EP2923114A1 - Boîte de vitesses à trains planétaires à 9 rapports - Google Patents

Boîte de vitesses à trains planétaires à 9 rapports

Info

Publication number
EP2923114A1
EP2923114A1 EP13780150.2A EP13780150A EP2923114A1 EP 2923114 A1 EP2923114 A1 EP 2923114A1 EP 13780150 A EP13780150 A EP 13780150A EP 2923114 A1 EP2923114 A1 EP 2923114A1
Authority
EP
European Patent Office
Prior art keywords
clutch
planetary gear
gear
closed
gear set
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Withdrawn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
EP13780150.2A
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 EP2923114A1 publication Critical patent/EP2923114A1/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Withdrawn legal-status Critical Current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
    • 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
    • F16H2306/00—Shifting

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.
  • 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 at which the torque, taking into account the corresponding transmission ratios, is introduced, for example, into a transfer case or transmitted to drive shafts of the vehicle.
  • 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. In particular, 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 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 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 freely rotatable, 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 ro- tierbaren component to a standstill, which means that a firm connection between the rotatable element and the stationary element can be produced.
  • 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. Are rotatably mounted on the planet carrier 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 the planetary gears are rotatably mounted, with a sun gear and with a ring gear, wherein the toothing meshes with at least one of the planet gears 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 second clutch with the ring gear of the second planetary gear set and the sun gear of the third planetary gear set is connectable.
  • the ring gear of the second planetary gear set and the sun gear of the third planetary gear set are also connected to each other.
  • the external teeth of the ring gear of the second planetary gear mesh with the teeth of the planetary gears of the third planetary gear set.
  • the drive shaft is connected via the first clutch to the second brake and the sun gear of the second planetary gear set, wherein the second brake and the sun gear of the second planetary gear set are preferably also connected to each other.
  • the second brake and the sun gear of the second planetary gear set are preferably also connected to each other.
  • 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, for example, electromechanical switching elements or electromagnetic switching elements, are particularly suitable here. 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.
  • 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 ring 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.
  • the transmission is particularly preferably 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.
  • this is of particular importance since the available space for the drive source and the transmission is limited in a special way by the vehicle width.
  • 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.
  • the respective parts of the spur gears or the axes of rotation of the shafts and spur gears are arranged parallel to each other.
  • the two front drives are particularly preferably arranged between the first planetary gear set and the second planetary gear set in the order of the 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 not intersect the various waves, for example, in the arrangement.
  • the first planetary gear set, the second planetary gear set, and the third planetary gear set are preferably arranged coaxially with the drive shaft.
  • a spur gear of the first spur gear and a spur gear of the second spur gear are arranged coaxially with the drive shaft.
  • the second planetary gear set and the third planetary gear set are axially positioned with respect to the drive shaft such that the third planetary gear set is disposed radially above the second planetary gear set.
  • the arrangement of the third planetary gear set radially above the second planetary gear set is characterized in a special way by a particularly small axial space requirement.
  • the ring gear of the second planetary gear set and the sun gear of the third planetary gear set are interconnected.
  • a one-piece or one-piece design of the sun gear of the third planetary gear and the ring gear of the second planetary gear is conceivable.
  • this case for example, has the ring gear of the second planetary gear in addition to an internal toothing, which meshes with the teeth of the planetary gears of the second planetary gear, via an external toothing, which preferably takes over the function of the teeth of the sun gear of the third planetary gear.
  • the external teeth of the ring gear of the second planetary gear set mesh with the teeth of the planet gears of the third planetary gear set.
  • this arrangement allows to use the outer radius of the ring gear of the third planet carrier simultaneously as a plate carrier, which is for example in engagement with the first brake.
  • first clutch and the second clutch are each connected at one of its sides to the drive shaft. As a result, the first clutch and the second clutch are particularly well accessible from the outside.
  • 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 in a special way as cost-effective implementation possibility. At the same time, 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 third clutch to the planet carrier of the first planetary gear set is connectable.
  • the sun gear of the first planetary gear set is preferably connected to a second spur gear and the planet carrier of the third planetary gear set.
  • the second spur gear is preferably further connected via the fourth clutch to the output shaft and the planet carrier of the third planetary gear set is further preferably connected to the planet carrier of the second planetary gear set.
  • the ring gear of the first planetary gear set with a first spur gear and the first spur gear is further connected to the output shaft.
  • the drive shaft is connected to the planet carrier of the first planetary gear set. More preferably that is Sun of the first planetary gear set via the third clutch with a second spur gear and the planet carrier of the third planetary gear set connectable.
  • the second spur gear is further preferably connected via the fourth clutch to the output shaft and the planet carrier of the third planetary gear set is further connected to the planet carrier of the second planetary gear set.
  • the ring gear of the first planetary gear set with a first spur gear and the first spur gear is further preferably connected to the output shaft.
  • the drive shaft is connected to the planet carrier of the first planetary gear set.
  • the sun gear of the first planetary gear set is further preferably connected to a second spur gear and the planet carrier of the third planetary gear set, wherein the second spur gear is further preferably connected via the fourth clutch to the output shaft.
  • the planet carrier of the third planetary gear set is connected to the planet carrier of the second planetary gear set.
  • the ring gear of the first planetary gear set is preferably connectable via the third clutch with a first spur gear.
  • the first spur gear is further preferably connected to the output shaft.
  • the drive shaft is connected to the planet carrier of the first gearset.
  • the sun gear of the first planetary gear set is preferably connected to a second spur gear and the planet carrier of the third planetary gear set.
  • the second spur gear is further preferably connected via the fourth clutch to the drive shaft and the planet carrier of the third planetary gear set further preferably connected to the planet carrier of the second planetary gear set.
  • the ring gear of the first planetary gear set is connected to a first spur gear and the first spur gear further connectable via the third clutch to the output shaft.
  • the drive shaft via the third clutch with the planet carrier of the first planetary gear set is connectable. More preferably, the sun gear of the first planetary gear set is connected to the planet carrier of the third planetary gear set. Via the fourth clutch, the sun gear of the first planetary gear set is preferably connected to a second spur gear. bindable, wherein the second spur gear is further preferably connected to the output shaft.
  • the planet carrier of the third planetary gear set is connected to the planet carrier of the second planetary gear set. More preferably, the ring gear of the first planetary gear set is connected to a first spur gear and the first spur gear further connected to the output shaft.
  • the first forward gear is preferably represented by the closed first brake, the closed second clutch and the closed fourth clutch. Due to the closed second brake, the closed second clutch and the closed fourth clutch, the second forward gear is preferably displayed.
  • 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 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 first brake, the closed first clutch and the closed third clutch. Due to the closed first brake, the closed first clutch and the closed fourth clutch, the reverse gear is preferably displayed.
  • the switching elements not mentioned in each case are preferably opened in the corresponding gear.
  • a method of operating a transmission is proposed.
  • at least nine forward gears can be selected so that in each gear each three switching elements are closed and the other switching elements are 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. This particularly preferably contributes to a reduction of the switching times. Regardless of whether hydraulically, electromechanically or in any other way operable, this leads to a lower 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.
  • All switching elements can basically act in each case frictionally or positively.
  • the second clutch and the fourth clutch are particularly preferably designed as form-locking switching elements, 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 any other power / drive unit 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.
  • FIG. 5 shows a schematic view of a fifth preferred embodiment of a transmission according to the invention.
  • FIGS. 1 to 5 shows an exemplary circuit diagram for a transmission according to FIGS. 1 to 5.
  • 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 B1 and the second brake B2 are each connected at one side to the housing G.
  • 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. On one, the first side of the drive shaft 1 opposite side, the drive shaft 1 is connected to the first clutch K1. Spatially between the free end of the drive shaft 1 of the first clutch K1, the third clutch K3, the first planetary gear set PR1, the first spur gear ST1, the second front end drive ST2 and the second clutch K2 arranged in the order mentioned along the drive shaft 1. In addition, located between the second clutch K2 and the first clutch K1 in a spatial arrangement along the drive shaft 1, the second planetary PR2, the third planetary PR3, the first brake B1 and the second brake B2.
  • the third planetary PR3 is arranged radially over the second planetary PR2. This means that the ring gear H2 of the second planetary PR2 is connected to the sun gear S3 of the third planetary PR3. Radially above the third planetary PR3 and the ring gear H3 of the third planetary gear set PR3, the first brake B1 is arranged.
  • the first clutch K1, the first brake B1, the second brake B2, the second clutch K2, the third clutch K3, the first planetary PR1, the second planetary PR2 and the third planetary PR3 are arranged coaxially to the drive shaft 1. 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 drive shaft 1.
  • the output shaft 2 also has a free end on a first side.
  • the free end of the output shaft 2 and the free end of the drive shaft 1 point in the same direction.
  • the first spur gear ST1, the second spur gear ST2 and the fourth clutch K4 are arranged beginning at the free end of the output shaft 2 in the order named.
  • the fourth clutch K4 is arranged coaxially with the output shaft 2.
  • At least one respective spur gear of the first spur gear ST1 and one spur gear of the second spur gear ST2 are also arranged coaxially to the output shaft 2.
  • the drive shaft 1 is connected via the first clutch K1 with a third shaft 3, wherein the third shaft 3 is further connected to the second brake B2 and the sun gear S2 of the second planetary PR2.
  • the third shaft 3 connects the second brake B2 and the sun gear S2 of the second planetary gear set PR2 with each other.
  • the drive shaft 1 via the second clutch K2 with a fourth shaft 4 is connectable, wherein the fourth shaft 4 is further connected to the ring gear H2 of the second planetary PR2 and the sun gear S3 of the third planetary PR3.
  • the drive shaft 1 via the third clutch K3 with a fifth shaft 5 is connectable.
  • the fifth wave 5 is further connected to the planet carrier PT1 of the first planetary PR1.
  • the sun gear S1 of the first planetary gear set PR1 is connected to a seventh shaft 7.
  • the seventh shaft 7 is also connected to the second spur gear ST2 and the planet carrier PT3 of the third planetary PR3.
  • the second spur gear ST2 is further connected to a ninth shaft 9, wherein the ninth shaft 9 can be further connected to the output shaft 2 via the fourth clutch K4.
  • the planet carrier PT3 of the third planetary PR3 is further connected via the seventh shaft 7 with the planet carrier PT2 of the second planetary PR2.
  • the ring gear H1 of the first planetary gear PR1 is connected via a sixth shaft 6 to the first spur gear ST1, wherein the first spur gear ST1 is further connected to the output shaft 2.
  • the ring gear H3 of the third planetary PR3 is connected via an eighth shaft 8 with the first brake B1.
  • 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 gear set PR2 or the sun gear 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 clutch K1, the third clutch K3 and the fourth clutch K4 are particularly well accessible from the outside in the present embodiment, since no further components and / or connecting elements are arranged between the housing G and said switching elements.
  • Fig. 2 shows a further embodiment of the transmission described in Fig. 1, which is primarily by a different positioning of the third Clutch K3 'differs from the embodiment described in Fig. 1.
  • the third clutch K3 ' is positioned in the present example spatially between the first spur gear ST1 and the second spur gear ST2 in coaxial arrangement with the drive shaft 1.
  • the drive shaft 1 is here directly connected to the planet carrier PT1 of the first planetary PR1.
  • the sun gear S1 of the first planetary gear PR1 is connected to the fifth shaft 5, wherein the fifth shaft 5 via the third clutch K3 'with the seventh shaft 7 is connectable.
  • the seventh shaft 7 further connects the second spur gear ST2 to the planet carrier PT3 of the third planetary gear set PR3.
  • the second spur gear ST2 is further connected to the ninth shaft 9, wherein the ninth shaft 9 via the fourth clutch K4 with the output shaft 2 is connectable.
  • the planet carrier PT3 of the third planetary PR3 is connected via the seventh shaft 7 with the planet carrier PT2 of the second planetary PR2. All other interfaces, connections and arrangements of the individual elements and components correspond to the arrangement described in FIG.
  • FIG. 3 shows a further embodiment of the transmission described in FIG. This differs from the arrangement described in Fig. 1 in that the third clutch K3 "is positioned spatially between the first planetary gear set PR1 and the first spur gear ST1 in coaxial arrangement with the drive shaft 1.
  • the resulting changes in the connections and interfaces The drive shaft 1 is now connected directly to the planet carrier PT1 of the first planetary gearset PR1
  • the ring gear H1 of the first planetary gearset PR1 is connected to the fifth shaft 5, the fifth shaft 5 being connected to the sixth shaft 6 via the third clutch K3 " is connectable.
  • the sixth shaft 6 is further connected to the first spur gear ST1, and the first spur gear ST1 is further connected to the output shaft 2. All other interfaces, connections and arrangements of the individual elements correspond to the arrangement described in FIG.
  • FIG. 4 a further variant of the transmission described in Fig. 1 is shown.
  • 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 in the present embodiment.
  • the third clutch K3 "of the first spur gear ST1, the second spur gear ST2 and the fourth clutch K4 are arranged in the order just mentioned starting at the free end of the output shaft 2. Due to the arrangement described in FIG deviating positioning of the third clutch K3 '"results in deviations in the interfaces and connections, which are described below.
  • the drive shaft 1 is now connected directly to the planet carrier PT1 of the first planetary PR1.
  • the ring gear H1 of the first planetary gear PR1 is connected via the sixth shaft 6 to the first spur gear ST1, wherein the first spur gear ST1 is further connected to the fifth shaft 5.
  • the fifth shaft 5 can be connected via the third clutch K3 "to the output shaft 2. All other interfaces, connections and arrangements of the individual elements correspond to the arrangement described in FIG.
  • FIG. 5 shows a further embodiment of the transmission described in FIG. 1. This differs from the arrangement described in FIG. 1 in that the fourth clutch K4 'is positioned in a coaxial arrangement with the drive shaft 1 spatially between the second spur gear ST2 and the second clutch K2.
  • the resulting deviations in the interfaces and connections compared to the arrangement described in Fig. 1 are described below.
  • the sun gear S1 of the first planetary gear set PR1 is connected to the seventh shaft 7.
  • the seventh shaft 7 is also connected to the planet carrier PT3 of the third planetary PR3 and connectable via the fourth clutch K4 'with the ninth shaft 9.
  • the ninth shaft 9 is also connected to the second spur gear ST2, wherein the second spur gear ST2 is further connected to the output shaft 2.
  • the planet carrier PT3 of the third planetary PR3 is further connected via the seventh shaft 7 with the planet carrier PT2 of the second planetary PR2. All other interfaces, connections fertilize and arrangements of the individual elements correspond to the arrangement described in Fig. 1.
  • Fig. 6 shows in a table a switching matrix of the transmission according to the invention.
  • An X in the respective field 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 embodiments of the third clutch ⁇ 3 ', K3 ", ⁇ 3'” are identical to the switching states 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 8.658.

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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), un troisième embrayage (K3, 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 (H2) du deuxième train planétaire (PR2) et au pignon solaire (S3) du troisième train planétaire (PR3) par l'intermédiaire du deuxième embrayage (K2), et en ce que l'arbre d'entrée (1) peut être relié au deuxième frein (B2) et au pignon solaire (S2) du deuxième train planétaire (PR2) par l'intermédiaire du premier embrayage (K1), la couronne (H2) du deuxième train planétaire (PR2) et le deuxième frein (B2) étant également reliés ensemble.
EP13780150.2A 2012-11-21 2013-10-24 Boîte de vitesses à trains planétaires à 9 rapports Withdrawn EP2923114A1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102012221234.5A DE102012221234A1 (de) 2012-11-21 2012-11-21 Getriebe
PCT/EP2013/072228 WO2014079644A1 (fr) 2012-11-21 2013-10-24 Boîte de vitesses à trains planétaires à 9 rapports

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EP2923114A1 true EP2923114A1 (fr) 2015-09-30

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US (1) US9599196B2 (fr)
EP (1) EP2923114A1 (fr)
CN (1) CN104813069B (fr)
DE (1) DE102012221234A1 (fr)
WO (1) WO2014079644A1 (fr)

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* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102013205377A1 (de) * 2013-03-27 2014-10-02 Zf Friedrichshafen Ag Mehrstufen-Planetengetriebe
DE102016207440A1 (de) * 2016-04-29 2017-11-02 Zf Friedrichshafen Ag Getriebe für ein Kraftfahrzeug, sowie Antriebsstrang für ein Kraftfahrzeug mit einem solchen Getriebe
DE102016015302A1 (de) * 2016-12-22 2018-06-28 Daimler Ag Gruppengetriebevorrichtung
US11073198B1 (en) * 2020-04-27 2021-07-27 Steering Solutions Ip Holding Corporation Dual motor dual epicyclical gearbox with coupled annulus with external teeth

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US7118508B2 (en) * 2004-07-28 2006-10-10 General Motors Corporation Planetary transmissions having three interconnected gear members and clutched input members
US7828688B2 (en) 2007-07-09 2010-11-09 Gm Global Technology Operations, Inc. 10-speed transmission
US8113977B2 (en) * 2007-10-12 2012-02-14 GM Global Technology Operations LLC Eight and nine speed automatic transmissions
US20090305837A1 (en) * 2008-06-09 2009-12-10 Kazuyoshi Hiraiwa Planetary gear type multi-stage transmission
JP5088498B2 (ja) 2008-06-19 2012-12-05 セイコーエプソン株式会社 発光装置
JP5138500B2 (ja) * 2008-08-07 2013-02-06 本田技研工業株式会社 自動変速機
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KR101776712B1 (ko) * 2011-04-26 2017-09-08 현대자동차 주식회사 차량용 자동변속기의 유성기어트레인
DE102012224118A1 (de) * 2012-12-21 2014-06-26 Zf Friedrichshafen Ag Mehrstufengetriebe
DE102013202888A1 (de) * 2013-02-22 2014-08-28 Zf Friedrichshafen Ag Mehrstufengetriebe in Planetenbauweise

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Publication number Publication date
DE102012221234A1 (de) 2014-05-22
US9599196B2 (en) 2017-03-21
CN104813069A (zh) 2015-07-29
US20150285342A1 (en) 2015-10-08
WO2014079644A1 (fr) 2014-05-30
CN104813069B (zh) 2017-08-08

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