EP2906856A1 - Boîte de vitesses à plusieurs étages - Google Patents

Boîte de vitesses à plusieurs étages

Info

Publication number
EP2906856A1
EP2906856A1 EP13756488.6A EP13756488A EP2906856A1 EP 2906856 A1 EP2906856 A1 EP 2906856A1 EP 13756488 A EP13756488 A EP 13756488A EP 2906856 A1 EP2906856 A1 EP 2906856A1
Authority
EP
European Patent Office
Prior art keywords
planetary gear
clutch
brake
shaft
closing
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Withdrawn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
EP13756488.6A
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 EP2906856A1 publication Critical patent/EP2906856A1/fr
Withdrawn legal-status Critical Current

Links

Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H3/00—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion
    • F16H3/44—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion using gears having orbital motion
    • F16H3/62—Gearings having three or more central gears
    • F16H3/66—Gearings having three or more central gears composed of a number of gear trains without drive passing from one train to another
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H2200/00—Transmissions for multiple ratios
    • F16H2200/003—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
    • F16H2200/2094—Transmissions using gears with orbital motion using positive clutches, e.g. dog clutches

Definitions

  • the present invention relates to a planetary gear multi-speed transmission, in particular an automatic transmission for a motor vehicle, according to the preamble of patent claim 1.
  • Automatic transmissions particularly for motor vehicles, include, in the prior art, planetary gear sets that are switched by means of friction elements, such as clutches and brakes, and usually with a slip element and optionally a lockup clutch, such as a hydrodynamic torque converter or a fluid coupling connected.
  • friction elements such as clutches and brakes
  • slip element such as clutches and brakes
  • lockup clutch such as a hydrodynamic torque converter or a fluid coupling connected.
  • Such an automatic transmission is known for example from DE 199 12 480 B4 of the Applicant. It comprises three single planetary gear sets and three brakes and two clutches for shifting six forward gears and one reverse gear, a drive shaft and an output shaft, wherein the web of the first planetary gear set with the ring gear of the second planetary gear set and the bridge of the second planetary gear set with the ring gear of the third Planetenradsatzes is constantly connected and the drive shaft is connected directly to the sun gear of the second planetary gear set.
  • the drive shaft via the first clutch to the sun gear of the first planetary gear and the second clutch to the web of the first planetary gear set is connectable, wherein the sun gear of the first planetary gear set via the first brake with a housing of the transmission is connectable and the web of the first planetary gear set via the second brake to the housing of the transmission is connectable, wherein the sun gear of the third planetary gear set via the third brake to the housing of the transmission is connectable.
  • the output shaft of the transmission is permanently connected to the web of the third planetary gear set and the ring gear of the first planetary gear set.
  • a 9-speed multi-speed transmission known; it comprises eight switching elements and four planetary gear sets, one planetary gear set serving as a primary gear and the main gear has a Simpson set and another serving as a reverse gear planetary gear.
  • a planetary gear multi-speed transmission which has a drive and an output, which are arranged in a housing.
  • the known transmission at least four planetary gear sets, hereinafter referred to as the first, second, third and fourth planetary gear set, at least eight rotatable shafts - hereinafter referred to as drive shaft, output shaft, third, fourth, fifth, sixth, seventh and eighth shaft - and at least six switching elements, comprising brakes and clutches, provided, the selective engagement causes different ratios between the drive and the output, so that preferably nine forward gears and one reverse gear can be realized.
  • the first and the second planetary gear set which are preferably designed as negative planetary gear sets, that is to say with a negative stationary gear ratio, form a shiftable transfer gearset, the third and the fourth planetary gear set forming a main gearset.
  • the webs of the first and the second planetary gear sets are coupled to one another via the fourth shaft.
  • pelt are connected to an element of the main gearset that the ring gear of the first planetary gear set is coupled to the sun gear of the second planetary gear via the eighth shaft, which is releasably connectable via a first clutch to the drive shaft and that the sun gear of the first planetary gear set the third shaft via a first brake to a housing of the transmission is coupled and releasably connectable via a second clutch to the drive shaft, wherein the ring gear of the second planetary gear set by means of the fifth shaft via a second brake to a housing of the transmission can be coupled.
  • the seventh shaft with at least one element of the main gearset is constantly connected and coupled via a third brake to the housing of the transmission
  • the sixth shaft is continuously connected to at least one further element of the main gear and releasably connected via a third clutch to the drive shaft
  • the output shaft is permanently connected to at least one further element of the main gearset.
  • the fourth shaft is constantly connected to the ring gear of the third planetary gear set, wherein the sixth shaft is continuously connected to the ring gear of the fourth planetary gear set and the web of the third planetary gear and releasably connectable via the third clutch to the drive shaft.
  • the seventh shaft is constantly connected to the sun gears of the third and fourth planetary gear set and can be coupled via the third brake to a housing of the transmission. The output takes place here via the output shaft permanently connected to the web of the fourth planetary gear set.
  • the third and the fourth planetary gear set may be combined or reduced to form a Ravigneaux set having a common web and a common ring gear.
  • the switching elements of such executed multi-step transmission which are usually designed as multi-plate clutches or brakes, hydraulically operated, which have disadvantageously high hydraulic losses.
  • the use of demand-actuated switching elements would be particularly advantageous.
  • switching elements in particular switching elements are understood, which consume no or only less energy to maintain their circuit state, as in the change of the switching state.
  • the switching elements in particular the clutches should be easily accessible from the outside.
  • the present invention has for its object to propose a multi-speed transmission of the type mentioned, which has nine forward gears and one reverse gear with sufficient translation, in which the construction cost, component load and size are optimized and also the efficiency is improved. Furthermore, the switching elements of the transmission should be easily accessible from the outside, whereby the installation of demand-actuated switching elements is made possible. In addition, the transmission should be suitable for both a standard and a front-transverse construction.
  • a multi-speed transmission according to the invention in planetary design which has a drive and an output, and is arranged in a housing. Furthermore, at least four planetary gear sets, hereinafter referred to as the first, second, third and fourth planetary, eight rotatable shafts - hereinafter referred to as drive shaft, output shaft, third, fourth, fifth, sixth, seventh and eighth shaft - and six preferably as a slat - Lenschaltiano or designed as a form-locking switching elements switching elements comprising brakes and clutches, provided, the selective intervention causes different ratios between the drive and the output, so that preferably nine forward gears and one reverse gear can be realized.
  • the planetary gear sets of the transmission are preferably designed as negative planetary gear sets.
  • the ring gear at a fixed web on a sun gear opposite direction of rotation.
  • a simple plus planetary gear includes a sun gear, a ring gear and a web on which inner and outer planetary gears are rotatably mounted, wherein all inner planetary gears mesh with the sun gear and all outer planetary gears with the ring gear, each inner planetary gear each having an outer Planet wheel meshes.
  • the ring gear has the same direction of rotation when the web is held on as the sun gear and there is a positive stationary gear ratio.
  • the sun gear of the first planetary gear set is connected to the fifth shaft, which is releasably connectable via a first clutch to the drive shaft and can be coupled via a third brake to the housing, wherein the drive shaft via a second clutch with the the seventh shaft connected to the web of the fourth planetary gear set and the ring gear of the third planetary gear set is detachably connectable, and wherein the drive shaft is connected to the sun gear of the second planetary gear set.
  • the sixth shaft is connected to the ring gear of the first planetary gear set, the bridge of the second planetary gear set and the ring gear of the fourth planetary gear set, wherein the third shaft is connected to the sun gear of the third planetary gear set and the sun gear of the fourth planetary gear set and to a first brake Housing can be coupled.
  • the fourth shaft is connected to the web of the first planetary gear set, coupled via a second brake to the housing and releasably connectable via a third clutch to the eighth shaft connected to the ring gear of the second planetary gear set, wherein the output shaft of the transmission with the web of the third Planetary gear set is connected.
  • the sun gear of the first planetary gear is connected to the fifth shaft, which is releasably connectable via a first clutch to the drive shaft and can be coupled via a third brake to the housing, wherein the drive shaft via a second clutch with the connected to the web of the fourth planetary gear set and the ring gear of the third planetary gear set seventh shaft is releasably connectable and wherein the drive shaft is connected to the sun gear of the second planetary gear set.
  • the sixth shaft is connected to the ring gear of the first planetary gear set and the ring gear of the fourth planetary gear set and releasably connectable via a third clutch with the eighth shaft connected to the web of the second planetary gear set, wherein the third shaft with the sun gear of the third planetary gear set and the Sun gear of the fourth planetary gear set and coupled via a first brake to the housing can be coupled.
  • the fourth shaft is connected to the web of the first planetary gear set and the ring gear of the second planetary gear set and coupled via a second brake to the housing, wherein the output shaft of the transmission is connected to the web of the third planetary gear set.
  • switching elements of the transmission can be used as u.a. be executed hydraulically actuated switching elements.
  • the construction cost is significantly reduced with the multi-stage transmission according to the invention by a small number of switching elements.
  • a switching element which is actuated in the first forward gear and in reverse is suitable.
  • the transmission according to the invention is designed such that an adaptability to different drive train configurations is made possible both in the power flow direction as well as in space.
  • Figure 1 is a schematic view of a preferred embodiment of a multi-speed transmission according to the invention.
  • FIG. 2 shows an exemplary circuit diagram for a multistage transmission according to FIG. 1;
  • Figure 3 is a schematic view of another preferred embodiment of a multi-speed transmission according to the invention.
  • FIG. 4 shows an exemplary circuit diagram for a multistage transmission according to FIG. 3.
  • FIG. 1 shows a multi-speed transmission according to the invention with a drive shaft 1, an output shaft 2 and four planetary gear sets P1, P2, P3 and P4, which are arranged in a housing G.
  • the planetary gear sets P1, P2, P3, P4 are formed in the example shown in Figure 1 as negative planetary gear sets.
  • at least one of the planetary gear sets P1, P2, P3, P4 can be designed as a positive planetary gear set, if at the same time the web and Hohlradanulation exchanged and the amount of the stationary gear ratio is increased by 1 compared to the design as a minus planetary gear.
  • the planetary gear sets P1, P2, P3, P4 axially arranged in the order of the first planetary gear set P1, second planetary gear set P2, third planetary gear set P3, fourth planetary gear set P4.
  • the axial order of the individual planetary gear sets and the arrangement of the switching elements are freely selectable, as long as it allows the binding of the elements.
  • switching elements namely three brakes 03, 04, 05 and three clutches 15, 17, 48 are provided.
  • the spatial arrangement of the switching elements can be arbitrary and is limited only by the dimensions and the external shape.
  • the clutches and the brakes of the transmission are preferably designed as Reibschaltemia or lamellar switching elements, but can also be designed as a form-locking switching elements.
  • the multistage transmission according to the invention has a total of eight rotatable shafts, namely the shafts 1, 2, 3, 4, 5, 6, 7 and 8, wherein the drive shaft, the first shaft 1 and the output shaft, the second shaft 2 of the transmission.
  • the sun gear of the first planetary gear P1 is connected to the fifth shaft 5, which is detachably connected via a first clutch 15 to the drive shaft 1 and can be coupled via a third brake 05 to the housing G.
  • the drive shaft 1 is releasably connectable via a second clutch 17 to the seventh shaft 7 connected to the web of the fourth planetary gear set P4 and the ring gear of the third planetary gear set P3 and is connected to the sun gear of the second planetary gear set P2.
  • the sixth shaft 6 is connected to the ring gear of the first planetary gear set P1, the bridge of the second planetary gear P2 and the ring gear of the fourth planetary gear set P4, wherein the third shaft 3 with the sun gear of the third planetary gear P3 and the sun gear of the fourth Planetary gear P4 connected and can be coupled via a first brake 03 to the housing G.
  • the fourth shaft 4 is connected to the web of the first planetary gear set P1, via a second brake 04 can be coupled to the housing G and via a third clutch 48 with the connected to the ring gear of the second planetary gear P2 eighth shaft 8 detachably connected, wherein the output shaft 2 of the transmission is connected to the web of the third planetary gear P3.
  • the first and second coupling 15, 17 arranged axially adjacent to each other and designed as a lamellae switching elements and have a common Au .lamellenlasi.
  • the first brake 03 is suitable for execution as a claw switching element, whereby the consumption is significantly improved.
  • FIG. 2 shows an exemplary circuit diagram of a multi-stage mold according to FIG.
  • the shift pattern can be used to calculate the respective gear ratios i of the individual gear steps. fen and the step to be determined therefrom or increments ⁇ are taken to the next higher gear example, the value 9.01 6 represents the spread of the transmission.
  • the values for the stationary gear ratios of the planetary gear sets P1, P2, P3, P4 designed as minus planetary gear sets are -2.366, -1, 600, -3.189 and -2.763 in the example shown. From Figure 2 it is seen that in sequential switching mode only one switching element switched on and a switching element must be switched off because two adjacent gear stages use two switching elements together. Furthermore, it will be seen that a large spreading is achieved with small gear jumps.
  • the first forward gear is obtained by closing the first and second brakes 03, 04 and the third clutch 48, the second forward gear by closing the first and third brakes 03, 05 and the third clutch 48, the third forward gear by Closing the first brake 03 and the first and third clutches 15, 48, the fourth forward gear by closing the first brake 03 and the second and third clutches 17, 48, which in the example shown as a direct gear fifth forward gear by closing the first, second and third clutches 15, 17, 48, the sixth forward gear by closing the third brake 05 and the second and third clutches 17, 48, the seventh forward gear by closing the second brake 04 and the second and third Clutch 17, 48, the eighth forward gear by closing the second and third brakes 04, 05 and the second clutch 17 and the ninth forward speed is obtained by closing the second Bre mse 04 and the first and second clutches 15, 17, wherein the reverse gear by closing the first and second brake 03, 04 and the first clutch 15 results.
  • the fourth forward gear can be switched by further switching combinations, which are designated in Figure 2 with M. Accordingly, the fourth forward speed can be achieved by closing the first and second brakes 03, 04 and the second clutch 17 or by closing the first brake 03 and the first and second clutches 15, 17 or by closing the first and third brakes 03, 05 and the second coupling 17 result. Characterized in that in the first forward gear and / or in reverse, the first and second brake 03, 04, the first and third clutch 1 5, 48 are closed, these switching elements can be used as starting elements.
  • the object of FIG. 3 is an embodiment which differs from the embodiment according to FIG. 1 in that the third clutch 48 is dispensed with and replaced by a fourth clutch 68 which connects the sixth shaft 6 to the web in the example according to FIG the second planetary gear set P2 connected eighth shaft 8 releasably connects. Further, the fourth shaft 4 is connected to the web of the first planetary gear P1 and the ring gear of the second planetary gear set P2; in the embodiment of Figure 1, the fourth shaft 4 is connected only to the web of the first planetary gear set P1.
  • circuit diagram corresponding to the embodiment according to FIG. 3 is the subject of FIG. 4. It corresponds to the circuit diagram shown in FIG. 2 with the difference that the third clutch 48 is replaced by the fourth clutch 68.
  • an axle differential and / or a distributor differential can be arranged on the drive side or on the output side.
  • the drive shaft 1 can be separated by a coupling element of a drive motor as needed, as a coupling element, a hydrodynamic converter, a hydraulic clutch, a dry starting clutch, a wet starting clutch, a magnetic powder clutch or a centrifugal clutch or the like used are. It is also possible to arrange such a starting element in the power flow direction behind the transmission, in which case the drive shaft 1 is constantly connected to the crankshaft of the drive motor.
  • the multistage transmission according to the invention also allows the arrangement of a torsional vibration damper between the drive motor and transmission.
  • a wear-free brake such. a hydraulic or electric retarder or the like, be arranged, which is particularly important for use in commercial vehicles of particular importance.
  • a power take-off may be provided to drive additional units on each shaft, preferably on the drive shaft 1 or the output shaft 2.
  • the friction shift elements used can be designed as power shift clutches or brakes.
  • non-positive clutches or brakes such as e.g. Multi-plate clutches, band brakes and / or cone clutches are used.
  • Another advantage of the multistage transmission presented here is that an electric machine can be mounted on each shaft as a generator and / or as an additional drive machine.

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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 à plusieurs étages qui comprend quatre ensembles de roues planétaires (P1, P2, P3, P4), huit arbres rotatifs (1, 2, 3, 4, 5, 6, 7, 8) et six éléments de commutation (03, 04, 05, 15, 17, 48). La roue solaire du premier ensemble de roues planétaires (P1) est reliée au cinquième arbre (5), qui peut être relié à l'arbre d'entraînement (1) par un premier accouplement (15) et qui peut être couplé au boîtier (G) par un troisième frein (05). L'arbre d'entraînement (1) peut être relié par un deuxième accouplement (17) au septième arbre (7), qui est relié au support du quatrième ensemble de roues planétaires (P4) et à la couronne à denture intérieure du troisième ensemble de roues planétaires (P3), et qui est relié à la roue solaire du deuxième ensemble de roues planétaires (P2). Ledit sixième arbre (6) est relié à la couronne à denture intérieure du premier ensemble de roues planétaires (P1 ), au support du deuxième ensemble de roues planétaires (P2) et à la couronne à denture intérieure du quatrième ensemble de roues planétaires (P4) et le troisième arbre (3) est relié à la roue solaire du troisième ensemble de roues planétaires (P3) et à la roue solaire du quatrième ensemble de roues planétaire (P4) et il peut être couplé au boîtier (G) par un premier frein (03). Le quatrième arbre (4) est relié au support du premier ensemble de roues planétaires (P1), il peut être couplé au boîtier (G) par un second frein (04) et il est relié par un troisième accouplement (48) au huitième arbre (8), qui est relié à la couronne à denture intérieure du deuxième ensemble de roues planétaires (P2). L'arbre de sortie (2) de la boîte de vitesses est relié au support du troisième ensemble de roues planétaires (P3).
EP13756488.6A 2012-10-15 2013-09-04 Boîte de vitesses à plusieurs étages Withdrawn EP2906856A1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102012218687.5A DE102012218687B4 (de) 2012-10-15 2012-10-15 Mehrstufengetriebe
PCT/EP2013/068234 WO2014060141A1 (fr) 2012-10-15 2013-09-04 Boîte de vitesses à plusieurs étages

Publications (1)

Publication Number Publication Date
EP2906856A1 true EP2906856A1 (fr) 2015-08-19

Family

ID=49111203

Family Applications (1)

Application Number Title Priority Date Filing Date
EP13756488.6A Withdrawn EP2906856A1 (fr) 2012-10-15 2013-09-04 Boîte de vitesses à plusieurs étages

Country Status (5)

Country Link
US (1) US9377086B2 (fr)
EP (1) EP2906856A1 (fr)
CN (1) CN104718399B (fr)
DE (1) DE102012218687B4 (fr)
WO (1) WO2014060141A1 (fr)

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CN104718399A (zh) 2015-06-17
US9377086B2 (en) 2016-06-28
US20150267782A1 (en) 2015-09-24
CN104718399B (zh) 2017-04-19
DE102012218687A1 (de) 2014-04-17
WO2014060141A1 (fr) 2014-04-24
DE102012218687B4 (de) 2021-09-30

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