear set and a third planetary gear set.
  • a planetary gear set comprises a sun gear, a planet carrier and a ring gear.
  • Rotatably mounted on the planet carrier are the planet gears, which mesh with the toothing of the sun gear and / or with the toothing of the ring gear.
  • a minus planetary gear a single planetary gear set with a planet carrier to which the planet gears are rotatably storable, with a sun gear and a ring gear, wherein the teeth of at least one of the planet gears both with the teeth of the sun gear, as well as with the teeth of Ring gear meshes, whereby the ring gear and the sun gear rotate in opposite directions of rotation when the sun gear rotates at a fixed planet carrier.
  • planetary gear sets particularly compact gear can be realized, whereby a large freedom in the arrangement of the transmission is achieved.
  • the elements of a planetary gear set are understood in particular to mean the sun gear, the ring gear, the planet carrier and the planet wheels of the planetary gear set.
  • the switching elements are selectively, ie individually, actuated, whereby ten forward gears and one reverse gear can be realized by different gear ratios between the drive shaft and the output shaft. Due to the numerous gears, it is possible to realize a fine gear ratio with a large gear spread and thus, for example, the internal combustion engine in an optimal speed range and thus operate economically. At the same time this contributes to an increase in ride comfort, since the internal combustion engine is preferably operable at a low speed level. Thus, for example, noise emissions are reduced, which arise due to the operation of the internal combustion engine.
  • the drive shaft and the output shaft are mutually axially offset. This leads, for example, to a particularly small axial space requirement of the transmission.
  • the transmission is particularly suitable for use in a vehicle with a front-transverse arrangement of the drive train.
  • the drive source such as an internal combustion engine
  • the drive source is installed transversely to the direction of travel in the vehicle and preferably the wheels of the front axle are driven by the drive source or the transmission.
  • the drive shaft via the third clutch with a planet carrier of the first planetary gear set is connectable and the planet carrier of the first planetary gear set by means of the second brake with the housing connectable.
  • a multiplicity of degrees of freedom with respect to the planetary gear sets is achieved, so that a high number of gears can be realized when using comparatively few shifting elements and planetary gearsets.
  • all elements of the first planetary gear set, the second planetary gear set and the third planetary gear set are rotatable. This means that there is no permanent connection between the elements of the planetary gear sets and the housing, but this can be selectively produced by actuation of the switching elements. This also contributes advantageously to the fact that a high number of gears can be realized by means of a small number of planetary gearsets.
  • the efficiency of the transmission can preferably be increased by requiring energy in the switching elements for changing the switching state, but not for maintaining the switching state itself.
  • switching elements which can be actuated according to demand such as electromechanical switching elements or electromagnetic switching elements, are particularly suitable. They are characterized, in particular in comparison to conventionally hydraulically actuated switching elements, by a particularly low and efficient energy requirements, since they are virtually lossless operable.
  • it can advantageously be dispensed with in the above solution, permanently maintain a control pressure for the operation of, for example, conventionally hydraulic switching elements, or to act on the switching element in the switched state permanently with the required hydraulic pressure.
  • Switching element no further components are arranged, or that the switching elements are particularly preferably arranged on the drive shaft or on the output shaft.
  • a transmission input describes the location of a transmission to which torque is introduced from the drive source into the transmission while driving.
  • a transmission output to understand the location of the transmission, where the torque is introduced taking into account the corresponding gear ratios, for example, in a transfer case or transmitted to drive shafts of the vehicle.
  • the first planetary gear set, the second planetary gear set and the third planetary gear set are designed as a minus planetary gear set. More preferably, all elements of the planetary gear sets are rotatable. This means that there is no permanent connection to a fixed element, such as the housing. A blocking of the individual elements of the planetary gear sets takes place exclusively via actuation of the respective switching elements.
  • the transmission has a first spur gear and a second spur gear.
  • the transmission is particularly preferred for use in vehicles with a front-transverse arrangement of the drive train, since a small axial space is claimed by the axially offset arrangement of the drive shaft and the output shaft.
  • a spur gear is a single or multi-stage spur gear with at least two spur gears, which are engaged with each other.
  • the respective shafts of the spur gears are arranged parallel to each other.
  • the two front drives are arranged starting from the transmission input coaxial with the drive shaft in the order of the first spur drive, the second spur drive between the first planetary gear set and the second planetary gear set.
  • This arrangement ensures a particularly space-saving design. This is due to the fact that the individual planetary gear sets and switching elements can be nested well into one another, since z. B. do not cross the different waves in this arrangement.
  • the drive shaft by means of the first clutch with the first brake and the sun gear of the first planetary gear set is connectable and the sun gear of the first planetary gear set by means of the first brake with the housing connectable.
  • the drive shaft via the second clutch with the sun gear of the third planetary gear set and via the third clutch with the ring gear of the third planetary gear set is connectable.
  • the ring gear of the first planetary gear set is connected to a first spur gear and the sun gear of the second planetary gear set.
  • the first spur gear via the fourth clutch to the output shaft is connectable.
  • the planet carrier of the second planetary gear set is connected to a second spur gear and this to the output shaft.
  • the ring gear of the second planetary gear set is connected to the planet carrier of the third planetary gear set.
  • the drive shaft is connected to the sun gear of the third planetary gear set and further connectable via the second clutch with the ring gear of the third planetary gear set.
  • the ring gear of the first planetary gear set is connected to a first spur gear and the sun gear of the second planetary gear set and the first spur gear via the fourth clutch to the output shaft connectable.
  • a second spur drive is preferred on the one hand connected to the planet carrier of the second planetary gear set and on the other hand to the output shaft. More preferably, the ring gear of the second planetary gear set is connected to the planet carrier of the third planetary gear set.
  • the drive shaft is connected to the sun gear of the third planetary gear set.
  • the drive shaft is more preferably connected via the third clutch with the ring gear of the third planetary gear set.
  • the ring gear of the first planetary gear set is connected to a first spur gear and the sun gear of the second planetary gear set and the first spur gear via the fourth clutch to the output shaft connectable.
  • a planet carrier of the second planetary gear set is preferably connected to a second spur gear and this second spur gear to the output shaft, while the ring gear of the second planetary gear set via the second clutch to the planet carrier of the third planetary gear set is connectable.
  • the drive shaft is connected to the sun gear of the third planetary gear set.
  • this drive shaft can be connected via the third clutch to the ring gear of the third planetary gear set.
  • the ring gear of the first planetary gear set has a connection to a first spur gear, and the first spur gear can be connected to the output shaft via the fourth clutch.
  • the ring gear of the first planetary gear set via the second clutch to the sun gear of the second planetary gear set is connectable.
  • the planet carrier of the second planetary gear set is connected to a second spur gear and this second spur gear to the output shaft, while the ring gear of the second planetary gear set is connected to the planet carrier of the third planetary gear set.
  • the drive shaft is connected, on the one hand, to the sun gear of the third planetary gear set and, on the other hand, via the third clutch to the ring gear of the third planetary gear set. bindable.
  • the ring gear of the first planetary gear set is connected to a first spur gear and the sun gear of the second planetary gear set and the first spur gear via the fourth clutch to the output shaft connectable.
  • the planet carrier of the second planetary gear set is connectable via the second clutch with a second spur gear and the second spur gear further connected to the output shaft.
  • the ring gear of the second planetary carrier is connected to the planet carrier of the third planetary gear set.
  • the drive shaft is on the one hand connected to the sun gear of the third planetary gear set and on the other hand connectable via the third clutch with the ring gear of the third planetary gear set.
  • the ring gear of the first planetary gear set is connected to a first spur gear and the sun gear of the second planetary gear set and at the same time the first spur gear via the fourth clutch to the output shaft is connectable.
  • a second spur drive is on the one hand connected to the planet carrier of the second planetary gear set and on the other hand connected via the second clutch to the output shaft. Further, the ring gear of the second planetary gear set is connected to the planet carrier of the third planetary gear set.
  • the drive shaft via the second clutch with the sun gear of the third planetary gear set and at the same time via the third clutch with the ring gear of the third planetary gear set connectable.
  • the ring gear of the first planetary gear set is further connected to the sun gear of the second planetary gear set and connectable via the fourth clutch with a first spur gear, while the first spur gear is connected to the output shaft.
  • the planet carrier of the second planetary gear set with a second spur gear and this second spur gear is further connected to the output shaft.
  • the ring gear of the second planetary gear set is connected to the planet carrier of the third planetary gear set.
  • the first forward gear through the closed second brake, the closed first clutch and the closed second clutch is switchable.
  • the closed first brake, the closed second brake and the closed second clutch is the second forward gear switchable.
  • the third forward gear is preferably switchable by the closed second brake, the closed second clutch and the closed fourth clutch. Due to the closed first brake, the closed second clutch and the closed fourth clutch, the fourth forward gear is switchable.
  • the fifth forward gear is preferably switchable by the closed first clutch, the closed second clutch and the closed fourth clutch. Due to the closed second clutch, the closed third clutch and the closed fourth clutch, the sixth forward gear is switchable.
  • the seventh forward gear is preferably switchable by the closed first clutch, the closed second clutch and the closed third clutch.
  • the eighth forward gear is switchable by the closed first brake, the closed second clutch and the closed third clutch. Due to the closed first clutch, the closed third clutch and the closed fourth clutch, the ninth forward gear is preferably switchable.
  • the tenth forward gear is switchable by the closed first brake, the closed third clutch and the closed fourth clutch.
  • the closed second brake, the closed first clutch and the closed fourth clutch, the reverse gear is switchable. So can be changed from one to the next gear by only the switching state of two switching elements is changed. This particularly preferably contributes to a reduction of the switching times.
  • the change of the switching state takes place in such a way that at least one previously opened switching element is closed and at least one previously closed switching element is opened.
  • a method of operating a transmission is proposed.
  • three switching elements are closed simultaneously in each gear stage. Regardless of whether hydraulically, electromechanically or otherwise operable, this leads to a low energy consumption of the switching elements, which ultimately has an advantageous effect on the consumption of, for example, fuel in an internal combustion engine as a drive source of the vehicle.
  • FIG. 1 shows a schematic view of a first preferred embodiment of a transmission according to the invention
  • FIG. 2 shows a schematic view of a second preferred embodiment of a transmission according to the invention
  • Fig. 3 is a schematic view of a third preferred embodiment of a transmission according to the invention.
  • FIG. 4 shows a schematic view of a fourth preferred embodiment of a transmission according to the invention.
  • FIG. 5 shows a schematic view of a fifth preferred embodiment of a transmission according to the invention.
  • FIG. 6 shows a schematic view of a sixth preferred embodiment of a transmission according to the invention.
  • Fig. 7 is a schematic view of a seventh preferred embodiment of a transmission according to the invention.
  • Fig. 1 shows a schematic representation of a first preferred embodiment of the transmission, wherein the transmission comprises a first planetary PR1, a second planetary PR2, a third planetary PR3, a first spur ST1, a second spur ST2 and six switching elements, said All elements are arranged in a housing GE.
  • the six switching elements are a first brake B1, a second brake B2, a first clutch K1, a second clutch K2, a third clutch K3 and a fourth clutch K4.
  • the first brake B1 and the second brake B2 are in each case firmly connected on one side to the housing GE. Via a drive shaft 1, a rotational movement or a torque is introduced into the transmission.
  • the introduction of the torque or the rotational movement takes place at one end of the drive shaft 1, which projects out of the housing GE out.
  • This end of the drive shaft 1 is the second clutch K2 and the third Kupp ment K3 arranged axially opposite one another.
  • the elements of the transmission are between the transmission input and the third clutch K3 axially along the drive shaft 1 in the order first clutch K1, first brake B1, second brake B2, first planetary PR1, first spur ST1, second spur ST2, second planetary PR2, third Planetary gear set PR3, second clutch K2 arranged.
  • the fourth clutch K4 Between the first spur gear ST1 and one end of the output shaft 2, which protrudes from the housing GE out, there is the fourth clutch K4.
  • the drive shaft 1 can be connected via the first clutch K1 to a third shaft 3, the third shaft 3 simultaneously connecting the sun gear S1 of the first planetary gearset PR1 to the first brake B1 and thus to the sun gear S1 of the first planetary gearset PR1 via the first brake B1 the housing GE is braked. Furthermore, the drive shaft 1 can be connected via the second clutch K2 with a fourth shaft 4, wherein the fourth shaft 4 is in turn connected to the sun gear S3 of the third planetary PR3. Via the third clutch K3, the drive shaft 1 is also connectable to a fifth shaft 5, wherein the fifth shaft 5 is connected to the planet carrier PT1 of the first planetary PR1 and also has a connection to the ring gear H3 of the third planetary PR3.
  • the fifth shaft 5 connects the planet carrier PT1 of the first planetary gear set PR1 to the second brake B2, ie the fifth shaft 5 or the planet carrier PT1 of the first planetary gear set PR1 can be braked on the housing GE by means of the second brake B2.
  • a sixth shaft 6 connects the ring gear H2 of the second planetary gear PR2 with the planet carrier PT3 of the third planetary PR3.
  • a seventh shaft 7 connects the planet carrier PT2 of the second planetary PR2 with the second spur gear ST2, whereby a transmission of the rotational movement or the torque is made possible on the output shaft 2.
  • An eighth shaft 8 connects the ring gear H1 of the first planetary gear set PR1 on the one hand with the first spur gear ST1 and on the other hand with the sun gear S2 of the second Planetenradsat- zes PR2.
  • a ninth shaft 9 can be connected to the output shaft 2, the ninth shaft 9 in turn being connected to the first spur gear ST1.
  • the first planetary gearset PR1 is designed as a minus planetary gear set. This means that planetary gears of the planet carrier PT1 mesh with the sun gear S1 and the ring gear H1 of the first planetary gear set PR1. The same applies to the second planetary PR2 and the sun S2, the planet carrier PT2 and the ring gear H2 of the second planetary PR2, and for the third planetary PR3 and the sun S3, the planet carrier PT3 and the ring gear H3 of the third planetary PR3.
  • Fig. 2 shows a further embodiment of the transmission described in Fig. 1, which differs on the basis of two features of the embodiment described in Fig. 1.
  • the drive shaft 1 is directly connected to the sun gear S3 of the third planetary PR3 and not as in Fig. 1 via the second clutch K2 and the fourth shaft 4 with the sun gear S3 of the third planetary PR3.
  • FIG. 3 shows a further variant of the transmission described in FIG. 1.
  • the drive shaft 1 can be connected to the third shaft 3 via the first clutch K1, wherein the sun gear S1 of the first planetary gearset PR1 can be connected to the first brake B1 via the third shaft 3 or braked on the housing GE.
  • the drive shaft 1 is connected to the sun gear S3 of the third planetary PR3.
  • the drive shaft 1 via the third clutch K3 with the fifth shaft 5 is connectable, wherein the fifth shaft 5 is connected on the one hand with the ring gear H3 of the third planetary PR3 and on the other hand with the planet carrier PT1 of the first planetary PR1.
  • the planet carrier PT1 of the first planetary gear PR1 on the fifth shaft.
  • the ring gear H1 of the first planetary PR1 is, as described in Fig. 1, connected by means of the eighth shaft 8 on the one hand with the sun gear S2 of the second planetary PR2 and on the other hand with the first spur gear ST1.
  • the eighth shaft 8 thus also connects the sun gear S2 of the second planetary gear PR2 with the first spur gear ST1.
  • the first spur gear ST1 is connected to the ninth shaft 9, which in turn can be connected to the output shaft 2 via the fourth clutch K4.
  • the planet carrier PT2 of the second planetary PR2 is connected via the seventh shaft 7 with the second spur gear ST2.
  • the second spur gear ST2 is connected to the output shaft 2 and thus enables a transmission of the torque or rotational movement to the output shaft 2.
  • the sixth shaft 6 is connected on the one hand with the ring gear H2 of the second planetary PR2 and on the other hand via the second clutch K2 can be connected to the fourth shaft 4.
  • the fourth shaft 4 is in turn also connected to the planet carrier PT3 of the third planetary PR3.
  • a fourth variant of the transmission described in Fig. 1 is shown schematically.
  • the transmission corresponds largely to the embodiment described in Fig. 3, only the arrangement of the second clutch K2 '' and the fourth shaft 4 differ from the embodiment described in Fig. 3.
  • the ring gear H1 of the first planetary gear set PR1 is about the eighth Moreover, the eighth shaft 8 can be connected to the fourth shaft 4 via the second clutch K2 '", the fourth shaft 4 also being connected to the sun gear S2 of the second planetary gearset PR2.
  • Another difference compared to the embodiment shown in Fig. 3 is the connection of the ring gear H2 of the second planetary PR2 on the sixth shaft 6 with the planet carrier PT3 of the third planetary PR3.
  • FIG. 5 shows a fifth variant of the transmission described in FIG. 1.
  • the transmission corresponds largely to the embodiment described in Fig. 3.
  • the differences between the two embodiments are expressed in the positioning of the second clutch K2 "" and the fourth shaft 4.
  • the connection between the two see the planet carrier PT2 of the second planetary PR2 and the second spur gear ST2 does not take place, as described in Fig. 3, via the seventh shaft 7, but the planet carrier PT2 of the second planetary PR2 is connected to the seventh shaft 7, which via the second Clutch K2 "" with the fourth shaft 4 is connectable, and the fourth shaft 4 is in turn connected to the second spur gear ST2 and the second spur gear (ST2) transmits the torque or rotational movement to the output shaft 2.
  • the ring gear H2 of the second planetary gear set PR2 is connected via the sixth shaft 6 to the planet carrier PT3 of the third planetary PR3.
  • FIG. 1 A sixth variant of the transmission described in FIG. 1 is shown in FIG. This arrangement is similar to the embodiment described in FIG. 5. The only difference results from the positioning of the second clutch K2 and the fourth shaft 4. This manifests itself in that the second spur gear ST2 is connected to the fourth shaft 4 and the fourth shaft 4 can be connected to the output shaft 2 via the second clutch K2 is.
  • the planet carrier PT2 of the second planetary PR2 is connected via the seventh shaft 7 with the second spur gear ST2.
  • the remaining arrangement of the elements of the embodiment is similar to the arrangement described in FIG.
  • FIG. 7 shows a seventh variant of the transmission described in FIG. 1.
  • the drive shaft 1 can be connected to the third shaft 3 via the first clutch K1, wherein the third shaft 3 or the sun gear S1 of the first planetary gear set PR1 can be braked by means of the first brake B1 on the housing GE.
  • the drive shaft 1 via the second clutch K2 with the fourth shaft 4 is connectable, wherein the fourth shaft 4 is connected to the sun gear S3 of the third planetary PR3.
  • the drive shaft 1 via the third clutch K3 with the fifth shaft 5 is connectable.
  • the fifth shaft 5 moreover connects the ring gear H3 of the third planetary gear set PR3 to the planet carrier PT1 of the first planetary gear set PR1.
  • the planet carrier PT1 of the first planetary gearset PR1 is further connectable via the fifth shaft 5 to the second brake B2 or braked on the housing GE.
  • the ring gear H1 of the first planetary gearset PR1 is connected to the eighth shaft 8.
  • the eighth 8 shaft connected to the sun gear S2 of the second planetary PR2 and connectable via the fourth clutch K4 'with the ninth shaft 9.
  • the ninth shaft 9 is also connected to the first spur gear ST1, wherein the first spur gear ST1 transmits the rotational movement or the torque to the output shaft 2.
  • the planet carrier PT2 of the second planetary PR2 is connected via the seventh shaft 7 with the second spur gear ST2, which transmits the rotational movement and the torque to the output shaft 2.
  • the ring gear H2 of the second planetary PR2 is connected via the sixth shaft 6 with the planet carrier PT3 of the third Pianetenradsatzes PR3.
  • Fig. 8 shows in a table a switching matrix of the transmission.
  • An X in the respective field indicates which of the switching elements is closed for the realization of the first to tenth forward gear and the reverse gear.

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

Abstract

Boîte de vitesses, notamment pour véhicule automobile, la boîte de vitesses comprenant au moins un arbre d'entrée (1), un arbre de sortie (2), un carter (GE), six organes de changement de vitesses, comportant un premier frein (B1) et un deuxième frein (B2), ainsi qu'un premier embrayage (K1), un deuxième embrayage (K2, Κ2', K2", K2"', K2"", K2'''''), un troisième embrayage (K3) et un quatrième embrayage (K4, K4'), un premier train planétaire (PR1), un deuxième train planétaire (PR2) et un troisième train planétaire (PR3), chaque train planétaire présentant au moins un pignon solaire, un satellite, un porte-satellites et une couronne, et les organes de changement de vitesses étant actionnables sélectivement, ce qui permet d'obtenir dix vitesses de marche avant et une vitesse de marche arrière par différents rapports de démultiplication entre l'arbre d'entrée (1) et l'arbre de sortie (2), caractérisée en ce que l'arbre d'entrée (1) et l'arbre de sortie (2) sont disposés en présentant un décalage axial, en ce que l'arbre d'entrée (1) puisse être relié au porte-satellites (PT1) du premier train planétaire (PR1) par l'intermédiaire du troisième embrayage (K3) et en ce que le porte-satellites (PT1) du premier train planétaire (PR1) puisse être relié au carter (GE) par l'intermédiaire du deuxième frein (B2).
EP13780147.8A 2012-11-21 2013-10-24 Boîte de vitesses à trains planétaires à 10 rapports Withdrawn EP2923111A1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102012221241.8A DE102012221241A1 (de) 2012-11-21 2012-11-21 Getriebe
PCT/EP2013/072222 WO2014079639A1 (fr) 2012-11-21 2013-10-24 Boîte de vitesses à trains planétaires à 10 rapports

Publications (1)

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EP (1) EP2923111A1 (fr)
CN (1) CN104797854B (fr)
DE (1) DE102012221241A1 (fr)
WO (1) WO2014079639A1 (fr)

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DE102016211884A1 (de) * 2016-06-30 2018-01-04 Zf Friedrichshafen Ag Getriebe für ein Kraftfahrzeug, sowie Antriebsstrang für ein Kraftfahrzeug
DE102018000187B4 (de) * 2018-02-08 2022-10-06 Mercedes-Benz Group AG Getriebeeinrichtung, insbesondere für ein Kraftfahrzeug
DE102018217859A1 (de) * 2018-10-18 2020-04-23 Zf Friedrichshafen Ag Getriebe für ein Kraftfahrzeug

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Also Published As

Publication number Publication date
US20150300459A1 (en) 2015-10-22
US9574640B2 (en) 2017-02-21
DE102012221241A1 (de) 2014-05-22
WO2014079639A1 (fr) 2014-05-30
CN104797854A (zh) 2015-07-22
CN104797854B (zh) 2018-01-02

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