EP2979004A1 - Boîte de vitesses destinée à un véhicule automobile - Google Patents

Boîte de vitesses destinée à un véhicule automobile

Info

Publication number
EP2979004A1
EP2979004A1 EP14706579.1A EP14706579A EP2979004A1 EP 2979004 A1 EP2979004 A1 EP 2979004A1 EP 14706579 A EP14706579 A EP 14706579A EP 2979004 A1 EP2979004 A1 EP 2979004A1
Authority
EP
European Patent Office
Prior art keywords
clutch
closed
open
brake
planetary gear
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Withdrawn
Application number
EP14706579.1A
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 EP2979004A1 publication Critical patent/EP2979004A1/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Withdrawn legal-status Critical Current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
    • 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
    • F16H3/663—Gearings having three or more central gears composed of a number of gear trains without drive passing from one train to another with conveying rotary motion between axially spaced orbital gears, e.g. RAVIGNEAUX
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H3/00—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion
    • F16H3/44—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion using gears having orbital motion
    • F16H2003/445—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion using gears having orbital motion without permanent connection between the input and the set of orbital gears
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H2200/00—Transmissions for multiple ratios
    • F16H2200/003—Transmissions for multiple ratios characterised by the number of forward speeds
    • F16H2200/0065—Transmissions for multiple ratios characterised by the number of forward speeds the gear ratios comprising nine forward speeds
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H2200/00—Transmissions for multiple ratios
    • F16H2200/003—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
    • F16H2200/003—Transmissions for multiple ratios characterised by the number of forward speeds
    • F16H2200/0073—Transmissions for multiple ratios characterised by the number of forward speeds the gear ratios comprising eleven 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
    • F16H2200/003—Transmissions for multiple ratios characterised by the number of forward speeds
    • F16H2200/0078—Transmissions for multiple ratios characterised by the number of forward speeds the gear ratio comprising twelve or more 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
    • F16H2200/2012—Transmissions using gears with orbital motion characterised by the number of sets of orbital gears with four 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 invention relates to a transmission, in particular multistage transmission, for a motor vehicle, comprising a housing, a drive shaft, an output shaft, at least four planetary gear sets, the planetary gear sets each comprising a sun gear, a planet, a planet carrier and a ring gear, and a plurality of switching elements in the form of at least four clutches and at least two brakes.
  • WO 2012/052284 A1 a multistage transmission with six forward gears and one reverse gear is shown, which comprises four planetary gear sets, seven rotatable shafts and five shift elements, wherein the sun gear of the first planetary gear set is connected to the sixth shaft, which via a first brake to the Housing of the transmission can be coupled, wherein the web of the first planetary gear set is connected to the fifth shaft, which is connected to the sun gear of the second planetary gear set and coupled via a second brake to the housing, wherein the drive shaft with the ring gear of the first planetary gear set and the sun gear connected to the third planetary gear set and via a clutch with the connected to the web of the third planetary and the ring gear of the fourth planetary gear seventh shaft is detachably connected, wherein the fourth shaft connected to the ring gear of the third planetary gear set and the web of the second planetary gear set and a third brake is coupled to the housing, wherein the output shaft is connected
  • the disadvantage here is that switching elements such as multi-plate clutches or brakes are hydraulically actuated. This hydraulic actuation leads to high hydraulic losses. In order to circumvent these actuation losses, it has been proposed to provide electromechanical or electrohydraulic actuations.
  • the disadvantage here is again that the switching elements before in particular, the couplings are difficult to access, especially when good gear efficiencies and low component loads are sought at low construction costs.
  • An object of the present invention is therefore to provide a transmission for a motor vehicle, which has a good efficiency, low component load and low construction costs. Moreover, it is an object of the present invention to provide a transmission for a motor vehicle, which has good accessibility of its switching elements from the outside. Another object of the present invention is to provide an alternative transmission for a motor vehicle.
  • the present invention solves the problems in a transmission, in particular ehrcutnget ebe, for a motor vehicle, comprising a housing, a drive shaft, an output shaft, at least four planetary gear sets, wherein the Planentenrad arrangements each comprise a sun gear, a planet, a planet carrier and a ring gear, and a plurality of switching elements in the form of at least four clutches and at least two brakes, characterized in that the drive shaft via the second clutch with the planet carrier of the third planetary gear set and the planet carrier of the fourth planetary gear set is connectable, that the first brake with the ring gear of the first planetary gear set and with the Planet carrier of the second Planentenradsatzes is connected, that the second brake is connected to the sun gear of the first planetary gear set, and that the planet carrier of the first planetary gear set is connected to the sun gear of the fourth planetary gear set.
  • the invention solves the tasks also in a motor vehicle, in particular in a passenger or truck with a transmission according to one of claims 1 -5.
  • the invention also solves the problems with a method for operating a transmission, in particular according to one of claims 1-5, with two brakes and four clutches in that a first gear by means of closed first brake, open second brake, closed first clutch, open second
  • a second gear is formed by means of a closed first brake, a closed second brake, a closed first clutch, an open second clutch, an open third clutch and an open fourth clutch, and a third gear by means of a closed first brake, an open second brake, a closed first clutch, an open second clutch, closed third clutch and fourth open clutch is formed, and that a fourth gear by open first brake, closed second brake, closed first clutch, open second clutch, closed third clutch and fourth open clutch is formed and that a fifth gear by means of open first brake, open second brake, closed first clutch, closed second clutch, closed third clutch and fourth open clutch or by means of closed first brake, open second brake, open first clutch, closed second clutch, third open Clutch and closed fourth clutch or by means of open first brake, closed second brake, open first clutch, closed second clutch, third open Clutch and closed fourth clutch or by means of open first brake, closed second brake, open first clutch, closed second clutch, third open clutch and fourth clutch closed or by open first brake, open second brake, open first clutch, closed second clutch, third open clutch
  • a torque or a rotational movement of a drive shaft is preferably introduced into the transmission via the drive shaft.
  • a retraction 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 referred to in particular as connected to each other, if between the elements a solid, in particular rotationally fixed connection exists. 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.
  • a clutch is preferably in the description, in particular in the claims, a switching element to understand, which, depending on the operating state, a relative movement between two components permits or represents a connection for transmitting torque.
  • 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.
  • 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 switching element to understand which is connected on one side with a fixed element, such as a housing, and on another side with a rotatable element.
  • a non-actuated brake is understood to mean an opened brake.
  • the rotating component is freely rotatable, i.e., the brake preferably does not influence the rotational speed of the rotating component.
  • the brake is applied or closed, the rotational speed of the rotatable component is reduced to a standstill, that is, a firm 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 comprises a sun gear, a planet carrier respectively web and a ring gear.
  • Rotatably mounted on the planet carrier respectively web are planet gears or planets, which mesh with the toothing of the sun gear and / or the toothing of the ring gear.
  • a minus planetary gearset describes a planetary gearset with a planet carrier on which the planetary gears are rotatably mounted, with a sun gear and 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 toothing 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.
  • a planetary gear set in particular, the sun gear, the ring gear, the planet carrier respectively web and the planet gears respectively the planet of the planetary gear understood.
  • the switching elements are selectively, ie individually and as needed actuated, whereby different gears through different
  • Transmission ratios between the drive shaft and the output shaft real- are sierbar.
  • this contributes to an increase in ride comfort, since the internal combustion engine is preferably operable at a low speed level. For example, noise emissions resulting from the operation of the internal combustion engine are also reduced.
  • front-transverse arrangement is to be understood as an arrangement in which the drive shaft, for example an internal combustion engine, is installed transversely to a direction of travel in a motor vehicle and preferably the wheels of a front axle can be driven by the drive shaft or the transmission
  • the switching elements may be designed such that energy is needed for a change of a switching state of the switching elements, but not for maintaining the switching state itself.
  • switching elements which can be actuated as required in a particular manner, such as, for example, electromechanical switching elements or electromagnetic switching elements, are suitable for this purpose. 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 be advantageously omitted to permanently maintain a control pressure for the operation of, for example, conventionally hydraulic switching elements, or to act on the respective switching element in the switched state permanently with the required hydraulic pressure.
  • other components such as a hydraulic pump can be omitted, as far as they are used exclusively for controlling and supplying the conventionally hydraulically actuated switching elements.
  • This also particularly preferably contributes to an increase in efficiency of the transmission in the form of a higher efficiency.
  • switching elements are particularly well preferably arranged so that they are easily accessible from the outside.
  • Well accessible from the outside means in the sense of the switching elements, the intermediate housing of the transmission and the 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.
  • bondability is preferably to be understood in the description, in particular in the claims, that in the case of a different geometric position, the same connection or binding of interfaces is ensured without individual connecting elements or waves crossing each other.
  • stand translation is that translation to understand that is realized by the ratio between the sun and ring gear of each planetary gear set when the planet carrier respectively web is fixed.
  • the planetary gear sets in particular geometrically, are arranged behind one another in the transmission. This allows easy manufacture and easier accessibility of the planetary gear sets in the case of maintenance.
  • the drive shaft via the first clutch with the sun gear of the third planetary gear set is connectable or the planet carrier of the second planetary gear set is connected via the first clutch with the ring gear of the third planetary gear set.
  • a direct transmission of force and torque from the drive shaft to the central sun gear of the third planetary gear set or the flexibility of the transmission in terms of Representation of different grades is increased because then by means of the first clutch, as required, two planetary gear sets are coupled together.
  • the drive shaft via the third clutch with the sun gear of the second planetary gear set is connectable or the planet carrier of the first planetary gear set is connected via the third clutch with the ring gear of the second planetary gear set.
  • a direct transmission of force and torque from the drive shaft to the central sun gear of the third planetary gear set or the flexibility of the transmission with respect to the representation of different gear ratios is increased, as by means of the first clutch then as needed, two planetary gear sets are coupled together ,
  • the drive shaft via the fourth clutch to the planet carrier of the fourth planetary gear set is connectable or the planet carrier of the fourth planetary gear set is connected via the fourth clutch with the planet carrier of the first planetary gear set.
  • the output shaft can be flexibly connected to the fourth planetary gear as needed or the first planetary gear can be connected by means of the fourth clutch in a flexible manner and as needed directly to the fourth planetary gear.
  • an additional gear by means of open first brake, closed second brake, open first clutch, open second clutch, closed third clutch and closed fourth clutch and / or an additional gear by means of open first brake, closed second brake, closed first clutch, second open Clutch, open third clutch and closed fourth clutch formed.
  • FIG. 1 shows a transmission according to a first embodiment of the present invention
  • FIG. 2 shows a shift matrix for a transmission according to the first embodiment of the present invention
  • FIG. 7 shows a transmission according to a sixth embodiment of the present invention
  • 8 shows a transmission according to a seventh embodiment of the present invention
  • FIG. 10 shows a transmission according to a ninth embodiment of the present invention.
  • Fig. 1 1 shows a transmission according to a tenth embodiment of the present invention
  • FIG. 12 shows a transmission according to an eleventh embodiment of the present invention
  • Fig. 15 shows a transmission according to a fourteenth embodiment of the present invention.
  • Fig. 1 shows a transmission according to a first embodiment of the present invention.
  • reference numeral 1 denotes a multi-stage transmission.
  • the multi-speed transmission 1 has six shift elements in the form of four clutches K1, K2, K3, K4 and two brakes B1, B2.
  • the drive side can be coupled or connected to the output side of the transmission 1 for the transmission of force and torques.
  • the first clutch K1, the second clutch K2 and the third clutch K3 connected to the drive shaft ANW on the drive side.
  • the first clutch K1 is further connected to a connected to the first shaft W1, so that the first clutch K1 upon actuation transmits force and torque from the drive shaft ANW to the first shaft W1.
  • the fourth clutch K4 transmits power from a fifth shaft W5 to the output shaft AW.
  • the transmission 1 further four planetary gear sets GP1, GP2, GP3 and GP4 and six waves W1, W2, W3, W4, W5 and W6 are arranged.
  • the general structure of the first planetary gearset GP1, the second planetary gearset GP2, the third planetary gearset GP3 and the fourth planetary gearset GP4 will now be described in the following.
  • the above planetary gear sets GP1, GP2, GP3 and GP4 are constructed in the usual way and each have a central sun gear 101, 102, 103, 104, which with a planet 1 1 1, 1 12, 1 13, 1 14 for the transmission of Force and torque interacts.
  • the planet 1 1 1, 1 12, 1 13, 1 14 is rotatably mounted on a web / planet carrier 121, 122, 123, 124.
  • a ring gear 131, 132, 133, 134 is arranged, in which the respective planet 1 1 1, 1 12, 1 13, 1 14 for the transmission of Force and torque engages.
  • the web or planet carrier 121, 122, 123, 124 is further connected to a respective shaft.
  • the individual reference numerals for sun gear, planet, planet carrier / web and ring gear can be seen in Fig. 1. For clarity, the reference numerals have been omitted in the other figures.
  • the first shaft W1 connects the first clutch K1 and the sun gear 103 of the third planetary gear set GP3 for transmitting power and torques.
  • the second shaft W2 connects the second clutch K2 with the web 123 of the third planetary gear set GP3 and further with the web 124 of the fourth planetary gear set GP4.
  • the third wave W3 connects the third clutch K3 and the sun gear wheel 102 of the second planetary GP2.
  • the fourth shaft W4 can be connected to the housing G via a first brake B1; on the other hand, it connects the ring gear 131 of the first planetary gear set GP1, the land 122 of the second planetary gear set GP2, and the ring gear 133 of the third planetary gear set GP3.
  • the fifth shaft W5 connects the web 121 of the first planetary gear set GP1, the ring gear 132 of the second planetary gear set GP2 and the sun gear 104 of the fourth planetary gear set GP4.
  • the fifth shaft W5 can be connected via the fourth clutch K4 to the ring gear 134 of the fourth planetary gear set GP4 and to the output shaft AW.
  • the sixth shaft W6 can be connected to the housing G via a second brake B2; on the other hand, the sixth shaft W6 is connected to the sun gear 101 of the first planetary gearset GP1.
  • the output shaft AW is connected to the ring gear 134 of the fourth planetary gear set GP4 and connectable by means of the fourth clutch K4 with the fifth shaft W5.
  • Fig. 2 shows a shift matrix for a transmission according to the first embodiment of the present invention.
  • FIG. 2 shows a switching matrix for a transmission 1 according to FIG. 1.
  • An entry in the switching matrix provided with a cross designates a correspondingly actuated or closed switching element, that is to say in the switching matrix, for example in the forward gear stage V1 in the case of the brake B1 as well as the clutch K1 and the clutch K4.
  • the switching elements B1, B2, K1, K2, K3, K4 are open.
  • the gear ratio i is 4.890.
  • the gear ratio i is 2.934.
  • the gear ratio i is 1, 938.
  • the gear ratio i is 1, 347.
  • the gear ratio i is 1, 000.
  • the brake B2 and the clutch K1 and the clutch K2 are closed.
  • the gear ratio i is 0.834.
  • the gear ratio i is 0.69.
  • the gear ratio i is 0.600.
  • the gear ratio i is 0.543.
  • the brake B1 and the clutches K3 and K4 are closed.
  • the gear ratio i is -3.807.
  • the gear ratio i is 3,051.
  • the gear ratio i is -0.661.
  • the gear ratio i is 1, 000.
  • the gear ratio i is 1, 000.
  • the clutches K2, K3 and K4 are closed.
  • the gear ratio i is 1, 000.
  • the clutches K1, K2 and the clutch K4 are closed.
  • the gear ratio i is 1, 000.
  • the gear gap ⁇ between the first forward speed V1 and the second forward speed V2 is 1, 667, between the second forward speed V2 and the third forward speed V3 1, 514.
  • the gear gap ⁇ between the third forward speed V3 and the fourth forward speed V4 is 1, 439, between the fourth forward speed V4 and the fifth forward speed V5 1, 347.
  • the gear shift ⁇ between the fifth forward gear V5 and the sixth forward gear V6 is 1, 199, between the sixth forward speed V6 and the seventh forward speed V7 1, 207th
  • the gear gap ⁇ between the seventh forward speed V7 and the eighth forward speed V8 is 1, 151, between the eighth forward speed V8 and the ninth forward speed V9 1, 105.
  • the total jump is 9.006.
  • the first planetary gear set GP1 has a stand translation
  • i 0 -3.806
  • the third planetary gear set GP3 a stand ratio i 0 -3.891
  • the fourth planetary gear set GP4 a stand ratio of i 0 -1, 500 on.
  • Fig. 3 shows a transmission according to a second embodiment of the present invention.
  • FIG. 3 shows an alternative position A for the first clutch K1, in which the first clutch K1 can be arranged in an identical manner to the position according to FIG.
  • the alternative position A for the first clutch K1 is located between the web 122 of the second planetary gear set GP2 and the ring gear 133 of the third planetary gear set GP3 on the fifth shaft W5.
  • the first clutch K1 at the position A allows a coupling of the web 122 of the second planetary gearset GP2 and further via the fourth shaft W4 to the ring gear 133 of the third planetary gearset GP3.
  • the fourth wave W4 is coupled to the housing G via the first brake B1 as stated above.
  • FIG. 4 shows an alternative position B for the third clutch K3, in which the third clutch K3 can be arranged to have the same effect as the position according to FIG.
  • the alternative position B for the third clutch K3 is between the ring gear 132 of the second planetary gear set GP2 and the portion of the fifth shaft W5 connecting the land 121 of the first planetary gear set GP1 and the sun gear 104 of the fourth planetary gear set GP4.
  • the third clutch K3 at the position B allows at Betä- a coupling of the ring gear 132 of the second planetary GP2 with the fifth wave W5.
  • the fifth wave W5 is - as already stated above - further connected to the web 121 of the first planetary gear set GP1 and the sun gear 104 of the fourth planetary gear set GP4.
  • the fifth shaft W5 can be coupled via the fourth clutch K4 to the output shaft AW and to the ring gear 134 of the fourth planetary gear set GP4.
  • Fig. 5 shows a transmission according to a fourth embodiment of the present invention.
  • a transmission 1 according to FIG. 1 is shown substantially.
  • the fourth clutch K4 is not arranged to connect the fifth shaft W5 and the output shaft AW, but the fourth clutch K4, designated here by the reference symbol K4 ', serves to couple the second shaft W2 with the output shaft AW and with the ring gear 134 of the fourth planetary GP4.
  • Fig. 6 shows a transmission according to a fifth embodiment of the present invention.
  • FIG. 6 essentially shows a transmission 1 according to FIG. 5.
  • the fourth clutch K4 now denoted by reference symbol K4 ", now connects the fifth shaft W5 to the second shaft W2 via the web 124 of the fourth planetary gearset GP4 and thus via the fifth shaft W5 to the latter Sun gear 104 of the fourth planetary gear set GP4.
  • the fourth planetary gear set GP4 can be locked via sun gear 104 and web 124 by means of the fourth clutch K4 ".
  • FIG. 7 shows a transmission according to a sixth embodiment of the present invention.
  • the first clutch K1 is now arranged at the position A according to FIG. 3, now designated by the reference symbol K1 '.
  • the web 122 of the second planetary gearset GP2 can now be coupled to the ring gear 133 of the third planetary gearset GP3 by means of the first clutch K1 '.
  • the ring gear 133 of the third planetary gear GP3 is thus further coupled by means of the first clutch K1 'via the fourth shaft W4 with the ring gear 131 of the first planetary GP1 and coupled via the first brake B1 with the housing G.
  • the first shaft W1 is formed in the form of the drive shaft ANW and directly connected to the sun gear 103 of the third planetary GP3.
  • Fig. 8 shows a transmission according to a seventh embodiment of the present invention.
  • FIG. 8 shows a transmission 1 according to FIG. 7.
  • the fourth clutch K4 is now arranged at the position according to FIG. 5, designated here by reference K4 ' .
  • the fourth clutch K4 now allows a blocking of web 124 and ring gear 134 of the fourth planetary GP4.
  • the second shaft W2 can now be coupled via the fourth clutch K4 'to the output shaft AW and the ring gear 134 of the fourth planetary gearset GP4.
  • the first wave W1 is - as in Fig. 7 - formed in the form of the drive shaft ANW and directly connected to the sun gear 103 of the third planetary GP3.
  • Fig. 9 shows a transmission according to an eighth embodiment of the present invention.
  • FIG. 9 shows a transmission 1 according to FIG. 7.
  • the fourth clutch K4 here denoted by the reference symbol K4 "
  • the fourth clutch K4 now allows a blocking of the web 124 and sun gear 104 of the fourth Planetary gear set GP4 via the second wave W2 and the fifth wave W5.
  • the fifth shaft W5 can be coupled to the second shaft W2
  • the first shaft W1 is designed in the form of the drive shaft ANW and directly connected to the sun gear 103 of the third planetary gearset GP3.
  • FIG. 10 shows a transmission according to a ninth embodiment of the present invention.
  • FIG. 10 shows a transmission 1 according to FIG. 4.
  • the third clutch K3, designated here by the reference symbol K3 ' is now arranged in the region of the ring gear 132 of the second planetary gear set GP2 on the fifth shaft W5.
  • the ring gear 132 of the second planetary gearset GP2 can now be connected via the third clutch K3 'to the section of the fifth shaft W5, which connects the web 121 of the first planetary gear set GP1 and the sun gear 104 of the fourth planetary gear set GP4.
  • the ring gear 132 of the second planetary gear set GP2 can be coupled via the third clutch K3 'and the fourth clutch K4 to the output shaft AW and the ring gear 134 of the fourth planetary gear set GP4.
  • the third wave W3 is formed in the form of the drive shaft ANW and is directly connected to the sun gear 102 of the second planetary GP2.
  • Fig. 11 shows a transmission according to a tenth embodiment of the present invention.
  • a transmission 1 according to FIG. 10 is shown substantially.
  • the fourth clutch K4 here designated by reference K4
  • the fourth clutch K4 'now allows a blocking of web 124 and ring gear 134 of the fourth planetary GP4.
  • the second shaft W2 via the fourth clutch K4 'with the output shaft AW and - as already stated - be coupled to the ring gear 134 of the fourth planetary gear set GP4.
  • the third wave W3 is formed in the form of the drive shaft ANW and is directly connected to the sun gear 102 of the second planetary GP2.
  • FIG. 12 shows a transmission according to an eleventh embodiment of the present invention.
  • FIG. 12 essentially shows a transmission 1 according to FIG. 10.
  • the fourth clutch K4 here denoted by reference symbol K4 "
  • the fourth clutch K4" now enables a blocking of the bar 124 and sun gear 104 of the fourth planetary gear set GP4 via the second wave W2 and the fifth wave W5.
  • the fifth shaft W5 can therefore be coupled to the second shaft W2 by means of the fourth clutch K4.
  • the third shaft W3 is designed in the form of the drive shaft ANW and is connected directly to the sun gear 102 of the second planetary gearset GP2.
  • Fig. 13 shows a transmission according to a twelfth embodiment of the present invention.
  • FIG. 13 essentially shows a transmission 1 according to FIG. 10.
  • the first clutch K1 designated here by reference symbol K1 '
  • the third wave W3 is directly connected to the drive shaft ANW or formed as a drive shaft ANW and connected to both the sun gear 102 of the second planetary GP2 and the sun gear 103 of the third planetary GP3.
  • the first wave W1 is omitted.
  • Fig. 14 shows a transmission according to a thirteenth embodiment of the present invention.
  • a transmission 1 according to FIG. 13 is shown substantially.
  • the fourth clutch K4 here designated by reference symbol K4 ', is now arranged at the position according to FIG.
  • the fourth clutch K4 'thus enables a blocking of the web 124 of the fourth planetary gear set GP4 with the ring gear 134 of the fourth planetary GP4, as well as a connection of the second shaft W2 with the output shaft AW and with the ring gear 134 of the fourth planetary GP4.
  • FIG. 15 shows a transmission according to a fourteenth embodiment of the present invention.
  • FIG. 15 essentially shows a transmission 1 according to FIG. 13.
  • the fourth clutch K4 here denoted by reference symbol K4 ", is now arranged at the position according to Fig. 6.
  • the fourth clutch K4 thus enables a blocking of the web 124 of the fourth planetary gear set GP4 with the sun gear 104 of the fourth planetary gear set GP4 via the fifth shaft W5.
  • the transmission 1 comprises four planetary gear set planes GP1, GP2, GP3 and GP4, six switching elements B1, B2, K1, K2, K3, K4, the switching elements being in the form of four clutches K1, K2, K3 , K4 and two brakes B1, B2 are formed, therefore, therefore, the number of clutches and the brakes in the ratio 2: 1 are executed. Furthermore, there are no fixed housing couplings. Finally, two switching elements to be switched at the same time are arranged.
  • a hydrodynamic torque converter As a starting element for the transmission 1, a hydrodynamic torque converter, a hydrodynamic clutch, an additional starting clutch, an integrated starting clutch or brake and / or an additional electric machine can be arranged. On each of the six shafts W1 to W6, an electric machine or other power / power source can be arranged. Moreover, on each of the shafts W1 to W6 or each link, a freewheel may be arranged to the housing G or to another shaft W1, W2, W3, W4, W5, W6.
  • the transmission 1 can preferably be installed in standard drive construction or in front / transverse design in a motor vehicle. As switching elements frictional and / or positive switching elements are possible.
  • the first brake B1, the first clutch K1 and the clutch K4 can be designed as positive locking, in particular as claw switching elements, which leads to significant fuel consumption advantages of a provided with the transmission motor vehicle with internal combustion engine.
  • the present invention has the advantage that a low construction cost for the transmission is required, which results in lower manufacturing costs and lower weight of the transmission.
  • a good gear ratio, low absolute and relative speeds such as low planetary gearset and shift element torques.
  • the present invention provides good gearing efficiencies and a very good accessibility of all switching elements, in particular for their maintenance.
  • the geometrical position / sequence of the individual planetary gear sets GP1, GP2, GP3, GP4 and the individual switching elements K1, K2, K3, K4, B1, B2 can be chosen freely taking into account the bondability of the respective transmission elements.
  • Individual transmission elements can be moved as desired in their position within the transmission 1.

Landscapes

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

Abstract

L'invention concerne une boîte de vitesses, en particulier une boîte de vitesses à plusieurs rapports destinée à un véhicule automobile. Ladite boîte de vitesses comprend un carter, un arbre d'entrée, un arbre de sortie, au moins quatre trains planétaires, les trains planétaires comprenant chacun un pignon planétaire, un satellite, un porte-satellite et une couronne. La boîte de vitesses comprend également plusieurs éléments de changement de vitesse sous la forme d'au moins quatre embrayages et d'au moins deux freins. L'arbre d'entrée peut être relié par l'intermédiaire du deuxième embrayage au porte-satellite du troisième train planétaire et au porte-satellite du quatrième train planétaire. Le premier frein est relié à la couronne du premier train planétaire et au porte-satellite du deuxième train planétaire. Le deuxième frein est relié au pignon planétaire du premier train planétaire. Et le porte-satellite du premier train planétaire est relié au pignon satellite du quatrième train planétaire.
EP14706579.1A 2013-03-27 2014-02-25 Boîte de vitesses destinée à un véhicule automobile Withdrawn EP2979004A1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102013205379.7A DE102013205379A1 (de) 2013-03-27 2013-03-27 Getriebe für ein Kraftfahrzeug
PCT/EP2014/053595 WO2014154421A1 (fr) 2013-03-27 2014-02-25 Boîte de vitesses destinée à un véhicule automobile

Publications (1)

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EP2979004A1 true EP2979004A1 (fr) 2016-02-03

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EP14706579.1A Withdrawn EP2979004A1 (fr) 2013-03-27 2014-02-25 Boîte de vitesses destinée à un véhicule automobile

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US (1) US20160053869A1 (fr)
EP (1) EP2979004A1 (fr)
JP (1) JP2016514813A (fr)
CN (1) CN105051417A (fr)
DE (1) DE102013205379A1 (fr)
WO (1) WO2014154421A1 (fr)

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Also Published As

Publication number Publication date
JP2016514813A (ja) 2016-05-23
US20160053869A1 (en) 2016-02-25
CN105051417A (zh) 2015-11-11
DE102013205379A1 (de) 2014-10-02
WO2014154421A1 (fr) 2014-10-02

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