EP2923113A1 - Boîte de vitesses à trains planétaires à 9 rapports - Google Patents

Boîte de vitesses à trains planétaires à 9 rapports

Info

Publication number
EP2923113A1
EP2923113A1 EP13780149.4A EP13780149A EP2923113A1 EP 2923113 A1 EP2923113 A1 EP 2923113A1 EP 13780149 A EP13780149 A EP 13780149A EP 2923113 A1 EP2923113 A1 EP 2923113A1
Authority
EP
European Patent Office
Prior art keywords
clutch
gear
planetary gear
gear set
closed
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Withdrawn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
EP13780149.4A
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 EP2923113A1 publication Critical patent/EP2923113A1/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Withdrawn legal-status Critical Current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
    • F16H2003/442—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion using gears having orbital motion comprising two or more sets of orbital gears arranged in a single plane
    • 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
    • F16H2200/0065—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 transmission, in particular for use in motor vehicles.
  • the switching elements are, for example, clutches or brakes here.
  • DE 10 2008 032 015 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 / or has a high efficiency.
  • a gear spread is understood as meaning the quotient of the gear ratio of the lowest gear and the gear ratio of the highest gear, the lowest gear having the highest gear ratio and the highest gear having the lowest gear ratio.
  • a transmission ratio of i ⁇ 1, 0 is a translation into speed, that is, at the transmission output a higher speed is applied than at the transmission input.
  • the transmission comprises at least one drive shaft, an output shaft, a housing, a first planetary gear set, a second planetary gear set and a third planetary gear set and six shifting elements.
  • a torque or a rotational movement of a drive source 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 exclusively as an example cylindrical, rotatably mounted machine element for transmitting torque, but these are also general fasteners to understand that connect individual components or elements together, in particular connecting elements that connect a plurality of elements rotatably together.
  • Two elements are in particular referred to as connected to each other if there is a fixed, in particular rotationally fixed connection between the elements. In particular, such connected elements rotate at the same speed.
  • Two elements will be referred to as connectable if there is a detachable connection between these elements.
  • such elements rotate at the same speed when the connection is made.
  • the various components and elements of said invention can be connected to one another via a shaft or a connecting element, but also directly, for example by means of a welding, pressing or other connection.
  • 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.
  • Couplings describe switching elements which, depending on the operating state, allow a relative movement between two components or constitute a 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 rotatable 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.
  • the clutch is actuated or closed, the two components accordingly rotate at the same speed and 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.
  • the rotatable component is in free-running, that is to say that the brake preferably has no influence on the rotational speed of the rotatable component.
  • the brake is actuated or closed, the rotational speed of the rotatable component is reduced to a standstill, that is, a connection can be established between the rotatable element and the stationary element. Element and component are to be equated in this context.
  • a planetary gear set includes a sun gear, a planet carrier, and a ring gear.
  • Rotatably mounted on the planet carrier are planetary gears, which mesh with the toothing of the sun gear and / or with the toothing of the ring gear.
  • a minus planetary gearset describes a planetary gear set with a planet carrier on which planetary gears are rotatably mounted, with a sun gear and with a ring gear, wherein the toothing of at least one of the planet gears meshes both with the toothing of the sun gear and with the toothing of the ring gear, whereby the ring gear and the sun gear rotate in opposite directions of rotation when the sun gear rotates when the planet carrier is stationary.
  • a plus planetary gear set differs from the negative planetary gear set just described in that the plus planetary gear set has inner and outer planetary gears rotatably supported on the planetary carrier.
  • the toothing of the inner planet gears meshes on the one hand with the teeth of the sun gear and on the other hand with the teeth of the outer planetary gears.
  • the toothing of the outer planetary gears also meshes with the teeth of the ring gear.
  • 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 selective, ie individually and as needed operable, whereby nine 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.
  • all elements of the first planetary gear set, the second planetary gear set and the third planetary gear set are rotatable.
  • a blocking of the individual elements of the planetary gear sets is exclusively produced by actuation of the respective switching elements.
  • the drive shaft via the first clutch with the ring gear of the third planetary gear set and with the second brake is connectable.
  • the ring gear of the third planetary gear set and the second brake are also connected to each other.
  • a plurality of degrees of freedom with respect to the planetary gear sets is achieved, so that a plurality of gears when using comparatively few switching elements and planetary gear sets is feasible.
  • a third shaft is arranged coaxially with the drive shaft.
  • 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.
  • the sun gear of the third planetary gear set is connected to the first brake.
  • the transmission has a first spur gear and a second spur gear. At least each of a spur gear of the first spur gear and a spur gear of the second spur gear is arranged coaxially with the drive shaft.
  • a torque between the drive shaft and the output shaft can be transmitted.
  • front drives enables the transmission of torques or rotational movements between the axially offset drive shaft and the output shaft, resulting in a particularly small axial space requirement of the transmission in the vehicle.
  • the drive source for example an internal combustion engine
  • the wheels of the rear axle can be driven by the drive source or the transmission.
  • a spur gear is a single or multi-stage spur gear with at least two spur gears, which are engaged with each other. there the respective shafts or axes of rotation of the spur gears are arranged parallel to each other.
  • the two end drives are positioned in axial alignment along the third shaft, particularly preferably between the first planetary gear set and the third planetary gear set. They are arranged in the order of first planetary gear set, first spur gear, second spur gear, third planetary gear set.
  • This arrangement ensures a particularly space-saving design, since the individual planetary gear sets and switching elements can be nested well into one another and the different waves do not intersect, for example, in this arrangement.
  • geometric position of the individual wheelsets, shift elements and front drives is conceivable, as far as the change of the geometric position of the components along the third wave.
  • the first planetary gear set and the second planetary gear set are axially positioned with respect to the third shaft such that the second planetary gear set is disposed radially above the first planetary gear set.
  • the arrangement of the second planetary gear set radially above the first planetary gear set is characterized in a special way by a particularly small axial space requirement.
  • the sun gear of the second planetary gear set and the ring gear of the first planetary gear set are interconnected.
  • a one-piece or one-piece design is also available. tion of the sun gear of the second planetary gear and the ring gear of the first planetary gear conceivable.
  • the ring gear of the first planetary gear has next to an internal toothing, which meshes with the teeth of the planetary gears of the first planetary gear, also via an external toothing, which preferably takes over the function of the toothing of the sun gear of the second planetary gear set.
  • the external teeth of the ring gear of the first planetary gear set meshes with the teeth of the planet gears of the second planetary gear set.
  • the first planetary gear set, the second planetary gear set and the third planetary gear set are each designed as a minus planetary gear set.
  • This arrangement proves on the one hand in a special way as a cost-effective implementation of the wheelset. On the other hand, this arrangement has a high efficiency with respect to the wheelset, since minus planetary gear sets over positive planetary gear sets have improved efficiency.
  • At least one minus planetary gear set can be converted into a plus planetary gear set. At the same time, however, this requires that the planet carrier and the ring gear connection are exchanged and the amount of stand ratio is increased by the value 1.
  • the state ratio indicates the ratio between the sun and ring gear when the planet carrier is fixed.
  • the drive shaft via the first clutch to the planet carrier of the first planetary gear set is connectable. More preferably, the drive shaft via the second clutch to the sun gear of the first planetary gear set is connectable.
  • the drive shaft is further preferably connected via the third clutch with the planet carrier of the second planetary gear set.
  • the ring gear of the second planetary gear set is preferably connected to a first spur gear and the first spur gear is further connected to the Ab lake- connected to the drive shaft.
  • the planet carrier of the third planetary gear set is connected to a second spur gear, the ring gear of the first planetary gear set and the sun gear of the second planetary gear set.
  • the second spur drive is preferably further connectable via the fourth clutch to the output shaft.
  • the first clutch, the second clutch, and the third clutch are positioned side by side and in coaxial relation with the drive shaft and connected to the drive shaft at one side, respectively.
  • the first clutch, the second clutch and the third clutch are positioned between the transmission input and the first planetary gear set along the third shaft in the order of first clutch, second clutch, third clutch.
  • a transmission input describes a location of a transmission on which torque is introduced from the drive source into the transmission during driving operation.
  • a transmission output is to be understood as a location of the transmission on which the torque, taking into account the corresponding transmission ratios, is introduced, for example, into a transfer case or transmitted to the drive shafts of the vehicle.
  • the drive shaft via the first clutch and the second clutch with the planet carrier of the first planetary gear set is connectable. More preferably, the drive shaft is connected to the sun gear of the first planetary gear set.
  • the drive shaft is also preferably connected via the third clutch to the planet carrier of the second planetary gear set. More preferably, the ring gear of the second planetary gear set is connected to a first spur gear and the first spur gear further connected to the output shaft.
  • the planet carrier of the third planetary gear set is particularly preferably connected to a second spur gear, the ring gear of the first planetary gear set and the sun gear of the second planetary gear set. More preferably, the second spur gear is also connectable via the fourth clutch to the output shaft.
  • the drive shaft via the first clutch to the planet carrier of the first Pianetenradsatzes connectable. More preferably, the drive shaft via the second clutch to the sun gear of the first Pianetenradsatzes connectable.
  • the drive shaft is preferably connected to the planet carrier of the second Pianetenradsatzes.
  • the ring gear of the second Pianetenradsatzes via the third clutch with a first spur drive is connectable.
  • the first spur gear is further preferably connected to the output shaft.
  • the planet carrier of the third Pianetenradsatzes is preferably connected to a second spur gear, the ring gear of the first Pianetenradsatzes and the sun gear of the second Pianetenradsatzes. More preferably, the second spur gear is also connectable via the fourth clutch to the output shaft.
  • the drive shaft via the first clutch to the planet carrier of the first Pianetenradsatzes is connectable. More preferably, the drive shaft via the second clutch to the sun gear of the first Pianetenradsatzes connectable.
  • the drive shaft is preferably connected to the planet carrier of the second Pianetenradsatzes. More preferably, the ring gear of the second Pianetenradsatzes is connected to a first spur gear, wherein the first spur gearing is further preferably connected via the third clutch to the output shaft.
  • the planet carrier of the third Pianetenradsatzes is preferably connected to a second spur gear, the ring gear of the first Pianetenradsatzes and the sun gear of the second Pianetenradsatzes. More preferably, the second spur gear via the fourth clutch to the output shaft is connectable.
  • the drive shaft via the first clutch and the second clutch with the planet carrier of the first Pianetenradsatzes is connectable. More preferably, the drive shaft is connected to the sun gear of the first Pianetenradsatzes.
  • the drive shaft is further preferably connected to the planet carrier of the second Pianetenradsatzes.
  • the ring gear of the second Pianetenradsatzes is connectable via the third clutch with a first spur gear, wherein the first spur gear is further preferably connected to the output shaft.
  • the second spur gear is further preferably connected via the fourth clutch to the output shaft.
  • the drive shaft via the first clutch and the second clutch with the planet carrier of the first planetary gear set is connectable. More preferably, the drive shaft is connected to the sun gear of the first planetary gear set. The drive shaft is further preferably connected to the planet carrier of the second planetary gear set. Preferably, the ring gear of the second planetary gear set is connected to a first spur gear, wherein the first spur gear is further preferably connected via the third clutch to the output shaft. More preferably, the planet carrier of the third planetary gear set is connected to a second spur gear, the ring gear of the first planetary gear set and the sun gear of the second planetary gear set. More preferably, the second spur gear via the fourth clutch to the output shaft is connectable.
  • the drive shaft via the first clutch to the planet carrier of the first planetary gear set is connectable. More preferably, the drive shaft via the second clutch to the sun gear of the first planetary gear set is connectable.
  • the drive shaft is preferably connectable via the third clutch with the planet carrier of the second planetary gear set. More preferably, the ring gear of the second planetary gear set is connected to a first spur gear. More preferably, the first spur gear is connected to the output shaft.
  • the planet carrier of the third planetary gear set is preferably connected to the ring gear of the first planetary gear set and the sun gear of the second planetary gear set and preferably connectable via the fourth clutch with a second spur gear.
  • the second spur gear is further connected to the output shaft.
  • the first forward gear can be represented by the closed first brake, the closed second clutch and the closed fourth clutch.
  • the closed first clutch and the closed fourth clutch is preferably the second forward speed representable.
  • the third forward gear is preferably represented by the closed first clutch, the closed second clutch and the closed fourth clutch.
  • the fifth forward gear is preferably represented by the closed first clutch, the closed second clutch and the closed third clutch.
  • the sixth forward gear is preferably displayed.
  • the seventh forward gear is preferably represented by the closed first brake, the closed second clutch and the closed third clutch. Due to the closed first brake, the closed second brake and the closed third clutch, preferably the eighth forward gear can be displayed.
  • the ninth forward gear is preferably represented by the closed second brake, the closed second clutch and the closed third clutch. Due to the closed second brake, the closed second clutch and the closed fourth clutch, the reverse gear is particularly preferably represented.
  • a method of operating a transmission is proposed.
  • at least nine forward gears can preferably be selected so that in each gear each three switching elements are closed simultaneously.
  • the remaining switching elements are preferably open.
  • a gear change into an adjacent higher gear or into an adjacent lower gear is preferably realized by closing at least one previously opened and by opening at least one previously closed switching element.
  • the fourth clutch is particularly preferably designed as a form-locking switching element, in particular as a dog clutch. This leads to a significantly improved efficiency of the transmission and thus to significant fuel consumption advantages, for example in vehicles with internal combustion engine.
  • an electric machine or another power / power source can additionally be arranged on each shaft or each connecting element.
  • a freewheel to the housing or to another shaft can in principle be arranged on each shaft or each connecting element. This results in that the corresponding switching element can be made smaller, since at least part of the torque is absorbed by the freewheel.
  • 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
  • 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.
  • the said elements are all arranged in a housing G.
  • 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 B ⁇ b> 1 and the second brake B ⁇ b> 2 are fixedly connected to the housing G with their one side, respectively.
  • Fig. 1 shows a drive shaft 1 and an output shaft 2, wherein the drive shaft 1 and the output shaft 2 are arranged parallel to each other.
  • the drive shaft 1 On a first side of the drive shaft 1, the drive shaft 1 has a free end. On this first side of the drive shaft 1, a rotational movement or a torque is introduced into the transmission.
  • the drive shaft 1 can be connected to a third shaft 3 via the first clutch K1.
  • the third shaft 3 is further connected to the planet carrier PT1 of the first planetary gear set PR1, the ring gear H3 of the third planetary gear set PR3 and the second brake B2.
  • the third shaft 3 connects the planetary carrier PT1 of the first planetary gear set PR1, the ring gear H3 of the third planetary gear set PR3 and the second brake B2 with each other.
  • the third shaft 3 is coaxial with the drive shaft.
  • the first clutch K1, the second clutch K2 and the third clutch K3 are arranged coaxially with the third shaft 3 in the order of first clutch K1, second clutch K2, third clutch K3, wherein the first clutch K1 is spaced closer to the free end of the first clutch Drive shaft 1 has as the second clutch K2 and the third Coupling K3. Also disposed coaxially with the third shaft 3 are the first planetary gear set PR1, the second planetary gear set PR2, the third planetary gear set PR3, the first brake B1, and the second brake B2.
  • the second planetary PR2 is disposed radially above the first planetary PR1.
  • the ring gear H1 of the first planetary gear PR1 is therefore connected to the sun gear S2 of the second planetary PR2.
  • the first planetary gear set PR1, the third planetary gear set PR3, the first brake B1 and the second brake B2 are arranged along the third shaft 3 starting from the third clutch K3 in the order of the first planetary gearset PR1, third planetary gear set PR3, first brake B1, second brake B2 , Between the first planetary gearset PR1 and the second planetary gear PR2 and the third planetary PR3 are in the order first planetary PR1 and second planetary PR2, first spur ST1, second spur ST2, third planetary PR3, the first spur ST1 and the second spur gear ST2. At least one respective spur gear of the first spur gear ST1 and the second spur gear ST2 is arranged coaxially with the third shaft 3.
  • the fourth clutch K4 is arranged beginning at the free end of the drive shaft 2.
  • the first spur gear ST1, the second spur gear ST2 and the fourth clutch K4 are arranged in the order just mentioned along the output shaft 2.
  • At least each of a spur gear of the first spur gear ST1 and a spur gear of the second spur gear ST2 is arranged coaxially with the output shaft 2.
  • the drive shaft 1 is further connectable via the second clutch K2 with a fourth shaft 4, wherein the fourth shaft 4 is further connected to the sun gear S1 of the first planetary PR1.
  • the drive shaft 1 is connected to a fifth shaft 5, wherein the fifth shaft 5 is further connected to the planet carrier PT2 of the second planetary PR2.
  • the ring gear H2 of the second planetary PR2 is connected via a sixth shaft 6 with the first spur gear ST1.
  • the first spur gear ST1 is further connected to the output shaft 2.
  • the sun gear S3 of the third planetary gear set PR3 is connected via a seventh shaft 7 to the first brake B1.
  • the planet carrier PT3 of the third planetary PR3 is connected to an eighth shaft 8, wherein the eighth shaft 8 is further connected to the second spur gear ST2, the ring gear H1 of the first planetary PR1 and the sun gear S2 of the second planetary PR2.
  • the eighth shaft 8 connects the just mentioned elements with each other.
  • the second spur gear ST2 is further connected to a ninth shaft 9, wherein the ninth shaft 9 via the fourth clutch K4 with the output shaft 2 is connectable.
  • the first planetary gearset PR1, the second planetary gearset PR2 and the third planetary gearset PR3 are each 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.
  • the first spur gear ST1 and the second spur gear ST2 are each designed as single-stage spur gear.
  • Fig. 2 shows a further embodiment of the transmission described in Fig. 1, which differs primarily by a different positioning of the second clutch K2 'of the embodiment described in Fig. 1.
  • the second clutch K2 ' is spatially positioned between the first planetary gear set PR1 and the first spur gear ST1 in coaxial arrangement with the third shaft 3 in the present embodiment. This results in the following changes with respect to the interfaces or connections in the transmission.
  • the drive shaft 1 can be connected to the third shaft 3 via the first clutch K1.
  • the third shaft 3 is also connected to the ring gear H3 of the third planetary gear set PR3 and the second brake B2. Deviating from the arrangement described in Fig.
  • the third shaft 3 is also connected via the second clutch K2 'with the fourth shaft 4, wherein the fourth shaft 4 continues with the Planet carrier PT1 of the first planetary gear set PR1 is connected.
  • a further deviation of the connection of the individual elements of the planetary gear sets PR1, PR2, PR3 is moreover that the drive shaft 1 is now directly connected to the sun gear S1 of the first planetary PR1. All other interfaces and component arrangements are consistent with the arrangement described in FIG.
  • FIG. 3 shows a third variant of the transmission described in FIG. 1.
  • An essential difference from the arrangement described in FIG. 1 is the positioning of the third clutch K3 '.
  • the third clutch K3 ' is arranged coaxially with the third shaft 3 between the first planetary gear set PR1 and the second planetary gear set PR2 and the first spur gear ST1.
  • This has the consequence that the drive shaft 1 is now connected directly to the planet carrier PT2 of the second planetary PR2.
  • the ring gear H2 of the second planetary PR2 is connected to the sixth shaft 6, wherein the sixth shaft 6 is now connected via the third clutch K3 'with the fifth shaft 5.
  • the fifth shaft 5 is further connected to the first spur gear ST1 and the first spur gear ST1 further connected to the output shaft 2. All other connections and interfaces as well as the arrangement of the respective components correspond to the arrangement described in FIG.
  • a fourth variant of the transmission described in Fig. 1 is shown.
  • the transmission corresponds largely to the embodiment described in Fig. 1.
  • An essential difference to the transmission described in Fig. 1 is expressed in the geometric position of the third clutch K3 ".
  • the third clutch K3" is arranged coaxially with the output shaft 2.
  • the third clutch K3 ", the first spur gear ST1, the second spur gear ST2 and the fourth clutch K4 are arranged in the stated order, starting at the free end of the output shaft 2.
  • the third clutch K3" and the fourth clutch K4 are arranged coaxially with the output shaft 2.
  • At least one spur gear of the first spur gear ST1 and at least one spur gear of the second spur gear ST2 are also arranged coaxially with the output shaft 2.
  • the planetary carrier is eng PT2 of the second planetary PR2 directly connected to the drive shaft 1.
  • the ring gear H2 of the second planetary gear PR2 is connected to the sixth shaft 6, wherein the sixth shaft 6 is further connected to the first spur gear ST1.
  • the first spur gear ST1 is further connected to the fifth shaft 5, which can be connected to the output shaft 2 via the third clutch K3 "All other connections and interfaces as well as the arrangement of the respective components correspond to the arrangement described in FIG.
  • FIG. 5 shows a fifth variant of the transmission described in FIG. 1.
  • This differs from the variant described in Fig. 1 in that the second clutch K2 'and the third clutch K3' spatially between the first planetary PR1 and the second planetary PR2 and the first spur gear ST1 in the order of the first planetary PR1 and second planetary PR2, second clutch K2 ', third clutch K3', first spur gear ST1 coaxial with the third shaft 3 are arranged.
  • the drive shaft 1 can be connected to the third shaft 3 via the first clutch K1.
  • the third shaft 3 is further connected via the second clutch K2 'with the fourth shaft 4, wherein the fourth shaft 4 is further connected to the planet carrier PT1 of the first planetary gear set PR1.
  • the drive shaft 1 is connected to the sun gear S1 of the first planetary gear PR1 and the planet carrier PT2 of the second planetary PR2.
  • the ring gear H2 of the second planetary PR2 is connected to the sixth shaft 6, wherein the sixth shaft 6 via the third clutch K3 'with the fifth shaft 5 is connectable.
  • the fifth shaft 5 is further connected to the first spur gear ST1, and the first spur gear ST1 is further connected to the output shaft 2.
  • the embodiment shown in FIG. 5 results from a combination of the embodiments of the alternative embodiments of the second clutch K2 'and the third clutch K3' described in FIGS. 2 and 3.
  • FIG. 6 shows a further embodiment of the transmission described in FIG. 1.
  • the second clutch K2 ' is spatially arranged between the first plane tenradsatz PR1 and the second planetary PR2 and the first spur gear ST1 in coaxial arrangement with the third shaft 3 is positioned.
  • the third clutch K3 is arranged coaxially with the output shaft 2, wherein the following elements along the output shaft 2, starting at the free end of the output shaft 2, in the order third clutch K3", first spur ST1, second spur ST2, fourth clutch K4 are arranged.
  • the deviations with regard to the interfaces or connections of the individual elements described below result from the aforementioned changes in the positioning of the second clutch K2 'and the third clutch K3.
  • the drive shaft 1 can be connected to the third shaft 3 via the first clutch K1, wherein the third The third shaft 4 is further connectable to the fourth shaft 4 via the second clutch K2 'and the fourth shaft 4 is further connected to the planet carrier PT1 of the first planetary gear set PR1
  • the ring gear H2 of the second planetary gearset PR2 is connected to the sixth shaft 6, the sixth shaft 6 being further connected to the first spur gear ST1 fifth shaft 5 via the third clutch K3 "with the Abt the shaft 2 is connectable. All other connections and interfaces as well as the arrangement of the respective components correspond to the arrangement described in FIG.
  • the embodiment of the transmission shown in FIG. 6 results from a combination of the embodiments of the second clutch K2 'and the third clutch K3 "described in FIGS. 2 and 4.
  • a further embodiment of the transmission described in Fig. 1 is shown. This differs from the arrangement described in FIG. 1 in that the fourth clutch K4 'is positioned spatially between the second spur gear ST2 and the third planetary gear set PR3 in coaxial arrangement with the third shaft 3. Among other things, this leads to the output shaft 2 being free of switching elements. The positioning of the fourth clutch K4 'results in deviations with respect to the interfaces, which will be described below.
  • the planet carrier PT3 of the third planetary gear set PR3 is connected via the eighth shaft 8 to the ring gear H1 of the first planetary gear set PR1 and the sun gear. wheel S2 of the second planetary PR2.
  • the eighth shaft 8 via the fourth clutch K4 'with the ninth shaft 9 connectable.
  • the ninth shaft 9 is further connected to the second spur gear ST2, and the second spur gear ST2 is further connected to the output shaft 2. All other connections and interfaces as well as the arrangement of the respective components correspond to the arrangement described in FIG.
  • Fig. 8 shows in a table a switching matrix of the transmission according to the invention.
  • An X in the respective field of the table indicates which of the switching elements is closed for the realization of the first to ninth forward gear and the reverse gear.
  • the numbers 4-I, 4-II and 4-III three switching alternatives for the fourth forward gear are specified.
  • the switching states of the alternative embodiment of the second clutch K2 ' are identical to the switching states of the second clutch K2.
  • the same applies to the switching states of the alternative embodiment of the third clutch K3 ', K3 "and the shifting states of the third clutch K3 or the shifting states of the alternative embodiment of the fourth clutch K4' and the shifting states of the fourth clutch K4 alternative embodiments of the third clutch ⁇ 3 ', K3 "in the table are defined in each case via the switching state of the third clutch K3.
  • the table shows the corresponding gear jumps of the forward gears.
  • a gear jump is the quotient of the translation of the lower forward gear and the adjacent higher forward gear to understand.
  • the transmission spread as quotient of the transmission ratio of the lowest forward speed and the transmission ratio of the highest forward speed is 8.942.

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

Abstract

Boîte de vitesses, comprenant un arbre d'entrée (1), un arbre de sortie (2), un carter (G), un premier train planétaire (PR1), un deuxième train planétaire (PR2) et un troisième train planétaire (PR3), six organes de changement de vitesses, comportant un premier frein (B1), un deuxième frein (B2), ainsi qu'un premier embrayage (K1), un deuxième embrayage (K2, K2'), un troisième embrayage (K3, K3', K3'') et un quatrième embrayage (K4, K4'), les organes de changement de vitesses étant actionnables sélectivement, ce qui permet d'obtenir neuf 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), chaque train planétaire (PR1, PR2, PR3) présentant au moins un pignon solaire (S1, S2, S3), un satellite, un porte-satellites (PT1, PT2, PT3) et une couronne (H1, H2, H3), 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) peut être relié à la couronne (H3) du troisième train planétaire (PR3) et au deuxième frein (B2) par l'intermédiaire du premier embrayage (K1), la couronne (H3) du troisième train planétaire (PR3) et le deuxième frein (B2) étant également reliés ensemble et un troisième arbre (3) étant disposé coaxialement à l'arbre d'entrée (1).
EP13780149.4A 2012-11-21 2013-10-24 Boîte de vitesses à trains planétaires à 9 rapports Withdrawn EP2923113A1 (fr)

Applications Claiming Priority (2)

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DE102012221235.3A DE102012221235A1 (de) 2012-11-21 2012-11-21 Getriebe
PCT/EP2013/072226 WO2014079643A1 (fr) 2012-11-21 2013-10-24 Boîte de vitesses à trains planétaires à 9 rapports

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EP2923113A1 true EP2923113A1 (fr) 2015-09-30

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US (1) US9382979B2 (fr)
EP (1) EP2923113A1 (fr)
CN (1) CN104813070B (fr)
DE (1) DE102012221235A1 (fr)
WO (1) WO2014079643A1 (fr)

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DE102013202886A1 (de) * 2013-02-22 2014-08-28 Zf Friedrichshafen Ag Mehrstufengetriebe in Planetenbauweise
JP6206294B2 (ja) * 2014-03-28 2017-10-04 マツダ株式会社 自動変速機
JP6511943B2 (ja) * 2015-04-30 2019-05-15 アイシン・エィ・ダブリュ株式会社 変速装置
EP3118484B1 (fr) * 2015-07-16 2018-03-21 ZF Friedrichshafen AG Boite de vitesses pour un vehicule hybride, chaine cinematique pour un vehicule hybride ayant une telle boite de vitesse, et procede de demarrage d'un vehicule hybride
DE102016211225B3 (de) * 2016-06-23 2017-10-19 Bayerische Motoren Werke Aktiengesellschaft Kombiniertes Mehrstufengetriebe
DE102016212060B3 (de) * 2016-07-01 2017-10-19 Bayerische Motoren Werke Aktiengesellschaft Kombiniertes Mehrstufenumlaufgetriebe
DE102018112405B3 (de) * 2018-05-24 2019-03-28 Schaeffler Technologies AG & Co. KG Antriebsvorrichtung mit einer elektrischen Maschine

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Publication number Publication date
WO2014079643A1 (fr) 2014-05-30
CN104813070A (zh) 2015-07-29
US20150300458A1 (en) 2015-10-22
CN104813070B (zh) 2017-08-04
US9382979B2 (en) 2016-07-05
DE102012221235A1 (de) 2014-05-22

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