EP3011200A1 - Boîte de vitesses à plusieurs étages pour véhicule automobile - Google Patents

Boîte de vitesses à plusieurs étages pour véhicule automobile

Info

Publication number
EP3011200A1
EP3011200A1 EP14730753.2A EP14730753A EP3011200A1 EP 3011200 A1 EP3011200 A1 EP 3011200A1 EP 14730753 A EP14730753 A EP 14730753A EP 3011200 A1 EP3011200 A1 EP 3011200A1
Authority
EP
European Patent Office
Prior art keywords
unit
switching unit
planetary gear
combined
actuating
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Withdrawn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
EP14730753.2A
Other languages
German (de)
English (en)
Inventor
Tobias Schilder
Klaus Riedl
Jürgen Schweitzer
Tobias Härter
Thomas Kull
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.)
Mercedes Benz Group AG
Original Assignee
Daimler 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 Daimler AG filed Critical Daimler AG
Publication of EP3011200A1 publication Critical patent/EP3011200A1/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Withdrawn legal-status Critical Current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
    • F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
    • F16D23/00—Details of mechanically-actuated clutches not specific for one distinct type
    • F16D23/02—Arrangements for synchronisation, also for power-operated clutches
    • F16D23/04—Arrangements for synchronisation, also for power-operated clutches with an additional friction clutch
    • F16D23/06—Arrangements for synchronisation, also for power-operated clutches with an additional friction clutch and a blocking mechanism preventing the engagement of the main clutch prior to synchronisation
    • 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
    • F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
    • F16D25/00—Fluid-actuated clutches
    • F16D25/12—Details not specific to one of the before-mentioned types
    • F16D25/14—Fluid pressure control
    • 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
    • F16H61/00—Control functions within control units of change-speed- or reversing-gearings for conveying rotary motion ; Control of exclusively fluid gearing, friction gearing, gearings with endless flexible members or other particular types of gearing
    • F16H61/02—Control functions within control units of change-speed- or reversing-gearings for conveying rotary motion ; Control of exclusively fluid gearing, friction gearing, gearings with endless flexible members or other particular types of gearing characterised by the signals used
    • F16H61/0262—Control functions within control units of change-speed- or reversing-gearings for conveying rotary motion ; Control of exclusively fluid gearing, friction gearing, gearings with endless flexible members or other particular types of gearing characterised by the signals used the signals being hydraulic
    • F16H61/0265—Control functions within control units of change-speed- or reversing-gearings for conveying rotary motion ; Control of exclusively fluid gearing, friction gearing, gearings with endless flexible members or other particular types of gearing characterised by the signals used the signals being hydraulic for gearshift control, e.g. control functions for performing shifting or generation of shift signals
    • 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
    • F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
    • F16D21/00—Systems comprising a plurality of actuated clutches
    • 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
    • F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
    • F16D25/00—Fluid-actuated clutches
    • F16D25/10—Clutch systems with a plurality of fluid-actuated clutches
    • 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
    • F16H2200/203—Transmissions using gears with orbital motion characterised by the engaging friction means not of the freewheel type, e.g. friction clutches or brakes
    • F16H2200/2064—Transmissions using gears with orbital motion characterised by the engaging friction means not of the freewheel type, e.g. friction clutches or brakes using at least one positive clutch, e.g. dog clutch
    • 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 invention relates to a multistage transmission according to the preamble of claim 1.
  • the switching unit is designed as a brake and has a rotatable coupling element and a Reib gleichö and a parallel to the Reib gleich ancient time.
  • Coupling element fixed to the housing.
  • Multi-speed transmission from DE 10 201 1 108 024 A1 is associated with the combined switching unit and has a transmission element which is permanently connected in a rotationally fixed manner to the rotatable coupling element of the combined switching unit.
  • the invention is in particular the object of a power loss of
  • the invention is based on a multi-speed transmission for a motor vehicle, with a transmission input shaft for the rotationally fixed connection of an internal combustion engine, with at least four along a main axis of rotation arranged one behind the other
  • Planetary gear and at least one combined switching unit which is formed as a brake and a rotatable coupling element and a Reib gleichö and a parallel to the Reib gleichtechnik switched form-locking unit, which are each provided to connect the rotatable coupling element fixed to the housing, having one of the planetary gear stages of the combined Switching unit is assigned and a Includes transmission element which is permanently connected non-rotatably connected to the rotatable coupling element of the combined switching unit.
  • Planet wheel includes a further transmission element which is permanently connected in rotation with the transmission input shaft.
  • a transmission element of a planetary gear stage embodied as an input stage can be connected to a transmission housing in a particularly advantageous frictional and / or positive-locking manner, so that switchable transmission gears with different torque requirements can be optimally switched loss-adjusted and conveniently by holding the transmission element.
  • a power loss in particular a towing power of the multi-speed transmission, can be reduced in a particularly space-neutral manner, in particular without provision of additional installation space.
  • additional should in particular additionally in comparison to a multi-stage transmission, which is a combined switching unit, the one formed as an input stage
  • Switching unit "should be understood in particular a switching unit, the
  • a "form-locking unit” is to be understood as meaning, in particular, a part of the combined switching unit which has toothing and / or claws for the connection fixed to the housing and which engage in a form-fitting manner to produce a rotationally fixed coupling, such as, in particular, a coupling
  • a “friction-locking unit” is to be understood as meaning, in particular, a part of the combined shifting unit which has frictional elements, in particular slats, which are frictionally connected to one another to produce a rotationally fixed coupling, such as, in particular, a multiple-disk shift unit
  • Form-fitting unit are preferably arranged operatively between the gear housing and the rotatable coupling element of the combined switching unit.
  • non-rotatably connected is meant in particular a connection in which a power flow averaged over a complete revolution with an unchanged torque, an unchanged direction of rotation and / or an unchanged speed is transmitted.
  • combined switching unit is intended in particular a
  • Ratchet unit alone can be made by the form-locking unit alone or together by the Reib gleichtechnik and the form-locking unit.
  • a "planetary gear stage associated with the combined shifting unit” is to be understood in particular as meaning a planetary gear wheel having at least one transmission element which is permanently connected in a rotationally fixed manner to the rotatable coupling element of the combined shifting unit. the at least one
  • Planet wheel is designed as a sun gear. This can be one of the
  • Combustion engine provided drive torque over that of the combined
  • Coupling element of the combined switching unit connected gear element of the combined switching unit associated planetary gear is designed as a planet carrier, whereby the formed as an input stage planetary gear can be connected advantageously.
  • the combined switching unit associated with the planetary gear has a trained as a ring gear member which is non-rotatably connected to a transmission element at least one other planetary gear at least, whereby the interconnection of the combined switching unit
  • Switching unit rotatably with a transmission element at least one of the other
  • Planetenradkgn is at least connectable, whereby the combined switching unit can act on at least one other planetary gear.
  • the multistage transmission has a drive-side
  • Housing end wall is to be understood in particular a housing end wall, which is arranged closer to the combustion engine compared to an axially opposite, output side housing end wall axially and / or along an emanating from the engine power flow closer to” arranged with respect to the other Planetenradizin immediately adjacent to the housing end wall " in particular be understood that axially missing between the drive-side housing end wall and the combined switching unit associated planetary gear planetary gear.
  • the term "axial” is particularly related to the main axis of rotation, so that the term “axial” refers to a direction that extends on the main axis of rotation or parallel to it.
  • Planetenradkg arranged, whereby a particularly compact multi-step transmission can be provided.
  • the form-locking unit on an equal radius as the
  • Friction element be arranged. It is further proposed that the form-locking unit be radially inside the
  • ReibBank Republic is arranged, whereby a peripheral speed of a
  • Form-fitting teeth of the form-locking unit can be kept low.
  • the term “radial” and the term “radius” are particularly related to the main axis of rotation, so that the term “radially” denotes a direction that is perpendicular to the main axis of rotation a form-locking unit are understood, the teeth and / or claws circulate on a circular path having a mean diameter which is smaller than a mean diameter of a circular path on the friction surfaces of the friction elements rotate.
  • the multistage transmission comprises a further, designed as a clutch switching unit having a rotatable coupling element which is permanently connected in rotation with the transmission input shaft and a
  • Has outer disk carrier at least partially in one piece with a
  • a "switching unit designed as a clutch” is to be understood in particular as meaning a switching unit which is provided to non-rotatably interconnect its two rotatably arranged coupling elements, which are independently rotatable in an open state, in a closed state trained switching unit in a power flow between at least two
  • integral should be understood to mean, in particular, a single piece, such as, for example, a single-piece production
  • Outer disk carrier formed inner disk carrier for receiving inner disk of ReibQueryiens the combined switching unit and for receiving
  • Switching unit is arranged axially between the drive-side housing end wall and the further switching unit, whereby an alternative arrangement of the form-locking unit can be provided. Furthermore, it is advantageous if the combined switching unit has a first actuating unit provided for actuating the friction-locking unit and a second actuating unit provided for actuating the positive-locking unit and the further switching unit has a third actuating unit, wherein the first actuating unit and the third actuating unit axially between the drive-side housing end wall and the second actuating unit are arranged. This allows an advantageous operation of the combined switching unit and the other switching unit can be realized without providing additional space.
  • the combined switching unit has a first actuating unit provided for actuating the friction-locking unit and a second actuating unit provided for actuating the positive-locking unit and the further switching unit has a third actuating unit
  • the second actuator and the third actuator unit are arranged axially between the drive-side housing end wall and the Reib gleichritt the combined switching unit.
  • the form-fitting unit of the combined switching unit can be arranged radially inside the Reib gleichritt the combined switching unit and radially within a Reib gleichritt the other switching unit, whereby the peripheral speed of the form-fitting toothing can be further reduced.
  • closing directions of the actuating units are all rectified, whereby a supply of the
  • a "closing direction” should be understood in particular a direction in which a
  • actuating element is to be understood to mean, in particular, an axially movable element that presses the inner and outer disks of a friction-locking unit against one another to close the friction-locking unit or a form-fitting toothing of a form-locking unit moves into a corresponding positive-locking toothing of the form-fitting unit for closing the form-fitting unit.
  • the combined switching unit has a first one provided for actuating the friction-locking unit
  • Actuator and provided for actuating the form-locking unit second Actuating unit and the further switching unit comprises a third actuating unit, wherein the second actuating unit and the third actuating unit are arranged axially between the drive-side housing end wall and the first actuating unit.
  • the form-fitting unit of the combined switching unit can be arranged in a particularly space-neutral manner radially inside the friction-locking unit of the further switching unit.
  • Planetary gear as a first planetary gear and one of the combined switching unit associated planetary gear adjacent planetary gear as a second
  • Planetary gear is formed, wherein the adjacent planetary gear as a
  • Planet gear carrier has trained gear member which is permanently connected rotationally fixed with a gear formed as a ring gear of the combined switching unit associated planetary gear, and designed as a ring gear
  • gear element having a trained as a sun gear element of a third planetary gear and a trained as a sun gear
  • Transmission element of a fourth planetary gear is permanently connected rotationally fixed and rotatably connected to the planetary gear formed as a gear member of the combined switching unit associated planetary gear.
  • a particularly advantageous interconnection of the planetary gear stages can be realized.
  • the first planetary gear stage is located in the first place, the second planetary gear stage second, the third planetary gear stage in third place and the fourth planetary gear stage in fourth place.
  • a "planetary gear stage associated with the planetary gear stage associated with the combined switching unit” is to be understood in particular as meaning a planetary gear stage which is arranged axially next to the planetary gear stage associated with the combined switching unit.
  • FIG. 1 is a transmission diagram of a multi-speed transmission according to the invention
  • Fig. 4 shows schematically a part of a multi-speed transmission in a third
  • Fig. 5 shows schematically a part of a multi-speed transmission in a fourth
  • Figures 1 and 2 show a multi-speed transmission of a motor vehicle.
  • the motor vehicle has an internal combustion engine, not shown, for driving the motor vehicle and driving wheels not shown in detail.
  • the multistage transmission is arranged in a power flow between the internal combustion engine and the drive wheels.
  • the multistage transmission connects the combustion engine with the drive wheels.
  • a transmission ratio between the engine and the drive wheels is set.
  • the multi-speed transmission can be connected to a hybrid drive module, by means of which a drive torque can be changed.
  • a CVT can be realized, whereby the transmission ratio can be adjusted continuously, at least in some areas.
  • the multi-speed transmission has a gear 17a.
  • the gear set 17a has nine forward gears and one reverse gear.
  • the forward gears have sequential gear ratios.
  • the first forward gear has the largest gear ratio and the last, in this embodiment ninth forward gear on the smallest gear ratio, wherein the gear ratio from the low to the high forward gear.
  • the reverse gear has a direction of rotation reversal compared to the forward gears.
  • the multistage transmission furthermore has a transmission housing 18a, which comprises a drive-side housing end wall 14a, an output-side housing front wall 19a located axially opposite the drive-side housing end wall 14a, and a housing peripheral wall 20a arranged axially between the housing end walls 14a, 19a.
  • a transmission housing 18a which comprises a drive-side housing end wall 14a, an output-side housing front wall 19a located axially opposite the drive-side housing end wall 14a, and a housing peripheral wall 20a arranged axially between the housing end walls 14a, 19a.
  • the housing end walls 14a, 19a and the housing peripheral wall 20a are formed integrally with each other.
  • the gear set 17a is disposed inside the transmission case 18a.
  • the transmission housing 18a is arranged stationary. In principle, at least one of the housing end walls 14a, 19a may be formed separately from the housing peripheral wall 20a.
  • the multi-stage transmission has a transmission input shaft 10a.
  • the transmission input shaft 10a passes through the drive-side housing end wall 14a and ends within the transmission housing 18a between the two housing end walls 14a, 19a.
  • the transmission input shaft 10a is disposed in a power flow from the engine after the engine and before the gear train 17a. It is provided for the rotationally fixed connection of the internal combustion engine and thus for the rotationally fixed connection of a crankshaft of the internal combustion engine to the gear set 17a.
  • the transmission input shaft 10a drivingly connects the engine with the gear set 17a.
  • the transmission input shaft 10a may be preceded by a module not shown in detail, which in particular provides a start-up functionality. As an upstream module, for example, a torque converter or a wet starting clutch is conceivable. In principle, however, the module provided for starting can also be integrated in the gear set 17a.
  • the multi-speed transmission has a transmission output shaft 21 a.
  • the transmission output shaft 21 a passes through the output-side housing end wall 19 a and ends outside the transmission housing 18 a.
  • the transmission output shaft 21a is disposed in the power flow from the engine after the gear train 17a and before the drive wheels.
  • the transmission output shaft 21 a connects the gear set 17 a drive technology with the drive wheels of the motor vehicle.
  • the transmission output shaft 21 a may be connected downstream of a module not shown in detail, by means of which the output from the gear set 17 a driven torque can be distributed to the drive wheels, such as example, a planetary gear, which is provided for a speed compensation between the drive wheels, or an all-wheel drive unit that distributes the drive torque to two different drive axles.
  • the transmission input shaft 10a and the transmission output shaft 21a can basically be arranged arbitrarily to each other.
  • the gear set 17a has four planetary gear stages Pi a, P2a, P3a, P4a, which are operatively connected to each other for switching the gears.
  • the first planetary gear stage Pi a, the second planetary gear P2a, the third planetary gear P3a and the fourth planetary gear P4a are arranged one behind the other along a main axis of rotation 1 1 a.
  • An axis of rotation of the transmission input shaft 10a coincides with the main axis of rotation 1 1 a.
  • All planetary gear stages Pi a, P2a, P3a, P4a of the gear set 17a have a jointlyplanetenradsatz.
  • first”, “second”, “third” and “fourth” indicate an axial order of the planetary gear stages Pi a, P2a, P3a, P4a starting from the internal combustion engine. Accordingly, the first planetary gear Pi is compared to the other planetary gear P2a, P3a, P4a at the first axial position, the second planetary gear P2a compared to the other planetary gear stages Pi a, P3a, P4a at the second axial position, the third planetary gear P3a in comparison to the other planetary gear stages Pi a, P2a, P4a arranged at the third axial position and the fourth planetary gear P4a compared to the other planetary gear stages Pi a, P2a, P3a at fourth axial position.
  • the first planetary gear stage Pi a and the second planetary gear P2a are arranged adjacent to each other, the second planetary gear P2a and the third planetary gear P3a are adjacent to each other and the third planetary gear P3a and the fourth planetary gear P4a are adjacent to each other.
  • the first planetary gear stage Pi a is disposed immediately adjacent to the drive-side housing end wall 14a with respect to the planetary gear stages P2a, P3a, P4a, i. the first planetary gear stage Pi a is arranged closest to the drive-side housing end wall 14a in comparison with the other planetary gear stages P2a, P3a, P4a.
  • the fourth planetary gear P4a is arranged with respect to the planetary gear stages Pi a, P2a, P3a immediately adjacent to the drive-side housing end wall 19a, i. the fourth planetary gear P4a is compared to the other planetary gear stages Pi a, P2a, P3a closest to the drive-side housing end wall 19a arranged.
  • the four planetary gear stages Pi a, P2a, P3a, P4a are described in more detail.
  • the four planetary gear stages Pi a, P 2 a, P 3 a, P 4 a each have a gear element designed as a sun gear, a gear element designed as a planet carrier and a trained as a ring gear element.
  • a "first to fourth planetary gear carrier”, a “first to fourth sun gear” and a “first to fourth ring gear” are to be understood as one of the first to fourth planetary gear carriers or a sun gear or a ring gear, ie, for example Under the first planet carrier designed as a planet carrier gear element of the first planetary gear to be understood.
  • the first planetary gear Pia is arranged on the input side.
  • the first planetary gear Pia includes a first sun gear P1 1 a, a first ring gear P13a and a first planet P12a.
  • the first planet carrier P12a leads planetary gears P14a of the first planetary gear Pia on a circular path.
  • the planetary gears P14a mesh with the first sun gear P1 1 a and with the first ring gear P13a.
  • the planetary gears P14a are rotatably supported on the first planet carrier P12a.
  • the second planetary gear P2a is arranged centrally on the input side.
  • the second planetary gear P2a includes a second sun gear P21a, a second ring gear P23a, and a second planetary gear carrier P22a.
  • the second planet carrier P22a leads planetary gears P24a of the second planetary gear P2a on a circular path.
  • the planet gears P24a mesh with the second sun gear P21a and with the second ring gear P23a.
  • the planetary gears P24a are rotatably supported on the second planet carrier P22a.
  • the third planetary gear P3a is arranged centrally on the output side.
  • the third planetary gear P3a includes a third sun gear P31a, a third ring gear P33a, and a third planetary gear P32a.
  • the third planet carrier P32a leads planetary gears P34a of the third planetary gear P3a on a circular path.
  • the planetary gears P34a mesh with the third sun gear P31a and with the third ring gear P33a.
  • the planetary gears P34a are rotatably supported on the third planet carrier P32a.
  • the fourth planetary gear P4a is arranged on the output side.
  • the fourth planetary gear P4a includes a fourth sun gear P41a, a fourth ring gear P43a and a fourth planet carrier P42a.
  • the fourth planet carrier P42a leads planetary gears P44a of the fourth planetary gear P4a on a circular path.
  • the planet gears P44a mesh with the fourth sun gear P41a and with the fourth ring gear P43a.
  • the planet gears P44a are rotatably supported on the fourth planet carrier P42a.
  • a part of the transmission elements of the planetary gear stages Pi a, P2a, P3a, P4a are permanently connected to each other in a rotationally fixed manner.
  • the first ring gear P13a is permanently rotatable with the second planet carrier P22a connected.
  • the second ring gear P23a is permanently non-rotatably connected to the third sun P31a and permanently rotatably connected to the fourth sun gear P41a.
  • the third sun P31a and the fourth sun P41a are permanently connected to each other rotatably.
  • the first planetary gear stage Pia and the fourth planetary gear stage P4a are each designed as an input stage.
  • the first sun P11a permanently connected rotationally fixed to the transmission input shaft 10a.
  • the fourth planetary gear P4a as an input stage of the fourth planet P42a is permanently connected rotationally fixed to the transmission input shaft 10a.
  • the third planetary gear P3a and the fourth planetary gear P4a are each formed as an output stage.
  • the third planet P32a permanently connected rotationally fixed to the transmission output shaft 21a.
  • the fourth ring gear P43a rotatably connected to the transmission output shaft 21 a connectable.
  • the gear set 17a has six switching units S1a, S2a, S3a, S4a, S5a, S6a.
  • the switching units S1a, S2a, S3a, S4a, S5a, S6a transmit different torques in the transmission gears.
  • the gear set 17a defines for the switching units S1a, S2a, S3a, S4a, S5a, S6a torque factors in the transmission gears. By the torque factors in the gear trains of the switching units S1a, S2a, S3a, S4a, S5a, S6a transmitted torques defined in the gear set 17a.
  • the torque factors are dependent on a position of the switching units S1a, S2a, S3a, S4a, S5a, S6a in the gear set 17a.
  • the torques transmitted by the switching units S1a, S2a, S3a, S4a, S5a, S6a are dependent on a switched gear, the torque factor and a drive torque.
  • the six switching units S1 a, S2a, S3a, S4a, S5a, S6a each have a total design torque.
  • the respective overall design moments are based on a maximum torque to be transmitted from the respective shift unit S1 a, S2a, S3a, S4a, S5a, S6a in the associated transmission gears.
  • the overall design torques are adapted to the gear shifts and may differ from switching unit S1a, S2a, S3a, S4a, S5a, S6a to switching unit S1a, S2a, S3a, S4a, S5a, S6a.
  • the three switching units S1 a, S3a, S6a are each formed as a coupling. They respectively have a first rotatable coupling element S11a, S31a, S61a and a second rotatable coupling element S11a. tes rotatable coupling element S12a, S32a, S62a.
  • the three switching units S1 a, S3a, S6a are each provided to connect their two coupling elements S1 1 a, S12a, S31a, S32a, S61a, S62a rotation with each other.
  • the three switching units S2a, S4a, S5a are each formed as a brake. They each have a rotatable coupling element S21a, S41a, S51a.
  • the switching units S2a, S4a, S5a are each provided to their rotatable coupling element S21 a, S41a, S51a fixed to the housing and thus rotatably connected to the transmission housing 18a to connect.
  • the first switching unit S1 a has the first rotatable coupling element S1 1 a and the second rotatable coupling element S12a.
  • the first rotatable coupling element S11 a of the first switching unit S1a is permanently non-rotatably connected to the transmission input shaft 10a.
  • the second rotatable coupling element S12a of the first switching unit S1a is permanently connected in a rotationally fixed manner to the rotatable coupling element S21a of the second switching unit S2a.
  • the second rotatable coupling element S12a of the first switching unit S1a is further permanently non-rotatably connected to the first planet carrier P12a.
  • the second rotatable coupling element S12a of the first switching unit S1a is permanently connected in a rotationally fixed manner to the first rotatable coupling element S31a of the third switching unit S3a.
  • the first switching unit S1 a is provided to rotatably connect the first planet P12a with the transmission input shaft 10a.
  • the second switching unit S2a has the rotatable coupling element S21a.
  • the rotatable coupling element S21 a of the second switching unit S2a is permanently connected in a rotationally fixed manner to the first planet carrier P12a. Further, the rotatable coupling element S21 a of the second switching unit S2a permanently non-rotatably connected to the first rotatable coupling element S31 a of the third switching unit S3a.
  • the second switching unit S2a is provided to connect the first planet P12a fixed to the housing.
  • the third switching unit S3a has the first rotatable coupling element S31a and the second rotatable coupling element S32a.
  • the first rotatable coupling element S31a of the third switching unit S3a is permanently connected in a rotationally fixed manner to the first planet carrier P12a.
  • the second rotatable coupling element S32a of the third switching unit S3a is permanently connected in a rotationally fixed manner to the second ring gear P23a.
  • the second rotatable coupling element S32a of the third switching unit S3a is further permanently non-rotatably connected to the third sun gear P31 a.
  • the second rotatable coupling element S32a of the third switching unit S3a is permanently non-rotatably connected to the fourth sun gear P41 a connected.
  • the third switching unit S3a is provided for non-rotatably connecting the first planet carrier P12a, the second ring gear P23a, the third sun gear P31a and the fourth sun gear P41a.
  • the fourth switching unit S4a has the rotatable coupling element S41a.
  • the rotatable coupling element S41a of the fourth switching unit S4a is permanently connected in a rotationally fixed manner to the second sun gear P21a.
  • the fourth switching unit S4a is provided to connect the second sun gear P21a fixed to the housing.
  • the fifth switching unit S5a has the rotatable coupling element S51a.
  • the rotatable coupling element S51a of the fifth switching unit S5a is permanently connected in a rotationally fixed manner to the third ring gear P33a.
  • the fifth switching unit S5a is provided to connect the third ring gear P33a fixed to the housing.
  • the sixth switching unit S6a has the first rotatable coupling element S61a and the second rotatable coupling element S62a.
  • the first rotatable coupling element S61 a of the sixth switching unit S6a is permanently non-rotatably connected to the fourth ring gear P43a.
  • the second rotatable coupling element S62a of the sixth switching unit S6a is permanently connected in a rotationally fixed manner to the third planet carrier P32a.
  • the second rotatable coupling element S62a of the sixth switching unit S6a is further permanently non-rotatably connected to the transmission output shaft 21 a.
  • the sixth switching unit S6a is provided for non-rotatably connecting the fourth ring gear P43a, the third planet carrier P32a and the transmission output shaft 21a.
  • the three switching units S1 a, S3a, S6a designed as a coupling have only one friction-locking unit 22a, 23a, 24a for the non-rotatable connection of their coupling elements S11a, S12a, S31a, S32a, S61a, S62a.
  • the frictional engagement units 22a, 23a, 24a each comprise a disk pack.
  • the fourth switching unit S4a and the fifth switching unit S5a point to the housing-fixed connection of their rotatable
  • Coupling elements S41 a, S51 a each only one ReibBanktechnik 25a, 26a on.
  • the frictional engagement units 25a, 26a each comprise a disk pack.
  • the ReibBankilia 22 a of the first switching unit S1 a is axially between the
  • the first switching unit S1 a further comprises an inner disk carrier which is permanently connected in a rotationally fixed manner to the first rotatable coupling element S11 a of the first switching unit S1 a, and an outer disk carrier which is permanently non-rotatable is connected to the rotatable second coupling element S12a of the first switching unit S1 a, on.
  • the inner disk carrier of the first switching unit S1 a is permanently non-rotatably connected to the transmission input shaft 10a.
  • the intuitioniameilenovic the first switching unit S1 a is permanently connected rotationally fixed to the first planet P12a.
  • the frictional engagement unit 23a of the third shift unit S3a is arranged axially between the first planetary gear stage Pia and the second planetary gear P2a.
  • the first planetary gear stage Pi a is axially between the Reib gleichä 22 a of the first
  • the third switching unit S3a further comprises an inner disc carrier, which is permanently connected in a rotationally fixed manner to the second rotatable coupling element S32a of the third shift unit S3a, and an outer cam carrier, which is permanently connected in a rotationally fixed manner to the first rotatable coupling element S31a of the third shift unit S3a.
  • the inner disk carrier of the third switching unit S3a is permanently connected in a rotationally fixed manner to the ring gear P23a.
  • Switching unit S3a is permanently connected in a rotationally fixed manner to the first planet carrier P12a.
  • the phenomenoniameilenabo the first switching unit S1 a and the phenomenoniameilenovic the third switching unit S3a permanently non-rotatably connected to each other.
  • the frictional engagement unit 25a of the fourth shift unit S4a is arranged axially between the first planetary gear stage Pi a and the third planetary gear P3a.
  • Frictional engagement unit 25a of the fourth switching unit S4a is axially in the amount of the second
  • the frictional engagement unit 25a of the fourth shift unit S4a is disposed axially between the frictional engagement unit 23a of the third shift unit S3a and the frictional engagement unit 26a of the fifth shift unit S5a.
  • Planetary gear P2a is axially between the ReibBank Republic 23a of the third
  • the first planetary gear stage Pi a is arranged axially between the first switching unit S1 a and the fourth switching unit S4a.
  • the first planetary gear stage Pi a is axially between the ReibBankech 22 a of the first switching unit S1 a and the
  • the fourth switching unit S4a further comprises an inner disk carrier, which is permanently connected in a rotationally fixed manner to the rotatable coupling element S41a of the fourth switching unit S4a, and a
  • Switching unit S4a is connected to the housing peripheral wall 20a. It is attached to the housing peripheral wall 20a.
  • the frictional engagement unit 26a of the fifth shift unit S5a is disposed axially between the second planetary gear P2a and the fourth planetary gear P4a.
  • ReibsBanksaku 26a of the fifth switching unit S5a is axially equal to the third
  • the frictional engagement unit 26a of the fifth shift unit S5a is disposed axially between the frictional engagement unit 25a of the fourth shift unit S4a and the frictional engagement unit 24a of the sixth shift unit S6a.
  • Planetary gear P3a is axially between the ReibBankieri 25a of the fourth
  • the fifth switching unit S5a further comprises an inner disc carrier, which is permanently connected in a rotationally fixed manner to the rotatable coupling element S51a of the fifth shift unit S5a, and an outer disc carrier which is permanently connected in a rotationally fixed manner to the transmission housing 18a.
  • Switching unit S5a is permanently rotatably connected to the third ring gear P33a.
  • the outer disk carrier of the fifth shift unit S5a is connected to the housing peripheral wall 20a. It is attached to the housing peripheral wall 20a.
  • the frictional engagement unit 24a of the sixth shift unit S6a is located axially between the output-side housing front wall 19a and the fourth planetary gear P4a
  • the fourth planetary gear P4a is axially between the frictional engagement unit 26a of the fifth shift unit S5a and the frictional engagement unit 24a of the sixth
  • the sixth switching unit S6a also has a
  • Inner disc carrier permanently rotatable with the first rotatable
  • Coupling element S61 a of the sixth switching unit S6a is connected, and an outer disk carrier, the permanent rotation with the second rotatable
  • Coupling element S62a of the sixth switching unit S6a is connected, on.
  • Inner disk carrier of the sixth switching unit S6a is permanently connected in a rotationally fixed manner to the fourth ring gear P43a.
  • the outer disk carrier of the sixth switching unit S6a is permanently non-rotatably connected to the third planetary P32a and permanently rotatably connected to the transmission output shaft 21a.
  • the second switching unit S2a is formed in combination and thus has a
  • the second switching unit S2a is formed as a combined switching unit.
  • the first planetary gear stage Pi a is formed as one of the combined switching unit S2a associated planetary gear.
  • the combined switching unit S2a is the first formed as an input stage
  • combined switching unit S2a is permanently rotatably connected to the planet P12a of the input stage designed as a first planetary gear Pia.
  • the trained as input stage planetary gear Pi a is axially between the
  • the frictional engagement unit 12a transmits the torque applied to the first planet carrier P12a to the switched eighth forward gear and the switched ninth forward gear.
  • the form-fitting unit 13a transmits the torque applied to the first planet carrier P12a only in the switched reverse gear.
  • the friction-locking unit 12a and the form-fitting unit 13a of the combined switching unit S2a each have a design moment.
  • the design moment of the frictional engagement unit 12a and the design moment of the form-fitting unit 13a are different.
  • the design torque of the frictional engagement unit 12a is smaller than the total design torque of the second shift unit S2a.
  • the design moment of the form-fitting unit 13a corresponds to the total design moment of the second switching unit S2a.
  • the design moment of the frictional engagement unit 12a is smaller than the design moment of the form-fitting unit 13a.
  • the second switching unit S2a transmits in the switched reverse gear, a torque which is greater than the design torque of the Reib gleichtechnik 12a and in the switched eighth and ninth forward gear, a torque which is smaller than the design torque of the ReibBanktechnik 12a.
  • the friction engagement unit 12a transmits the applied torque completely.
  • the form-fitting unit 13a also completely transmits the torque.
  • the interlocking unit 13a in at least one of the gears in which the applied torque is greater than the design torque of the Reib gleichtechnik 12a, only transmits an excess torque.
  • the excess torque is approximately a difference between the applied torque and the design torque of the frictional engagement unit 12a.
  • the frictional engagement unit 12a of the combined shift unit S2a is formed as a multi-disc brake.
  • the frictionally engaging unit 12a comprises a disk pack for the housing-fixed connection of the rotatable coupling element S21a.
  • the friction-locking unit 12a of the combined switching unit S2a has an outer disk carrier 15a, which is permanently connected in a rotationally fixed manner to the transmission housing 18a, and an inner disk carrier 16a, which is permanently connected in a rotationally fixed manner to the rotatable coupling element S21a.
  • the inner disk carrier 16a of the combined switching unit S2a is permanently connected in a rotationally fixed manner to the planet carrier P12a of the first planetary gear stage Pi a designed as an input stage.
  • the inner disk carrier 16a of the combined switching unit S2a is formed integrally with the outer disk carrier of the first switching unit S1a.
  • the friction-locking unit 12a is operatively arranged between the drive-side housing end wall 14a and the rotatable coupling element S21a.
  • the outer plate carrier 15a of the combined switching unit S2a is connected to the drive-side housing end wall 14a. It is attached to the drive-side housing end wall 14a. Alternatively, the outer disk carrier 15a may also be connected in a more radial direction to a housing peripheral wall of the transmission housing 18a.
  • the form-fitting unit 13a of the combined switching unit S2a is designed as a claw brake.
  • the form-fitting unit 13a comprises a first form-fitting element 27a and a second form-fitting element 28a.
  • the first positive locking element 27a is permanently connected in a rotationally fixed manner to the rotatable coupling element S21 of the combined switching unit S2a. It is rotatably connected to the inner disk carrier 16a of the combined switching unit S2a.
  • the first positive locking element 27a has a dog toothing. The dog teeth are fixedly mounted on the rotatable coupling element S21 a of the combined switching unit S2a.
  • the first positive engagement element 27a is formed integrally with the rotatable coupling element S21a of the combined shift unit S2a.
  • the second positive locking element 28a is non-rotatably, but axially displaceably connected to the transmission housing 18a. It is rotationally fixed, but axially slidably connected to the housing peripheral wall 20a.
  • the form-fitting unit 13a is operatively disposed between the housing peripheral wall 20a and the rotatable coupling member S21a.
  • the second positive locking element 28a has a dog toothing, which is formed corresponding to the dog teeth of the first positive-locking element 27a.
  • the dog teeth are each formed as a spur toothing.
  • the second positive locking element 28a is arranged to be axially movable relative to the first positive locking element 27a.
  • Switching unit S2a are arranged axially between the drive-side housing end wall 14a and the first planetary gear stage Pia designed as an input stage.
  • Form-fitting unit 13a are arranged axially between the housing end wall 14a and formed as an input stage first planetary gear Pi a.
  • the frictional engagement unit 12a of the combined shift unit S2a is arranged axially at the level of the frictional engagement unit 22a of the first shift unit S1a.
  • the disk set of the friction engagement unit 12a of the combined shift unit S2a is radially above
  • Disk set of ReibBankica 22a of the first switching unit S1 a arranged.
  • the disk set of the friction engagement unit 22a of the first shift unit 5a is arranged radially inside the disk pack of the friction engagement unit 12a of the combined shift unit S2a.
  • Lamella packages of the combined switching unit S2a formed annular surface is greater than a mean diameter of an annular surface formed by a friction surface of the disk set of the first switching unit S1 a.
  • the form-fitting unit 13a of the combined switching unit S2a is arranged axially between the friction-locking unit 12a of the combined switching unit S2a and the first planetary gear stage Pia designed as an input stage.
  • the frictional engagement unit 12a of the combined shift unit S2a is disposed axially between the drive-side housing end wall 14a and the form-fitting unit 13a of the combined shift unit S2a.
  • the form-fitting unit 13a of the combined switching unit S2a is arranged axially between the first switching unit S1a and the first planetary gear stage Pia designed as an input stage.
  • the form-fitting unit 13a of the combined switching unit S2a is arranged radially inside the friction-locking unit 12a of the combined switching unit S2a.
  • Form-fitting unit 13a of the combined switching unit S2a is radially in the amount of
  • the mean diameter of the annular surface formed by the dog teeth of the second switching unit S2a is between an inner and
  • the combined switching unit S2a has two independent actuating units 29a, 30a.
  • the first operation unit 29a operates the friction engagement unit 12a.
  • the first actuating unit 29a has an axially movable actuating element, which presses against the housing-fixed connection of the rotatable coupling element S21 a of the combined switching unit S2a axially against the disk set of the Reib gleichtechnik 12a of the combined switching unit S2a, which move slats of the disk set axially relative to each other until they lie against each other and are positively connected with each other.
  • the first operating unit 29a is on the drive side
  • Housing end wall 14a connected. It is attached to the drive-side housing end wall 14a.
  • the first operating unit 29a is disposed axially between the frictional engagement unit 12a of the combined switching unit S2a and the drive-side housing end wall 14a. It is axially between the form-locking unit 13 a of the combined
  • the first operating unit 29a is axially between the ReibBankica 22a of the first
  • the second operating unit 30a actuates the form-locking unit 13a.
  • Actuator 30a has an axially movable actuator which is fixedly connected to the second positive locking element 28a and axially displaceable, but rotatably connected to the transmission housing 18a.
  • Actuator 30a For housing-fixed connection of the rotatable coupling element S21a of the combined switching unit S2a moves the
  • Positive locking element 28a axially in the direction of the first positive locking element 27a until the correspondingly formed to each other dog teeth of the form-locking unit 13a of the combined switching unit S2a intermesh positively.
  • the second positive locking element 28a is axially in the direction
  • the second operating unit 30a is connected to the housing peripheral wall 20a. She is at the Housing peripheral wall 20a attached.
  • the second operating unit 30a is arranged axially between the third switching unit S3a and the drive-side housing end wall 14a. It is axially between the ReibBankritt 12 a of the combined switching unit S2a shifted.
  • Actuator 30a radially surrounds partially the first switching unit S1 a.
  • Coupling element S12a of the first switching unit S1a are partially disposed within the second operating unit 30a.
  • the second operating unit 30a of the combined switching unit S2a partially surrounds the rotatable coupling element S21a of FIG
  • the first switching unit S1a For actuating the friction-locking unit 22a of the first switching unit S1a, the first switching unit S1a has an actuating unit 31a.
  • the operating unit 31a of the first switching unit S1a and the first operating unit 29a of the combined switching unit S2a are arranged axially between the drive-side housing end wall 14a and the second actuating unit 30a of the combined switching unit S2a.
  • Actuator 31 a of the first switching unit S1 a is axially between the
  • Housing end wall 14a arranged. It is arranged axially between the form-locking unit 13a of the combined switching unit S2a and the drive-side housing end wall 14a.
  • the operating unit 31a of the first switching unit S1a is disposed radially inside the first operating unit 29a of the combined switching unit S2a.
  • the actuating element of the first actuating unit 29a of the combined switching unit S2a radially surrounds the actuating unit 31a of the first switching unit S1a.
  • the actuating units 29a, 30a, 31a each have an axial closing direction into which the corresponding actuating element for closing the friction-locking unit 12a or the form-locking unit 13a is moved.
  • Actuating unit 29a of the combined switching unit S2a and the closing direction of the operating unit 31 a of the first switching unit S1 a are the same direction.
  • Closing direction of the first operating unit 29a of the combined switching unit S2a and the closing direction of the actuating unit 31 a of the first switching unit S1a point away from the drive-side housing end wall 14a and to the output side
  • the closing direction of the second operating unit 30a of the combined switching unit S2a is the closing direction of the first operating unit 29a of the combined switching unit S2a and the closing direction of the operating unit 31a the first switching unit S1 a opposite.
  • the closing direction of the second operating unit 30a of the combined switching unit S2a is the closing direction of the first operating unit 29a of the combined switching unit S2a and the closing direction of the operating unit 31a the first switching unit S1 a opposite.
  • Operating unit 30a of the combined switching unit S2a points away from the output-side housing end wall 19a and toward the drive-side housing end wall 14a.
  • the actuator units 29a, 30a, 31a are each formed hydraulically.
  • the actuating units 29a, 30a, 31a can also be designed electrically or pneumatically.
  • the switching units S1a, S2a, S3a, S4a, S5a, S6a and the actuator units 29a, 30a, 31a are within the transmission housing 18a
  • Actuating unit or two mutually dependent actuation units In this case, the friction-locking unit 12a and the form-fitting unit 13a are actuated in succession, wherein the friction-locking unit 12a preferably engages in front of the form-locking unit 13a.
  • FIGS. Three further embodiments of the invention are shown in FIGS.
  • the following descriptions are essentially limited to the differences between the exemplary embodiments, with regard in principle also to the figures and / or the description of the other embodiments, in particular of the embodiment in Figures 1 and 2, can be referenced. to
  • FIG. 3 shows a second exemplary embodiment of a multistage transmission
  • the multistage transmission comprises a transmission input shaft 10b, four along a main axis of rotation 1 1 b arranged one behind the other
  • the planetary gear stages P1b, P2b, P3b, P4b each have a sun gear P11b, P21b, P31b, P41b, a planet carrier P12b, P22b, P32b, P42b, and a ring gear P13b, P23b, P33b, P43b.
  • the multi-speed transmission continues to point
  • Transmission housing 18 b the drive-side housing end wall 14 b, a
  • Output-side housing end wall 19b and a housing peripheral wall 20b includes.
  • the first switching unit S1 b is formed as a coupling and has a first rotatable coupling element S1 1 b and a second rotatable coupling element S12b on, wherein the first rotatable coupling element S11 b permanently non-rotatably connected to the transmission input shaft 10b and the second rotatable coupling element S12d permanently rotatably connected to the planet P12d of the first planetary gear P1 b.
  • the second switching unit S2b is formed as a brake and has a rotatable coupling element S21 b, which is fixed to the housing, on.
  • the second switching unit S2b further comprises a Reib gleichussi 12b and a parallel to the Reib gleichtechnik 12b connected form-locking unit 13b, which are each provided to connect the rotatable coupling element S21 b fixed to the housing.
  • the second switching unit S2a is formed as a combined switching unit and associated with the first planetary gear Pia, which is formed as an input stage, whereby the first
  • the second switching unit S2b comprises an inner disk carrier 16b, which is non-rotatably connected to the rotatable coupling element S21b, and an outer disk carrier 15b, which is arranged fixed to the housing.
  • the outer disc carrier 15b is preferably connected to the housing end wall 14b or alternatively to a transmission housing peripheral wall.
  • the form-fitting unit 13b of the combined switching unit S2b is axially between the Reib gleichiens 12b of
  • the form-fitting unit 13b of the combined switching unit S2b is arranged axially between the first switching unit S1b and the drive-side housing end wall 14b.
  • the form-fitting unit 13b has dog teeth, which, in contrast to the previous embodiment, are arranged radially inside a friction-locking unit 22b of the first switching unit S1b.
  • Claw teeth of the combined switching unit S2b formed annular surface is smaller than a mean diameter of an annular surface formed by a friction surface of the ReibBankieri 22b of the first switching unit S1 b.
  • the combined switching unit S2b comprises a first actuating unit 29b, which is provided for actuating the friction-locking unit 12b, and a second actuating unit
  • Actuator 30b which is provided for actuating the form-locking unit 13b.
  • the second actuating unit 30b is arranged radially within the first actuating unit 29b.
  • Claw teeth of the form-fitting unit 13b are radially inward of the first one Actuator 29b of the combined switching unit S2b arranged.
  • Actuating member of the first operating unit 29b of the combined switching unit S2b surrounds the form-fitting unit 13b. Unlike the previous one
  • the form-fitting unit 13b is operatively arranged between the drive-side housing end wall 14b and the rotatable coupling element S21 b.
  • the second operating unit 30b of the combined switching unit S2b is connected to the drive-side housing end wall 14b. It is attached to the drive-side housing end wall 14b.
  • the friction engagement unit 12b and the form-fitting unit 13b are both operatively disposed between the drive-side housing end wall 14b and the rotatable coupling element S21b.
  • the first switching unit S1 b has an actuating unit 31 b, which is provided for actuating the ReibBankica 22 b of the first switching unit S1 b.
  • the form-fitting unit 13b is the
  • Combined switching unit S2b arranged axially between the actuating unit 31 b of the first switching unit S1 b and the drive-side housing end wall 14b.
  • Switching unit S1 b are arranged axially between the drive-side housing end wall 14b and the Reib gleichiens 12b of the combined switching unit S2b.
  • Actuator 31 b of the first switching unit S1 a is axially between the
  • Forming unit 13b of the combined switching unit S2b is disposed axially between the second operating unit 30b of the combined switching unit S2b and the operating unit 31b of the first switching unit S1b.
  • the actuating units 29b, 30b, 31b each have an axial closing direction into which the corresponding actuating element for closing the friction-locking unit 12b or the form-locking unit 13b is moved.
  • Closing direction of the actuating unit 31 b of the first switching unit S1 b are the same direction.
  • Switching unit S2b, the closing direction of the second operating unit 30b of Combined switching unit S2b and the closing direction of the actuating unit 31 b of the first switching unit S1 b respectively point away from the drive-side housing end wall 14b and toward the output-side housing front wall 19b.
  • the multistage transmission comprises a transmission input shaft 10 c, four along a main axis of rotation 11 c arranged one behind the other
  • Planetary gear stages and six switching units wherein in the figure 4, only the first planetary gear P1 c, the first switching unit Si c, the second switching unit S2c and the third switching unit S3c are shown.
  • the first planetary gear P1 c has a sun gear P1 1c, a planet P12c and a ring gear P13c.
  • the second switching unit S2c is formed as a combined switching unit and the first planetary gear P1 c, which is formed as an input stage, assigned, whereby the first planetary gear P1 c is formed as one of the combined switching unit S2c associated planetary gear.
  • Gear housing 18c which includes a drive-side housing end wall 14c, a non-illustrated output-side housing end wall and a housing peripheral wall 20c.
  • the first switching unit Sic is designed as a clutch and has a first rotatable coupling element S11 c and a second rotatable coupling element S12c, wherein the first rotatable coupling element S1 1 c permanently rotatably with the transmission input shaft 10c and the second rotatable coupling element S12c permanently rotatably connected to the planet P12c of the combined switching unit S2c associated planetary gear P1 c is connected.
  • the combined switching unit S2c is formed as a brake and has a rotatable coupling element S21 c, which is fixed to the housing, on.
  • the combined switching unit S2c further comprises a Reib gleich für 12c and a parallel to ReibBanktechnik 12c connected
  • Forming unit 13c which are each provided to the rotatable
  • the combined switching unit S2c comprises an inner disk carrier 16c, which is non-rotatable with the rotatable
  • Coupling element S21 c is connected, and an outer disk carrier 15 c, which is arranged fixed to the housing.
  • the Reib gleichtechnik 12c is operatively disposed between the housing peripheral wall 20c and the rotatable coupling element S21 c.
  • the outer disk carrier 15c of the friction engagement unit 12c is advantageously connected to the housing peripheral wall 20c. It is attached to the housing peripheral wall 20c.
  • External disk carrier 15c also be connected to the housing end wall 14c.
  • the combined switching unit S2c includes a first operating unit 29c provided for operating the friction engaging unit 12c, and a second operating unit 30c provided for operating the form-locking unit 13c.
  • the first actuating unit 29c of the combined switching unit S2c is arranged axially between the housing end wall 1c and the planetary gear stage P1c associated with the combined switching unit S2c.
  • Actuating member of the first operating unit 29c surrounds the second rotatable coupling element S12c of the first switching unit Sic.
  • Coupling element S12c of the first switching unit Sic is disposed radially inside the first operating unit 29c of the combined switching unit S2c.
  • Frictional engagement unit 12c of the combined shift unit S2c is disposed axially between the drive-side housing end wall 14c and the first operation unit 29c of the combined shift unit S2c.
  • the first operating unit 29c of the combined switching unit S2c is connected to the housing peripheral wall 20c. It is attached to the housing peripheral wall 20c.
  • the first switching unit S1 b has an actuating unit 31 c, which is provided for actuating a Reib gleichtechnik 22 c of the first switching unit Si c.
  • the second operating unit 30c of the combined switching unit S2c and the actuating unit 31c of the first switching unit Si c are axially between the drive-side housing end wall 14c and the first
  • Frictional engagement unit 12c of the combined shift unit S2c is disposed axially between the first operation unit 29c of the combined shift unit S2c and the operation unit 31c of the first shift unit Sic.
  • the actuating units 29c, 30c, 31c each have an axial closing direction into which the corresponding actuating element for closing the friction-locking unit 12c or the form-locking unit 13c is moved.
  • the closing direction of the second operating unit 30c of the combined switching unit S2c and the closing direction of the operating unit 31c of the first switching unit Sic are the same.
  • Actuating unit 30c of the combined switching unit S2c and the closing direction of the operating unit 31c of the first switching unit Sic point from the driving side Housing end wall 14c away and to the output side housing end wall.
  • Closing direction of the first operating unit 29c of the combined switching unit Si c is opposite to the closing direction of the second operating unit 30c of the combined switching unit S2c and the closing direction of the operating unit 31c of the first switching unit Si c.
  • combined switching unit S2c shows away from the output-side housing end wall and the drive-side housing end wall 14c out.
  • FIG. 5 shows a fourth exemplary embodiment of a multistage transmission
  • the multistage transmission comprises a transmission input shaft 10d, four along a main axis of rotation 1 1d arranged one behind the other
  • the first planetary gear P1 d has a sun gear P1 1d, a planet P12d and a ring gear P13d.
  • the second switching unit S2d is designed as a combined switching unit and associated with the first planetary gear P1d, which is formed as an input stage, whereby the first planetary gear P1d is formed as one of the combined switching unit S2d associated planetary gear.
  • Gear housing 18d which comprises a drive-side housing end wall 14d and a housing peripheral wall 20d.
  • the first switching unit S1d is designed as a clutch and has a first rotatable coupling element S1 1d and a second rotatable coupling element S12d, the first rotatable coupling element S1 1d permanently non-rotatably connected to the transmission input shaft 10d and the second rotatable coupling element S12d permanently rotatably with the planet P12d the planetary gear P1d associated with the combined switching unit S2d is connected.
  • the combined switching unit S2d is formed as a brake and has a rotatable coupling element S21d, which is fixed to the housing connectable on.
  • the combined switching unit S2d further comprises a Reib gleich 12d and a parallel to Reib gleich 12d connected
  • Forming unit 13d which are each provided to the rotatable
  • the combined switching unit S2d comprises an inner disk carrier 16d, which is non-rotatably connected to the rotatable coupling element S21d, and an outer disk carrier 15d, which is arranged fixed to the housing.
  • the combined switching unit S2d comprises a first actuating unit 29d, which is provided for actuating the friction-locking unit 12d, and a second actuating unit 29d
  • Actuator 30d which is provided for actuating the form-locking unit 13d.
  • the first switching unit S1d has an actuating unit 31d, which is provided for actuating a friction-locking unit 22d of the first switching unit S1d.
  • the second operating unit 30d of the combined switching unit S2d and the operating unit 31d of the first switching unit S1d are located axially between the drive side
  • the second operating unit 30d of the combined switching unit S2d is connected to the housing peripheral wall 20d.
  • the second operating unit 30d of the combined switching unit S2d is connected to the housing peripheral wall 20d.
  • Actuator 30d also be connected to the housing end wall 14d.
  • the second operating unit 30d of the combined switching unit S2d is at the
  • Form-fitting unit 13d are both operatively disposed between the housing peripheral wall 20d and the rotatable coupling member S21d.
  • the operating unit 31d of the first switching unit S1d is disposed radially inside the second operating unit 30d of the combined switching unit S2d.
  • the second operating unit 30d of the combined switching unit S2d radially surrounds the
  • Forming unit 13d of the combined switching unit S2d It is the

Landscapes

  • General Engineering & Computer Science (AREA)
  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Physics & Mathematics (AREA)
  • Fluid Mechanics (AREA)
  • Structure Of Transmissions (AREA)
  • Mechanical Operated Clutches (AREA)
  • Control Of Transmission Device (AREA)
  • Retarders (AREA)
  • General Details Of Gearings (AREA)
  • Motor Or Generator Frames (AREA)
  • Connection Of Motors, Electrical Generators, Mechanical Devices, And The Like (AREA)
  • Hydraulic Clutches, Magnetic Clutches, Fluid Clutches, And Fluid Joints (AREA)
  • Multiple-Way Valves (AREA)
  • Gear-Shifting Mechanisms (AREA)

Abstract

L'invention concerne une boîte de vitesses à plusieurs étages, destiné à un véhicule automobile, qui comprend un arbre d'entrée de boîte de vitesses (10a ; 10b ; 10c ; 10d) servant à la liaison solidaire en rotation d'un moteur à combustion interne, comprenant au moins quatre étages à roues planétaires (P1a, P2a, P3a, P4a ; P1b, P2b, P3b, P4b ; P1c ; P1d) disposés les uns derrière les autres le long d'un axe de rotation principal (11a ; 11b ; 11c ; 11d) et comprenant au moins une unité de changement de rapport combinée (S2a ; S2b ; S2c ; S2d), laquelle est configurée en tant que frein et possède un élément d'accouplement rotatif (S21a ; S21b ; S21c ; S21d) ainsi qu'une unité à maintien par friction (12a ; 12b ; 12c ; 12d) ainsi qu'une unité à coopération de formes (13a ; 13b ; 13c ; 13d) montée en parallèle avec l'unité à maintien par friction (12a ; 12b ; 12c ; 12d), lesquelles sont respectivement conçues pour solidariser l'élément d'accouplement rotatif (S21a ; S21b ; S21c ; S21d) avec le carter. L'un des étages à roues planétaires (P1a ; P1b ; P1c ; P1d) est associé à l'unité de changement de rapport combinée (S2a ; S2b ; S2c ; S2d) et comprend un élément d'engrenage (P12a ; P12b ; P12c ; P12d) qui est fixé à demeure et solidaire en rotation de l'élément d'accouplement rotatif (S21a ; S21b ; S21c ; S21d) de l'unité de changement de rapport combinée (S2a ; S2b ; S2c ; S2d). L'étage à roues planétaires (P1a ; P1b ; P1c ; P1d) qui est associé à l'unité de changement de rapport combinée (S2a ; S2b ; S2c ; S2d) comprend un élément d'engrenage supplémentaire (P11a ; P11b ; P11c ; P11d) qui est fixé à demeure et solidaire en rotation de l'arbre d'entrée de boîte de vitesses (10a ; 10b ; 10c ; 10d).
EP14730753.2A 2013-06-22 2014-06-17 Boîte de vitesses à plusieurs étages pour véhicule automobile Withdrawn EP3011200A1 (fr)

Applications Claiming Priority (3)

Application Number Priority Date Filing Date Title
DE102013010523 2013-06-22
DE102013011553.1A DE102013011553A1 (de) 2013-06-22 2013-07-11 Mehrstufengetriebe für ein Kraftfahrzeug
PCT/EP2014/001648 WO2014202210A1 (fr) 2013-06-22 2014-06-17 Boîte de vitesses à plusieurs étages pour véhicule automobile

Publications (1)

Publication Number Publication Date
EP3011200A1 true EP3011200A1 (fr) 2016-04-27

Family

ID=52010231

Family Applications (4)

Application Number Title Priority Date Filing Date
EP14723331.6A Active EP3011199B1 (fr) 2013-06-22 2014-05-07 Boîte de vitesses à plusieurs étages
EP14744764.3A Not-in-force EP3011196B1 (fr) 2013-06-22 2014-06-13 Dispositif de transmission pour véhicule automobile
EP14730753.2A Withdrawn EP3011200A1 (fr) 2013-06-22 2014-06-17 Boîte de vitesses à plusieurs étages pour véhicule automobile
EP14730754.0A Active EP3011195B1 (fr) 2013-06-22 2014-06-17 Dispositif d'accouplement pour véhicule automobile

Family Applications Before (2)

Application Number Title Priority Date Filing Date
EP14723331.6A Active EP3011199B1 (fr) 2013-06-22 2014-05-07 Boîte de vitesses à plusieurs étages
EP14744764.3A Not-in-force EP3011196B1 (fr) 2013-06-22 2014-06-13 Dispositif de transmission pour véhicule automobile

Family Applications After (1)

Application Number Title Priority Date Filing Date
EP14730754.0A Active EP3011195B1 (fr) 2013-06-22 2014-06-17 Dispositif d'accouplement pour véhicule automobile

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US (4) US10323697B2 (fr)
EP (4) EP3011199B1 (fr)
JP (2) JP6144830B2 (fr)
CN (3) CN105229337B (fr)
DE (5) DE102013011569A1 (fr)
WO (4) WO2014202166A1 (fr)

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DE102013011553A1 (de) 2014-12-24
WO2014202166A1 (fr) 2014-12-24
JP2016524682A (ja) 2016-08-18
DE102013011555A1 (de) 2014-12-24
CN105324587A (zh) 2016-02-10
US20160201765A1 (en) 2016-07-14
US20160138706A1 (en) 2016-05-19
US20160160936A1 (en) 2016-06-09
EP3011196A2 (fr) 2016-04-27
JP6144830B2 (ja) 2017-06-07
DE102013011569A1 (de) 2014-12-24
CN105324591A (zh) 2016-02-10
WO2014202195A2 (fr) 2014-12-24
DE102013011566A1 (de) 2014-12-24
EP3011199A1 (fr) 2016-04-27
EP3011195A1 (fr) 2016-04-27
EP3011195B1 (fr) 2019-03-27
US10323697B2 (en) 2019-06-18
WO2014202210A1 (fr) 2014-12-24
CN105229337A (zh) 2016-01-06
WO2014202211A1 (fr) 2014-12-24
US20160146309A1 (en) 2016-05-26
CN105324587B (zh) 2017-07-07
CN105229337B (zh) 2018-02-06
CN105324591B (zh) 2017-08-25
EP3011196B1 (fr) 2019-04-17
JP6190050B2 (ja) 2017-08-30
US9939028B2 (en) 2018-04-10
EP3011199B1 (fr) 2017-03-22
WO2014202211A8 (fr) 2016-03-24
DE102013011567A1 (de) 2014-12-24
US9964159B2 (en) 2018-05-08
US9624985B2 (en) 2017-04-18
JP2016522375A (ja) 2016-07-28
WO2014202195A3 (fr) 2015-05-07

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