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EP2979000A1 - Boîte de vitesses destinée à un véhicule automobile - Google Patents

Boîte de vitesses destinée à un véhicule automobile

Info

Publication number
EP2979000A1
EP2979000A1 EP14706572.6A EP14706572A EP2979000A1 EP 2979000 A1 EP2979000 A1 EP 2979000A1 EP 14706572 A EP14706572 A EP 14706572A EP 2979000 A1 EP2979000 A1 EP 2979000A1
Authority
EP
European Patent Office
Prior art keywords
clutch
closed
planetary gear
open
brake
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Withdrawn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
EP14706572.6A
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 EP2979000A1 publication Critical patent/EP2979000A1/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Withdrawn legal-status Critical Current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
    • F16H3/666—Gearings having three or more central gears composed of a number of gear trains without drive passing from one train to another with compound planetary gear units, e.g. two intermeshing 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
    • F16H3/00—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion
    • F16H3/44—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion using gears having orbital motion
    • F16H2003/445—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion using gears having orbital motion without permanent connection between the input and the set of orbital gears
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H2200/00—Transmissions for multiple ratios
    • F16H2200/003—Transmissions for multiple ratios characterised by the number of forward speeds
    • F16H2200/0065—Transmissions for multiple ratios characterised by the number of forward speeds the gear ratios comprising nine forward speeds
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H2200/00—Transmissions for multiple ratios
    • F16H2200/20—Transmissions using gears with orbital motion
    • F16H2200/2002—Transmissions using gears with orbital motion characterised by the number of sets of orbital gears
    • F16H2200/2012—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
    • 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
    • F16H2200/2097—Transmissions using gears with orbital motion comprising an orbital gear set member permanently connected to the housing, e.g. a sun wheel permanently connected to the housing

Definitions

  • the invention relates to a transmission, in particular multi-speed transmission, 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, at least one planet, a planet carrier and a ring gear, and a plurality of switching elements in shape of at least four clutches and at least two brakes.
  • WO 2012/052284 A1 a Mehrgenget ebe is shown with six forward gears and one reverse gear, which comprises four planetary gear sets, seven rotatable shafts and five switching elements, wherein the sun gear of the first planetary gear set is connected to the sixth shaft, via a first brake on 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 Connected to the sun gear of the third planetary gear set and releasably connected via a coupling with the connected to the web of the third planetary gear and the ring gear of the fourth planetary gear seventh shaft, 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
  • the disadvantage here is that internal 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 again is that the switching elements, especially the couplings are difficult to access, especially when good Verzah- tion efficiency and low component loads at low construction costs are sought.
  • 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 multi-speed transmission, for a motor vehicle comprising a housing, a drive shaft, an output shaft, at least four planetary gear sets, wherein the planetary gear sets each comprise a sun gear, at least one 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 to the sun gear of the first and second planetary gear set is connectable and the sun gear of the fourth planetary gear set is connected to the housing and that the ring gear of the fourth planetary gear set is connected to the planet carrier of the second planetary gear set and the planet carrier of the fourth planetary gear set via the fourth clutch to the output shaft and the ring gear of the second planetary gear set is connected via the second brake to the housing and the drive shaft üb the third clutch is connectable to the first brake and the first brake is connected to the housing.
  • 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 to 7.
  • the invention also achieves the objects with a method for operating a transmission, in particular according to one of claims 1-7, with two brakes and four clutches, characterized in that a first gear by means of open first brake, closed second brake, open first clutch, closed second Is formed by open first brake, closed second brake, open first clutch, open second clutch, closed third clutch and closed fourth clutch, and that a third gear by means of open first brake, open second brake, open first clutch, closed second clutch, closed third clutch and closed fourth clutch is formed, and that a fourth gear by means of open first brake, open second brake, closed first clutch, closed second clutch, third open Clutch and closed fourth clutch is formed or by closed first brake, open second brake, closed first clutch, open second clutch, third open clutch and closed fourth clutch or by means of open first brake, closed second brake, closed ner first clutch, open second clutch, third open clutch and closed fourth clutch or by means of open first brake, open second brake, closed first clutch, open second clutch, closed third clutch and closed fourth clutch is formed, and that a fifth gear by means
  • 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 in particular referred to as interconnected when between the elements a solid, in particular rotationally fixed connection consists. 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.
  • a coupling is preferably to be understood in the description, in particular in the claims, as a switching element which, depending on the actuation state, permits a relative movement between two components or a connection. represents binding for the transmission of 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 includes a sun gear, a planet carrier respectively
  • Bridge and a ring gear are rotatably mounted on the planet carrier respectively web Planetary gears or planets, which mesh with the teeth 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 operable, whereby different gears can be realized by different ratios between the drive shaft and the output shaft.
  • the higher the number of gears the finer a gear ratio can be realized at a large transmission spread and thus, for example, an internal combustion engine of a motor vehicle in an optimal speed range and thus be operated as economically as possible.
  • 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.
  • 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 first planetary gear set is a minus planetary gear and the drive shaft is connected via the third clutch to the planet carrier of the first planetary gear set and the ring gear of the first planetary gear set is connected to the planet carrier of the second planetary gear set.
  • the drive shaft can be flexibly connected to the first planetary gear as needed and via the first planetary gear also with the second planetary gear set.
  • the first planetary gear set is a positive planetary gear set and the drive shaft is connected via the third clutch to the ring gear of the first planetary gear set.
  • wheel set connectable and the planet carrier of the first planetary gear set is connected to the planet carrier of the second planetary gear set.
  • the drive shaft can be flexibly connected - so as needed - with the first planetary gear and via the first planetary gear also with the second planetary gear.
  • a positive planetary gear set further offers the advantage that, when the planet carrier is stationary, the ring gear and the sun gear rotate in the same direction of rotation.
  • the drive shaft via the first clutch with the planet carrier of the third planetary gear set is connectable and the sun gear of the third planetary gear set is connected to the ring gear of the fourth planetary, with the planet carrier of the second planetary gear set and with the ring gear of the first planetary gear set and the ring gear of the third planetary gear set connected to the output shaft.
  • the transmission structure is simplified because the four planetary gear sets are interconnected.
  • the ring gear of the third planetary gear set via the first clutch to the output shaft is connected and the drive shaft is connected to the planet carrier of the third planetary gear set and the sun gear of the third planetary gear set is connected to the planet carrier of the second planetary gear set and the ring gear of the fourth planetary gear set.
  • force and torque can be transmitted in a flexible manner from the third planetary gear directly to the output shaft and indirectly from the second planetary gear and the fourth planetary gear via the third planetary gear on this.
  • the sun gear of the third planetary gear set via the first clutch with the planet carrier of the second planetary gear set and with the ring gear of the fourth planetary gear set is connectable.
  • the third planetary gear set can be connected in a flexible manner, in particular with two directly adjacent planetary gear sets.
  • 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
  • 6 shows a transmission according to a fifth embodiment of the present invention
  • 7 shows a transmission according to a sixth embodiment of the present invention
  • Fig. 8 shows a transmission according to a seventh 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 for transmitting power and torques via shafts and / or planetary gear sets.
  • the first clutch K1, the second clutch K2 and the third clutch K3 are connected to the drive shaft ANW on the drive side.
  • the first clutch K1 is further connected to a 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 transmission 1 further four planetary gear sets GP1, GP2, GP3, GP4 and five waves W1, W2, W3, W4 and W5 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 at least one planet 1 1 1, 1 12, 1 13, 1 14 for transmission of force and torque interacts.
  • the planet 1 1 1, 1 12, 1 13, 1 14 is at one Bridge / planet carrier 121, 122, 123, 124 rotatably mounted.
  • 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 with the web 123 of the third planetary GP3.
  • the second shaft W2 connects the second clutch K2 with the sun gears 101, 102 of the first planetary gearset GP1 and the second planetary gearset GP2.
  • the third shaft W3 connects the third clutch K3 on the one hand via the brake B1 with the housing G, on the other hand, the third wave W3 is connected to the web 121 of the first planetary gearset GP1.
  • the fourth wave W4 is connected on the one hand to the sun gear 104 of the fourth planetary gear set GP4, on the other hand fixed to the housing G.
  • the fifth shaft W5 connects the ring gear 131 of the first planetary gear set GP1, the land 122 of the second planetary gear set GP2, the sun gear 103 of the third planetary gear set GP3, and the ring gear 134 of the fourth planetary gear set GP4.
  • the ring gear 132 of the second planetary gear set GP2 can be coupled to the housing G via a second brake B2.
  • the drive shaft ANW is connected to the clutches K1, K2, K3.
  • the output shaft AW is on the one hand connected to the ring gear 133 of the third planetary GP3 and coupled via the fourth clutch K4 with the web 124 of the fourth planetary GP4.
  • 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.
  • the released in the switching matrix entries so for example in the forward gear V1 in the first brake B1 and the first clutch K1 and the third clutch K3 indicate that the corresponding switching element or the brakes and the clutch is open, ie that the switching element in this case transmits no forces or no torque from the connected to the switching element or connected to this particular waves or elements of the transmission.
  • 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 B2 and of the clutches K2 and K4.
  • the gear ratio i is 4.333.
  • the gear ratio i is 2.586.
  • the gear ratio i is 0.496.
  • the clutches K2 and K4 and the brake B1 are closed.
  • the transmission ratio i is -3.1 67.
  • the brake B1 and the clutches K1 and K4 are closed.
  • the gear ratio i is 1, 267.
  • the brake B2 and the clutches K1 and K4 are closed.
  • the gear ratio i is 1, 267.
  • all the brakes B1, B2 are opened and the clutches K1, K3 and K4 are closed, and the transmission ratio i is 1.267.
  • the gear gap ⁇ between the first forward speed V1 and the second forward speed V2 is 1, 675, between the second forward speed V2 and the third forward speed V3 1, 552.
  • the gear gap ⁇ between the third forward gear V3 and the fourth forward gear V4 is 1, 31 6, between the fourth forward gear V4 and the fifth forward gear V5 1, 267th
  • the gear shift ⁇ between the fifth forward gear V5 and the sixth forward gear V6 is 1, 237, between the sixth forward speed V6 and the seventh forward speed V7 1, 140.
  • the gear gap ⁇ between the seventh forward gear V7 and the eighth forward gear V8 is 1, 182, between the eighth forward gear V8 and the ninth forward gear V9 1, 210.
  • the total jump is 8.741.
  • the first planetary gear set GP1 has a stand translation
  • Fig. 3 shows a transmission according to a second embodiment of the present invention.
  • a transmission 1 according to FIG. 1 is shown substantially.
  • the first planetary gear set GP1 is designed as a Ravigneaux planetary gearset.
  • the first planetary gear set GP1 therefore has two planets 1 1 1 a, 1 1 1 b, which are rotatably mounted together on the web 121 of the first planetary gear set GP1 and mesh with each other.
  • the third shaft W3 is now connected to the ring gear 131 of the first planetary gear set GP1 instead of the web 121 of the first planetary gear set GP1.
  • the fifth wave W5 in the transmission 1 according to FIG. 3 continues in contrast to the transmission 1 according to FIG 1, the web 121 of the first planetary gear set GP1, the land 122 of the second planetary gear set GP2, the sun gear 103 of the third planetary gear set GP3, and the ring gear 134 of the fourth planetary gear set GP4. Due to the formation of the first planetary GP1
  • the second wave W2 also cooperate only with one of the two sun gears 101, 102 of the first and second planetary gear set GP1, GP2.
  • FIG. 4 shows a transmission according to a third embodiment of the present invention. 4, a transmission 1 according to FIG. 1 is shown. 4 shows two alternative positions A, B for the first clutch K1, in which the first clutch K1 can be arranged to have the same effect as the position according to FIG.
  • the first alternative position A for the first clutch K1 is located between the ring gear of the third planetary GP3 and the portion of the output shaft AW, which is connected to the fourth clutch K4.
  • the second alternative position B for the first clutch K1 is located between the sun gear 103 of the third planetary GP3 and the section of the fifth shaft W5, which the ring gear 131 of the first planetary GP1, the web 122 of the second planetary GP3 and the ring gear 134 of the fourth Planetary gear GP4 connects with each other.
  • 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 first clutch K1 now designated by reference symbol K1 ', is arranged at the first alternative position A according to FIG.
  • the first wave W1 is omitted.
  • the drive shaft ANW is thus directly connected to the web 123 of the third planetary GP3.
  • Fig. 6 shows a transmission according to a fifth embodiment of the present invention.
  • FIG. 6 essentially shows a transmission 1 according to FIG. 3.
  • the first clutch K1 now denoted by reference symbol K1 ', is arranged at the first alternative position A according to FIG. 4 or FIG. 5.
  • the first wave W1 is omitted.
  • the drive shaft ANW is thus directly connected to the web 123 of the third planetary GP3.
  • Fig. 7 shows a transmission according to a sixth embodiment of the present invention.
  • a transmission 1 according to FIG. 1 is shown substantially.
  • the first clutch K1 now denoted by reference symbol K1 ", at the second alternative position B shown in Fig. 4.
  • the first shaft W1 is omitted ANW is thus directly connected to the web 123 of the third planetary GP3.
  • Fig. 8 shows a transmission according to a seventh embodiment of the present invention.
  • a transmission 1 according to FIG. 3 is shown substantially.
  • the first clutch K1 here denoted by reference symbol K1 "
  • the drive shaft ANW is thus directly connected to the web 123 of the third planetary gearset GP3.
  • the transmission 1 comprises four planetary gear sets GP1, GP2, GP3, GP4, six shift elements B1, B2, K1, K2, K3, K4 wherein the shift elements are in the form of at least four clutches and at least two brakes , Furthermore, there is a fixed housing coupling. Finally, two switching elements to be switched at the same time are arranged.
  • 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.
  • an electric machine or other power / power source can be arranged on each of the five shafts W1 to W5, an electric machine or other power / power source can be arranged.
  • a freewheel can be arranged to the housing G or to another shaft W1, W2, W3, W4, W5.
  • the transmission 1 may preferably in standard drive design or in front / transverse design in a Motor vehicle be installed.
  • the fourth clutch K4 can be designed as a form-fitting, in particular as a claw switching element, which leads to significant consumption advantages of a provided with the transmission motor vehicle with internal combustion engine.
  • the transmission offers a total of at least nine forward gears and at least one reverse gear.
  • 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.
  • the transmission offers a good gear ratio, low absolute and relative speeds and low planetary gear and switching element moments.
  • 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, K1 ', K1 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.

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

Abstract

L'invention concerne une boîte de vitesses, 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, au moins 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 pignon planétaire du premier et du deuxième train planétaire, le pignon planétaire du quatrième train planétaire est relié au carter. La couronne du quatrième train planétaire peut être reliée au porte-satellite du deuxième train planétaire et le porte-satellite du quatrième train planétaire peut être relié à l'arbre de sortie par l'intermédiaire du quatrième embrayage. La couronne du deuxième train planétaire est reliée au carter par l'intermédiaire du deuxième frein. L'arbre d'entrée peut être relié au premier frein par l'intermédiaire du troisième embrayage. Le premier frein est relié au carter. L'invention concerne également un procédé permettant de faire fonctionner une boîte de vitesses, ainsi qu'un véhicule automobile équipé d'une boîte de vitesses.
EP14706572.6A 2013-03-27 2014-02-25 Boîte de vitesses destinée à un véhicule automobile Withdrawn EP2979000A1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102013205383.5A DE102013205383A1 (de) 2013-03-27 2013-03-27 Getriebe für ein Kraftfahrzeug
PCT/EP2014/053581 WO2014154415A1 (fr) 2013-03-27 2014-02-25 Boîte de vitesses destinée à un véhicule automobile

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EP2979000A1 true EP2979000A1 (fr) 2016-02-03

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US (1) US9562589B2 (fr)
EP (1) EP2979000A1 (fr)
JP (1) JP6346660B2 (fr)
CN (1) CN105051416B (fr)
DE (1) DE102013205383A1 (fr)
WO (1) WO2014154415A1 (fr)

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CN105051416A (zh) 2015-11-11
US20160084356A1 (en) 2016-03-24
US9562589B2 (en) 2017-02-07
WO2014154415A1 (fr) 2014-10-02
CN105051416B (zh) 2017-04-19
DE102013205383A1 (de) 2014-10-02
JP2016517933A (ja) 2016-06-20
JP6346660B2 (ja) 2018-06-20

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