EP3365581A1 - Boîte de vitesses multi-étagée à changement de vitesse en charge de construction planétaire, en particulier pour une propulsion par moteur à combustion interne et/ou par moteur électrique d'un véhicule automobile - Google Patents

Boîte de vitesses multi-étagée à changement de vitesse en charge de construction planétaire, en particulier pour une propulsion par moteur à combustion interne et/ou par moteur électrique d'un véhicule automobile

Info

Publication number
EP3365581A1
EP3365581A1 EP16774957.1A EP16774957A EP3365581A1 EP 3365581 A1 EP3365581 A1 EP 3365581A1 EP 16774957 A EP16774957 A EP 16774957A EP 3365581 A1 EP3365581 A1 EP 3365581A1
Authority
EP
European Patent Office
Prior art keywords
switching element
gear
shaft
gear member
planetary gear
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Withdrawn
Application number
EP16774957.1A
Other languages
German (de)
English (en)
Inventor
Stefan Beck
Marc Seeberger
Michael Wechs
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 EP3365581A1 publication Critical patent/EP3365581A1/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Withdrawn legal-status Critical Current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
    • F16H3/666—Gearings having three or more central gears composed of a number of gear trains without drive passing from one train to another with intermeshing orbital gears
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B60—VEHICLES IN GENERAL
    • B60K—ARRANGEMENT OR MOUNTING OF PROPULSION UNITS OR OF TRANSMISSIONS IN VEHICLES; ARRANGEMENT OR MOUNTING OF PLURAL DIVERSE PRIME-MOVERS IN VEHICLES; AUXILIARY DRIVES FOR VEHICLES; INSTRUMENTATION OR DASHBOARDS FOR VEHICLES; ARRANGEMENTS IN CONNECTION WITH COOLING, AIR INTAKE, GAS EXHAUST OR FUEL SUPPLY OF PROPULSION UNITS IN VEHICLES
    • B60K6/00—Arrangement or mounting of plural diverse prime-movers for mutual or common propulsion, e.g. hybrid propulsion systems comprising electric motors and internal combustion engines
    • B60K6/20—Arrangement or mounting of plural diverse prime-movers for mutual or common propulsion, e.g. hybrid propulsion systems comprising electric motors and internal combustion engines the prime-movers consisting of electric motors and internal combustion engines, e.g. HEVs
    • B60K6/22—Arrangement or mounting of plural diverse prime-movers for mutual or common propulsion, e.g. hybrid propulsion systems comprising electric motors and internal combustion engines the prime-movers consisting of electric motors and internal combustion engines, e.g. HEVs characterised by apparatus, components or means specially adapted for HEVs
    • B60K6/36—Arrangement or mounting of plural diverse prime-movers for mutual or common propulsion, e.g. hybrid propulsion systems comprising electric motors and internal combustion engines the prime-movers consisting of electric motors and internal combustion engines, e.g. HEVs characterised by apparatus, components or means specially adapted for HEVs characterised by the transmission gearings
    • B60K6/365—Arrangement or mounting of plural diverse prime-movers for mutual or common propulsion, e.g. hybrid propulsion systems comprising electric motors and internal combustion engines the prime-movers consisting of electric motors and internal combustion engines, e.g. HEVs characterised by apparatus, components or means specially adapted for HEVs characterised by the transmission gearings with the gears having orbital motion
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B60—VEHICLES IN GENERAL
    • B60K—ARRANGEMENT OR MOUNTING OF PROPULSION UNITS OR OF TRANSMISSIONS IN VEHICLES; ARRANGEMENT OR MOUNTING OF PLURAL DIVERSE PRIME-MOVERS IN VEHICLES; AUXILIARY DRIVES FOR VEHICLES; INSTRUMENTATION OR DASHBOARDS FOR VEHICLES; ARRANGEMENTS IN CONNECTION WITH COOLING, AIR INTAKE, GAS EXHAUST OR FUEL SUPPLY OF PROPULSION UNITS IN VEHICLES
    • B60K6/00—Arrangement or mounting of plural diverse prime-movers for mutual or common propulsion, e.g. hybrid propulsion systems comprising electric motors and internal combustion engines
    • B60K6/20—Arrangement or mounting of plural diverse prime-movers for mutual or common propulsion, e.g. hybrid propulsion systems comprising electric motors and internal combustion engines the prime-movers consisting of electric motors and internal combustion engines, e.g. HEVs
    • B60K6/42—Arrangement or mounting of plural diverse prime-movers for mutual or common propulsion, e.g. hybrid propulsion systems comprising electric motors and internal combustion engines the prime-movers consisting of electric motors and internal combustion engines, e.g. HEVs characterised by the architecture of the hybrid electric vehicle
    • B60K6/48—Parallel type
    • B60K6/485—Motor-assist type
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H3/00—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion
    • F16H3/44—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion using gears having orbital motion
    • F16H3/62—Gearings having three or more central gears
    • F16H3/66—Gearings having three or more central gears composed of a number of gear trains without drive passing from one train to another
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H3/00—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion
    • F16H3/44—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion using gears having orbital motion
    • F16H2003/447—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion using gears having orbital motion without permanent connection between the set of orbital gears and the output
    • 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
    • F16H2200/0052—Transmissions for multiple ratios characterised by the number of forward speeds the gear ratios comprising six 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
    • F16H2200/2007—Transmissions using gears with orbital motion characterised by the number of sets of orbital gears with two 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
    • F16H2200/2048—Transmissions using gears with orbital motion characterised by the engaging friction means not of the freewheel type, e.g. friction clutches or brakes with seven 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 power-shiftable multi-speed transmission in planetary design, in particular for an internal combustion engine and / or electric motor drive of a motor vehicle.
  • Such a multi-speed transmission is usually referred to as an automatic transmission or automatic transmission. It is used for example in the drive train of motor vehicles and allows an automated circuit of its gears.
  • multistage transmissions In the case of motor vehicles, such multistage transmissions have hitherto been used primarily in the premium segment.
  • the multi-speed transmissions meanwhile have a relatively large number of gear stages in order to meet the requirement of a reduced CO 2 emission of the motor vehicle.
  • the multi-stage transmissions are thus spatially relatively constructive.
  • the underlying transmission concepts are relatively complex and therefore complicated and expensive.
  • An embodiment of the invention has for its object to provide a multi-step transmission of the type mentioned, which is compact, easy to drive and easy and inexpensive to implement, for example, to use it in small and / or compact cars.
  • the multistage transmission is suitable for an internal combustion engine and / or electric motor drive, for example, of a motor vehicle.
  • the multistage transmission is designed for connection to an internal combustion engine and / or an electric machine.
  • the multi-speed transmission may be part of a pure internal combustion engine drive or a pure electric motor drive or be the transmission of a hybrid drive.
  • the multistage transmission has a drive shaft as a first shaft and an output shaft as a second shaft. Furthermore, the multi-speed transmission has two planetary gear sets which are coupled or can be coupled to one another and which each have at least one first gear element, one second gear element and one third gear element. In addition, the multi-speed transmission has a plurality of the planetary gear sets associated switching elements, the selective switching causes the respective gear ratios zuêtdes transmission ratio between the drive shaft and the output shaft.
  • the multi-speed transmission is a simple structure.
  • the planetary gear sets themselves allow for a compact design of the transmission.
  • At least three of the switching elements are designed as a brake, by means of which the 1st gear member or the 2nd gear member or the 3rd gear member of the planetary gear sets against a housing-fixed component directly or indirectly, for example via at least one intermediate member, can be braked.
  • the brake elements designed as a switching elements of the gear members of the planetary gear sets directly or indirectly braked are designed as a brake, by means of which the 1st gear member or the 2nd gear member or the 3rd gear member of the planetary gear sets against a housing-fixed component directly or indirectly, for example via at least one intermediate member.
  • the switching elements can be controlled in a structurally and technically simple manner, because operating-medium-conducting lines for actuating these switching elements can be arranged coming from the housing.
  • the resource lines can thereby at least partially on short ways be led out of the housing of the multi-speed transmission.
  • this is the resource supply for the switching element easily accessible from the outside.
  • the multi-speed transmission due to the relatively high number of switching elements, which are designed as a brake, the multi-speed transmission, at least in the axial direction with respect to the space to realize relatively compact.
  • the housing-fixed component may be a part of the housing of the multi-speed transmission, for example by being integrally formed on the housing. Also, the housing-fixed component may be a separate component, which is fixed to the housing with the housing of the multi-speed transmission, for example, is releasably connected.
  • the switching elements as a form-locking switching element, in particular jaw switching element, are formed.
  • the switching element is relatively inexpensive to implement.
  • positive-locking switching elements can be made relatively compact, for example, when the switching elements are present as a claw switching element and, for example, relatively small diameter can be realized. It is thereby possible, at least in the axial direction, a compact construction of the multistage transmission, in particular if the multistage transmission is to be constructed on a relatively small diameter.
  • the at least one of the positive switching elements designed as a brake switching element, by means of which the 1st gear member or the 2nd gear member or the 3rd gear member of the planetary gear sets against the housing-fixed component is directly or indirectly braked.
  • the at least two switching elements can be designed as a frictional, but not friction-capable switching element, in particular to thereby withstand dynamic low stresses stand.
  • Such a switching element may be a band brake or a dry clutch or the like switching element, for example by a steel to steel friction pair is brought into operative contact against each other. This also favors a compact design of the multi-speed transmission.
  • a possible mechanical structure of the multi-speed transmission is that with respect to the first planetary gearset the 1st gear member with a third shaft, the 2nd gear member with the drive shaft and the 3rd gear member are rotatably connected to a fourth shaft, and with respect to the second planetary gear 1.
  • gear member with a fifth shaft, the 2nd gear member with the fourth shaft and the 3rd gear member are rotatably connected to a sixth shaft. It is thereby realized a mechanically relatively simple system structure with only two planetary gear sets.
  • a possible interconnection of the components of the multi-speed transmission can be realized according to an embodiment of the invention such that the third shaft via a first switching element, the fourth shaft via a second switching element and the sixth shaft via a third switching element each with the housing-fixed component or a housing-fixed component are operatively connected, in particular rotatably connected.
  • the first switching element, the second switching element and the third switching element form the switching elements described above, which are designed as a brake. It makes sense in this possible interconnection, that the drive shaft via a fourth switching element with the fifth shaft, the output shaft via a fifth
  • Switching element with the fourth wave and / or via a sixth switching element with the sixth shaft and the third shaft are operatively connected via a seventh switching element with the fifth shaft, in particular rotatably connected.
  • the fourth switching element, the fifth switching element, the sixth switching element and the seventh switching element thus act with respect to rotatable components and serve insofar as a coupling.
  • the selectively switchable forward gears are realized according to an embodiment of the invention in that in a 1st forward gear, the third switching element, the fourth switching element and the fifth switching element are closed, the third switching element, the fifth switching element and the seventh switching element closed in a 2nd forward gear are in a 3rd forward the fourth switching element, the fifth switching element and the seventh switching element are closed, in a fourth forward, the first switching element, the fourth switching element and the fifth switching element are closed, in a fifth forward the first switching element, the Fourth switching element and the sixth switching element are closed and in a sixth forward gear, the first switching element, the sixth switching element and the seventh switching element are closed.
  • the gear ratios for forward travel can be realized with a harmonic series of translations.
  • a high ride comfort can be achieved with low fuel consumption and high drive power.
  • the 3rd forward gear is a direct gear.
  • the selectively switchable reverse gear is realized according to a further embodiment of the invention in that in the reverse gear, the second switching element, the fourth switching element and the sixth switching element are closed. Thereby is to realize the reverse gear with a translation, which is suitable for use of the multi-speed transmission in small and / or compact car.
  • the second switching element and / or the third switching element and / or the fifth switching element are designed as a form-locking switching element, in particular jaw switching element.
  • the switching elements described above, which are designed as a brake, at least by the second switching element and / or the third switching element and / or the fifth switching element are formed.
  • the switching element is relatively inexpensive to implement.
  • positive-locking switching elements can be made relatively compact, for example, when the switching elements are present as a claw switching element and, for example, relatively small diameter can be realized.
  • the second switching element and / or the third switching element and / or the fifth switching element may be formed as a frictional, but not friction-able switching element, in particular to thereby keep dynamic low stresses stand.
  • a switching element may be a band brake or a dry clutch or the like switching element, for example by a steel to steel friction pair is brought into operative contact against each other. This also favors a compact design of the multi-speed transmission.
  • the double switching element has a neutral position in which both individual switching elements are opened.
  • the double switching element then has, for example, three switching positions, a first switching position for closing the one switching element, a second switching position for closing the other switching element, the preceding switching element in turn being opened and a third switching position, which is represented by the neutral position. ment is formed.
  • this measure also aims to achieve a compact design of the multi-speed transmission. By reducing to a double switching element at least a separate switching element is saved.
  • the planetary gear sets are designed as a minus gear, in particular in each case as a negative gear or minus planetary gear set. It can be provided that the
  • gear member a sun gear
  • the 2nd gear member is a planet carrier, in particular web
  • the 3rd gear member is a ring gear
  • the second planetary gear set may be designed as a plus transmission.
  • the positive planetary gear set is realized by the 1st gear member is a sun gear, the 2nd gear member a ring gear and the 3rd gear member is a planet carrier, in particular web.
  • the remaining planetary gear is then designed as a negative gear, in which the 1st gear member is a sun gear, the 2nd gear member is a planet carrier and the 3rd gear member is a ring gear.
  • the drive shaft or the first shaft and the output shaft or the second shaft are coaxial with each other.
  • the multistage transmission is suitable for installation in a vehicle in which the drive train extends in the vehicle longitudinal direction.
  • Such a coaxial arrangement of the drive shaft and the output shaft can be realized in a simple manner if, according to one embodiment of the invention, the transmission input side provided drive shaft or transmission input shaft for non-rotatable connection to an output shaft of an engine and the transmission output side provided output shaft or transmission output shaft for non-rotatable tethering a drive train of a motor vehicle are formed and in the axial direction With respect to the transmission input shaft and starting from the transmission input shaft, the order of the second planetary gear set, the first planetary gear set is provided.
  • the drive shaft and the output shaft may be offset from each other.
  • the drive input side provided drive shaft or transmission input shaft for rotationally fixed connection to an output shaft of an engine and the transmission output side provided output shaft or transmission output shaft are designed for rotationally fixed connection to a drive train of a motor vehicle and in the axial direction with respect to the transmission input shaft and Starting from the transmission input shaft, the order of the first planetary gear set, second planetary gear set is provided.
  • a starting element is provided. This makes it easier to start a motor vehicle. It can be provided that the starting element is separate and, for example, upstream of the planetary gear sets.
  • the starting element may be formed by a torque converter, a dry clutch or wet clutch or have.
  • one of the switching elements of the multi-speed transmission is usable as a starting element.
  • an additional starting element can be saved, so that there are advantages in terms of cost and space requirements.
  • the switching element which can be used as a starting element is designed as a frictionally engaged switching element, in particular a friction clutch.
  • the fourth shift element as Anfahrele- ment is usable. This is advisable because the fourth shift element for the 1st forward gear is closed or can be closed. The same applies to the reverse gear.
  • the third shaft or the fourth shaft or the fifth shaft or the sixth shaft is usable as a further drive shaft which is operatively connected, for example via a separating clutch with another drive.
  • the further drive can be an electric machine.
  • the further drive shaft can also be formed by the drive shaft itself. If, for example, the drive shaft is operatively connected via a separating clutch with an internal combustion engine and an electric motor is provided as a further drive, the further drive or the electric machine is entrained when the internal combustion engine is coupled via a separating clutch with the drive shaft.
  • a further embodiment of the invention is that a torsional vibration decoupling unit is provided, which is connected upstream of the planetary gear sets.
  • the invention proposes a multistage transmission with a simple structure and relatively few mechanical components, which only requires two planetary gear sets for a total of seven gear stages. For this purpose, seven switching elements may be provided, of which three switching elements are connected per gear stage.
  • the multi-speed transmission has a good gear ratio, good gear efficiency with low transmission losses and low component load.
  • Fig. 3 shows another embodiment of a power-shiftable multi-speed transmission, for example, for an internal combustion engine drive of a motor vehicle, with two minus planetary gear sets and an off-axis to a drive shaft arranged output shaft in a schematic representation and
  • Fig. 1 shows - in a schematic representation - a possible embodiment of a power-shiftable multi-speed transmission 100, which can be used for example in a drive train of a motor vehicle.
  • the multi-speed transmission 100 has a drive shaft 1 as a first shaft and an output shaft 2 as a second shaft.
  • the drive shaft 1 is arranged on the transmission input side and forms a transmission input shaft.
  • the output shaft 2 is arranged gear output side and forms a transmission output shaft.
  • the drive shaft 1 can be drive-connected or drive-connected to a drive machine (not shown in FIG. 1), such as an internal combustion engine or an electric machine, for example, to be rotatably connected to an output shaft of the drive machine or to be non-rotatably connected.
  • the prime mover may comprise a hybrid drive with an internal combustion engine and an electric machine, wherein the internal combustion engine and the electric machine with the drive shaft 1 is drive-connected.
  • the direction of action resulting from the coupling of the drive machine to the drive shaft 1 for the force flow entering the multistage transmission 100 and the force flow issuing from the multistage transmission 100 are indicated by the arrows A and B.
  • the multi-speed transmission 100 is constructed in Planetenradbauweise with only two planetary gear sets and has a first planetary gearset RS1 and a second planetary gearset RS2, which may be arranged for example within a common housing.
  • Each planetary gear set RS1 or RS2 has a 1st gear member 1.1 or 2.1, a 2nd gear member 1.2 or 2.2 and a 3rd gear member 1.3 or 2.3.
  • the multi-speed transmission 100 has seven, preferably a total of seven switching elements, namely a first switching element 10, a second switching element 20, a third switching element 30, a fourth switching element 40, a fifth switching element 50, a sixth switching element 60 and a seventh switching element 70, their selective switching a gear ratio between the drive shaft 1 and the output shaft 2, which is appropriate for the respective gear steps, is effected.
  • the switching elements 10, 20, 30, 40, 50, 60 and 70 and the planetary gear sets RS1 and RS2 are arranged as follows:
  • the 1st gear member 1.1 with a third shaft 3 With respect to the first planetary gear set RS1, the 1st gear member 1.1 with a third shaft 3, the 2nd gear member 1.2 with the drive shaft 1 and the third gear member 1.3 with a fourth shaft four rotatably connected.
  • the 1st gear element 2.1 with a fifth shaft 5 With regard to the second planetary gear set RS2, the 1st gear element 2.1 with a fifth shaft 5, the 2nd gear member 2.2 with the fourth shaft 4 and the 3rd gear member 2.3 rotatably connected to a sixth shaft 6.
  • the fourth switching element 40, the fifth switching element 50, the sixth switching element 60 and the seventh switching element 70 thus each act against rotatable components and serve insofar as a coupling.
  • the second switching element 20 and / or the third switching element 30 and / or the fifth switching element 50 as a form-locking switching element, for example in claw design, or as a dynamically low-stressed switching element, such as a band brake trained.
  • a dynamically low-stressed switching element basically any frictional switching element is possible, which is not frictionable.
  • the switching element may also be a dry clutch, which has, for example, a steel-on-steel friction pairing.
  • the second switching element 20 and the third switching element 30 may be formed by a common double switching element. By actuating the double switching element, either the second switching element 20 can be closed or the third switching element 30 can be closed.
  • the double switching element also has a neutral position, in which then neither the second switching element 20 or the third switching element 30 is closed.
  • the second switching element 20 and the fifth switching element 50 may be embodied in a common double switching element.
  • This double switching element can be provided with a neutral position, so that in a first position, the second switching element 20 is closed and the fifth switching element 50 is still open, in a second switch position, the second switching element 20 is open and the fifth switching element 50 is closed and in a third switch position, namely the neutral position, the second switching element 20 and the fifth switching element 50 are opened.
  • the first planetary gearset RS1 and the second planetary gearset RS2 are each designed as a minus gear.
  • the multistage transmission 100 is suitable for a drive train running continuously in the vehicle longitudinal direction.
  • the drive shaft 1 and the output shaft 2 are arranged coaxially with each other.
  • FIG. 2 shows a tabular overview of possible gears which can be selectively switched with the multi-speed transmission 100 and the switching combinations with respect to the first shifting element 10, the second shifting element 20, the third shifting element 30, the fourth shifting element 40, the fifth shifting element 50 Then, of the seven available gear stages, six gear stages may be selectively shifted as forward gears and one reverse gear selected.
  • each switching element 10 or 20 or 30 or 40 or 50th 60 or 70 is assigned a separate column It is indicated by crosses that the respectively associated switching element 10 or 20 or 30 or 40 or 50 or 60 or 70 is present in a closed switch position.
  • the 1st forward speed is by closing the third shift element 30, the fourth shift element 40 and the fifth shift element 50
  • the second forward speed is by closing the third shift element 30, the fifth shift element 50 and the seventh shift element 70
  • the third forward gear is through Closing the fourth switching element 40
  • the fifth switching element is achieved by closing the first shift element 10, the fourth shift element 40 and the fifth shift element 50
  • the fifth forward speed is achieved by closing the first shift element 10
  • the sixth forward speed is switched by closing the first switching element 10, the sixth switching element 60 and the seventh switching element 70.
  • the reverse gear is switched by closing the second switching element 20, the fourth switching element 40 and the sixth switching element 60.
  • FIG. 3 shows a further possible embodiment of a power-shiftable multistage transmission 200.
  • Components of the multistage transmission 200 which are identical or functionally identical to components of the multistage transmission 100 according to FIG. 1 are provided with the same reference numerals; In this respect, reference is made to the description of the multi-stage transmission 100 according to FIG. 1.
  • the multi-speed transmission 200 according to FIG. 2 differs from the multi-ratio transmission 100 according to FIG. 1 in that the multi-speed transmission 200 is suitable for front-transverse installation or rear-transverse installation in a motor vehicle.
  • the drive shaft 1 and the output shaft 2 are offset from each other.
  • the arrangement of the planetary gear sets RS1 and RS2 to each other in such a way that in the axial direction with respect to the drive shaft 1 and starting from the drive shaft 1, the order of the first planetary gearset RS1, second planetary gear set RS2 is provided.
  • FIG. 4 shows a multi-stage transmission 200 'modified from the multi-stage transmission 200 according to FIG. 3.
  • the modification consists in that the multi-stage transmission 200 'according to FIG. 4 has a planetary gear set which is designed as a plus or a plus planetary gearset.
  • the second planetary gear set RS2 is designed as a plus transmission.
  • the 1st gear member 2.1 is a sun gear
  • the 3rd gear member 2.3 a planet carrier, in particular web.
  • the first planetary gearset RS1 is - as in the multi-stage transmission 200 according to FIG. 3 - trained as a minus tune.
  • the 2nd gear member 1.2 a planet carrier, in particular web
  • the multi-stage transmissions 100, 200 and 200 'described in the preceding figures can be operated according to the switching matrix according to FIG. 2 and as described above for FIG. 1.
  • the multi-speed transmissions 100, 200 and 200 'each have two planetary gear sets, seven shift elements, of which three shift elements are used as brakes and the remaining four shift elements as clutches and of which three shift elements are to be switched simultaneously to shift a gear. Furthermore, the multi-stage transmissions 100, 200 and 200 'each have six forward gears and one reverse gear.
  • Designation drive shaft (first shaft)

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  • General Engineering & Computer Science (AREA)
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  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Transportation (AREA)
  • Structure Of Transmissions (AREA)

Abstract

L'invention concerne une boîte de vitesses multi-étagée à changement de vitesse en charge de construction planétaire, en particulier pour une propulsion par moteur à combustion interne et/ou par moteur électrique d'un véhicule automobile, comprenant plusieurs rapports de marche avant et un rapport de marche arrière et comprenant un arbre d'entraînement (1) en tant que premier arbre et un arbre de sortie (2) en tant que deuxième arbre, deux trains d'engrenages planétaires (RS1, RS2) accouplés ou pouvant être accouplés l'un à l'autre, lesquels comprennent respectivement au moins un premier organe de transmission (1.1, 2.1), un deuxième organe de transmission (1.2, 2.2) et un troisième organe de transmission (1.3, 2.3), et plusieurs éléments de changement de vitesse (10, 20, 30, 40, 50, 60, 70) associés aux trains d'engrenages planétaires (RS1, RS2), dont la commutation sélective produit un rapport de transmission entre l'arbre d'entraînement (1) et l'arbre de sortie (2) qui se rapporte au rapport de vitesse respectif. Selon l'invention, au moins trois des éléments de changement de vitesse (10, 20, 30, 40, 50, 60, 70) sont réalisés sous forme de freins, au moyen desquels le premier organe de transmission (1.1, 2.1) ou le deuxième organe de transmission (1.2, 2.2) ou le troisième organe de transmission (1.3, 2.3) des trains d'engrenages planétaires (RS1, RS2) peuvent être freiné directement ou indirectement contre un élément structural (G) solidaire du carter. En variante ou en plus, au moins deux des éléments de changement de vitesse (10, 20, 30, 40, 50, 60, 70) sont réalisés sous forme d'élément de changement de vitesse à complémentarité de formes, en particulier sous forme d'élément de changement de vitesse à griffe.
EP16774957.1A 2015-10-23 2016-10-04 Boîte de vitesses multi-étagée à changement de vitesse en charge de construction planétaire, en particulier pour une propulsion par moteur à combustion interne et/ou par moteur électrique d'un véhicule automobile Withdrawn EP3365581A1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102015220753.6A DE102015220753A1 (de) 2015-10-23 2015-10-23 Lastschaltbares Mehrstufengetriebe in Planetenbauweise, insbesondere für einen verbrennungsmotorischen und/oder elektromotorischen Antrieb eines Kraftfahrzeuges
PCT/EP2016/073603 WO2017067777A1 (fr) 2015-10-23 2016-10-04 Boîte de vitesses multi-étagée à changement de vitesse en charge de construction planétaire, en particulier pour une propulsion par moteur à combustion interne et/ou par moteur électrique d'un véhicule automobile

Publications (1)

Publication Number Publication Date
EP3365581A1 true EP3365581A1 (fr) 2018-08-29

Family

ID=57044972

Family Applications (1)

Application Number Title Priority Date Filing Date
EP16774957.1A Withdrawn EP3365581A1 (fr) 2015-10-23 2016-10-04 Boîte de vitesses multi-étagée à changement de vitesse en charge de construction planétaire, en particulier pour une propulsion par moteur à combustion interne et/ou par moteur électrique d'un véhicule automobile

Country Status (5)

Country Link
US (1) US20180306280A1 (fr)
EP (1) EP3365581A1 (fr)
CN (1) CN107923495A (fr)
DE (1) DE102015220753A1 (fr)
WO (1) WO2017067777A1 (fr)

Families Citing this family (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102016015302A1 (de) * 2016-12-22 2018-06-28 Daimler Ag Gruppengetriebevorrichtung

Family Cites Families (13)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2838960A (en) * 1956-10-01 1958-06-17 Howard W Simpson Tractor transmission
US3031901A (en) * 1959-09-23 1962-05-01 Howard W Simpson Twelve speed power shift planetary transmission
US5692988A (en) * 1996-05-24 1997-12-02 Ford Global Technologies, Inc. Multiple-speed automatic transmission for an automotive vehicle
FR2770601B1 (fr) * 1997-11-06 1999-12-03 Renault Boite de vitesse mecanique de vehicule automobile
US5984825A (en) * 1998-03-10 1999-11-16 General Motors Corporation Power transmission with two simple planetary gearsets
US6056665A (en) * 1998-10-09 2000-05-02 General Motors Corporation Five speed planetary transmission
US6165097A (en) * 1999-11-22 2000-12-26 General Motors Corporation Powertrain with a six speed planetary transmission
EP1491794B1 (fr) * 2002-03-29 2012-08-22 Aisin Aw Co., Ltd. Transmission automatique
US7699745B2 (en) * 2006-05-25 2010-04-20 Gm Global Technology Operations, Inc. Multi-speed transmissions with a long pinion and one fixed interconnection
JP4481273B2 (ja) * 2006-05-30 2010-06-16 ジヤトコ株式会社 有段自動変速機の変速機構
US7442145B2 (en) * 2006-06-02 2008-10-28 Gm Global Technology Operations, Inc. Multi-Speed transmissions with a long pinion
DE102007022776A1 (de) * 2007-05-15 2008-12-04 Zf Friedrichshafen Ag Mehrstufengetriebe
DE102014204009A1 (de) * 2014-03-05 2015-09-10 Schaeffler Technologies AG & Co. KG Mehrgängiges Planetengetriebesystem als Komponente des Antriebsstrangs eines Kraftfahrzeuges

Also Published As

Publication number Publication date
WO2017067777A1 (fr) 2017-04-27
US20180306280A1 (en) 2018-10-25
CN107923495A (zh) 2018-04-17
DE102015220753A1 (de) 2017-04-27

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