EP3164622A1 - Transmission multi-vitesse pour véhicules ferroviaires - Google Patents

Transmission multi-vitesse pour véhicules ferroviaires

Info

Publication number
EP3164622A1
EP3164622A1 EP15727375.6A EP15727375A EP3164622A1 EP 3164622 A1 EP3164622 A1 EP 3164622A1 EP 15727375 A EP15727375 A EP 15727375A EP 3164622 A1 EP3164622 A1 EP 3164622A1
Authority
EP
European Patent Office
Prior art keywords
shaft
switching element
gear
transmission
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Withdrawn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
EP15727375.6A
Other languages
German (de)
English (en)
Inventor
Kazutaka Iuchi
Michael Wechs
Stefan Beck
Viktor Warth
Bernd Somschor
Benedikt Reick
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 EP3164622A1 publication Critical patent/EP3164622A1/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Withdrawn legal-status Critical Current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
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B61—RAILWAYS
    • B61C—LOCOMOTIVES; MOTOR RAILCARS
    • B61C9/00—Locomotives or motor railcars characterised by the type of transmission system used; Transmission systems specially adapted for locomotives or motor railcars
    • 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
    • F16H3/46—Gearings having only two central gears, connected by orbital gears
    • F16H3/48—Gearings having only two central gears, connected by orbital gears with single orbital gears or pairs of rigidly-connected orbital gears
    • F16H3/52—Gearings having only two central gears, connected by orbital gears with single orbital gears or pairs of rigidly-connected orbital gears comprising orbital spur gears
    • F16H3/54—Gearings having only two central gears, connected by orbital gears with single orbital gears or pairs of rigidly-connected orbital gears comprising orbital spur gears one of the central gears being internally toothed and the other externally toothed
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B60—VEHICLES IN GENERAL
    • B60Y—INDEXING SCHEME RELATING TO ASPECTS CROSS-CUTTING VEHICLE TECHNOLOGY
    • B60Y2400/00—Special features of vehicle units
    • B60Y2400/42—Clutches or brakes
    • B60Y2400/421—Dog type clutches or brakes
    • 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
    • F16H37/00—Combinations of mechanical gearings, not provided for in groups F16H1/00 - F16H35/00
    • F16H37/02—Combinations of mechanical gearings, not provided for in groups F16H1/00 - F16H35/00 comprising essentially only toothed or friction gearings
    • F16H37/04—Combinations of toothed gearings only
    • F16H2037/047—Combinations of toothed gearings only comprising one or more orbital gear sets coaxial with a first shaft and having more than one drive connection to a second shaft parallel to the first shaft
    • 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
    • F16H2200/0034—Transmissions for multiple ratios characterised by the number of forward speeds the gear ratios comprising two forward speeds
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H2200/00—Transmissions for multiple ratios
    • F16H2200/003—Transmissions for multiple ratios characterised by the number of forward speeds
    • F16H2200/0039—Transmissions for multiple ratios characterised by the number of forward speeds the gear ratios comprising three 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
    • F16H2200/2005—Transmissions using gears with orbital motion characterised by the number of sets of orbital gears with one 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
    • F16H2200/2002—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
    • F16H2200/2033—Transmissions using gears with orbital motion characterised by the engaging friction means not of the freewheel type, e.g. friction clutches or brakes with one 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
    • F16H2200/2035—Transmissions using gears with orbital motion characterised by the engaging friction means not of the freewheel type, e.g. friction clutches or brakes with two 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
    • F16H2200/2038—Transmissions using gears with orbital motion characterised by the engaging friction means not of the freewheel type, e.g. friction clutches or brakes with three 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
    • F16H2200/2041—Transmissions using gears with orbital motion characterised by the engaging friction means not of the freewheel type, e.g. friction clutches or brakes with four 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
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H2200/00—Transmissions for multiple ratios
    • F16H2200/20—Transmissions using gears with orbital motion
    • F16H2200/2097—Transmissions using gears with orbital motion comprising an orbital gear set member permanently connected to the housing, e.g. a sun wheel permanently connected to the housing

Definitions

  • the invention relates to a switchable multi-speed transmission for rail vehicles, in particular electric multiple units, so-called electrical multiple units (EMU).
  • EMU electrical multiple units
  • Rail vehicles are characterized by the fact that they drive or are guided on one or more rails.
  • multiple units are in this context as well to call locomotives.
  • the trainset Under a train train is usually to understand a non-separable unit of several vehicles / train segments, the trainset has an on-board drive.
  • a vehicle / train segment, several vehicles / Switzerlandsemente or all vehicles / train segments of the railcar each have a drive.
  • EMU electric multiple units
  • DMU diesel-powered multiple units
  • DMU diesel multiple units
  • These have one or more on-board diesel engines instead of electric motors in electric multiple units (EMU).
  • DE1 177671 B discloses a drive control for rail traction vehicles, in particular for bogie locomotives.
  • the rail traction vehicles have at least one reversible electric drive motor, which is in each case operatively connected to a positive-locking transmission.
  • an electric drive motor with a positive gear is arranged on each bogie of the railcar.
  • Via a gear selector a gear is preselected at a rear derailleur of two possible gears (first gear, second gear).
  • a piston rod is actuated in such a way that a rotationally fixed connection with the desired transmission ratio between the electric drive motor and the output takes place by means of a shift fork connected to the piston rod.
  • the positive gear each have two paired gear pairs in engagement.
  • the idler gears are arranged on the drive shaft and the fixed gears on the output shaft, wherein the drive shaft is positioned above the output shaft.
  • the present invention has for its object to provide a multi-speed transmission, especially for rail vehicles, through which the drive train of the rail vehicle can be operated with a higher efficiency, in particular, the multi-speed transmission has a high efficiency at the same time small dimensions.
  • the object is achieved with a multi-speed transmission according to the patent claim 1. Further advantages and advantageous embodiments will become apparent from the dependent claims.
  • the multi-speed transmission includes at least one transmission input and a transmission output, and at least one planetary gear, a switching element and a housing.
  • a planetary gear or a planetary gear set generally comprises at least one sun gear, a planet carrier and a ring gear. Are rotatably mounted on the planet carrier planetary gears, which mesh with the toothing of the sun gear and / or with the toothing of the ring gear.
  • the at least one planetary gearset preferably has at least one sun gear, one or more planet gears, a planet carrier and a ring gear.
  • a negative planetary gear set preferably describes a single planetary gear set with a planet carrier on which the planetary gears are rotatably mounted, with a sun gear and with a ring gear, wherein the teeth of at least one of the planet gears both with the teeth of the sun gear, and with the teeth of the ring gear meshes, whereby the ring gear and the sun gear rotate in opposite directions of rotation when the sun gear rotates with a fixed planetary carrier.
  • a plus planetary gear set differs from the minus planetary gear set just described in that the plus planetary gear set has inner and outer planetary gears rotatably supported on the planetary carrier.
  • the toothing of the inner planet gears meshes on the one hand with the teeth of the sun gear and on the other hand with the teeth of the outer planetary gears.
  • the gearing The outer planetary gears also meshes with the teeth of the ring gear.
  • planetary gear sets particularly compact multi-speed transmission can be realized, whereby a large freedom in the arrangement of the multi-speed transmission is achieved in the rail vehicle.
  • the elements of a planetary gear set are understood in particular to mean the sun gear, the ring gear, the planet carrier and the planet wheels of the planetary gear set.
  • a rotational movement in the multi-speed transmission can be introduced, and by operating the at least one switching element at least two different ratios between the transmission input and the transmission output can be displayed.
  • a multi-speed transmission is preferably characterized in that a translation of a rotational speed or a torque takes place from a transmission input to a transmission output taking into account different transmission ratios.
  • the transmission input is preferably arranged on one side of the transmission, which faces a drive element, for example an internal combustion engine or electric motor.
  • the transmission output is preferably located on a side opposite the transmission input side of the transmission, for example, in coaxial arrangement with the transmission input or in parallel shifted arrangement.
  • embodiments are also conceivable in which the transmission input and the transmission output are arranged on the same side of the multi-speed transmission.
  • a transmission input describes a location on a multi-speed transmission, at which a rotational movement, for example, by a drive element, is introduced into the multi-speed transmission.
  • a transmission output designates a location of the multi-speed transmission, at which the rotational movement introduced at the transmission input is discharged from the multi-speed transmission taking into account the respective transmission ratio.
  • gears that is, different ratios, switchable.
  • a brake is to be understood as meaning a switching element which is connected on one side to a stationary element, for example a housing, and on another side to a rotatable element, for example a shaft or a toothed wheel.
  • a non-actuated brake is understood to mean an opened brake.
  • the rotatable element is in free-running, that is to say that the brake preferably has no influence on a rotational speed of the rotatable element.
  • the brake is actuated or closed, the rotational movement of the rotatable element is reduced, for example, to a standstill, that is, a rotationally fixed connection can be produced between the rotatable element and the stationary element.
  • a non-rotatable connection can preferably be produced or separable in a form-fitting or frictionally engaged manner.
  • a force is usually introduced via an actuator in the connection point, whereby a frictional force arises, by which a force or torque between the rotatable element and the fixed element transferable, so a solid connection can be produced.
  • the actuator may be electromotive, pneumatic, electro-hydraulic, electromagnetic or otherwise operable.
  • Positive connections In positive connections, a connection takes place due to an engagement of a contour of the two elements. Positive connections have the particular advantage that they can transmit high forces and moments with comparatively small dimensions and weight. In addition, the energy to be applied for the connection is much lower than in frictional connections, whereby, for example, the actuator can be made smaller.
  • brakable to understand that by pressing the brake differential speed between the two elements can be reduced and can be performed up to the standstill of the rotatable element.
  • actuating a frictionally engaged brake By actuating a frictionally engaged brake, a transition from a rotational movement of the rotatable element to a reduction of this rotational movement up to standstill is thus possible. Conversely, a gradual increase in a rotational movement, for example, from a standstill of the rotatable element out, realized.
  • a positive brake only the states standstill or unrestrained rotation of the rotatable element can be realized.
  • Couplings describe in contrast to brakes switching elements, which, depending on the operating state, allow a relative movements between two elements or constitute a connection for transmitting a torque or a force.
  • a relative movement for example, to understand a rotation of two elements, wherein the rotational speed of the first element and the rotational speed of the second element differ from each other.
  • the rotation of only one of the two elements is conceivable, while the other element is stationary or rotating in the opposite direction.
  • a non-actuated clutch is understood to mean an opened clutch. This means that a relative movement between the two elements is possible.
  • the clutch When the clutch is actuated or closed, the two elements accordingly rotate at the same speed in the same direction of rotation.
  • Couplings can, in analogy to the above-described embodiment of brakes, be designed as frictionally engaged or form-locking shifting elements.
  • the at least one switching element is designed as a double switching element.
  • a double switching element is characterized for example by the fact that through this a first rotatable element with a second rotatable element, or the second rotatable element with a third rotatable element is connectable, this double switching element in this case has only a single actuator.
  • the double switching element may also have another switching state, namely that of a neutral state. Position. This means that no connection is made between the first element and the second element, nor between the second element and the third element.
  • the multi-speed transmission has a first planetary gearset and a second planetary gearset. Furthermore, a rotational movement into the multi-speed transmission can preferably be introduced at the transmission input via a drive shaft. Under a drive shaft is in particular a shaft to understand, which is preferably arranged on the transmission input. Through this, a rotational movement, for example a drive element, in the multi-speed transmission can be introduced in an advantageous manner.
  • a shaft is not to be understood hereinafter exclusively as an example cylindrical, rotatably mounted machine element for transferring torques, but this is also general connecting elements to understand that connect individual components or elements together, in particular connecting elements that connect a plurality of elements rotation with each other.
  • a shaft further designates a mechanical component provided with a defined rigidity, by means of which preferably torques or rotational movements between two or more components connected to the shaft can be transmitted.
  • torques or rotational movements between two or more components connected to the shaft can be transmitted.
  • translational movements that is to say movements caused by tensile or compressive forces, for example along a rotation axis of a shaft.
  • two elements instead of a shaft or other connecting element also directly, for example by a welding, screwing, gluing, clamping or plug connection, be connected to each other.
  • a one-piece design of elements to be connected is conceivable.
  • Two elements are in particular referred to as connected to each other if there is a fixed, in particular rotationally fixed connection between the elements. In particular, such connected elements rotate at the same speed in the same direction of rotation.
  • Two elements are referred to as connectable, if between these elements a releasable, non-rotatable connection can be produced. In particular, such elements, when connected, rotate at the same speed in the same direction of rotation.
  • the drive shaft is connected to the sun gear of the first planetary gear set.
  • the planet carrier of the first planetary gear set is preferably connected via a third shaft with the ring gear of the second planetary gear set.
  • the ring gear of the first planetary gear set is preferably connected via a fourth shaft to the switching element, while a fifth shaft is further connected via the switching element to the housing and via an output shaft, the switching element is connected to the planet carrier of the second planetary gear set.
  • the switching element is either the fifth shaft with the fourth shaft, or the output shaft connected to the fourth shaft.
  • the sun gear of the second planetary gear set is connected via a sixth shaft to the housing.
  • the state ratio indicates the ratio between the sun and ring gear when the planet carrier is fixed.
  • the first gear can be realized that is connected by the switching element, the fourth shaft to the fifth shaft.
  • the second gear can be realized that is connected by the switching element, the output shaft to the fourth shaft.
  • An output shaft is preferably understood to mean a shaft which is arranged in particular in a region of the transmission output of the multi-gear transmission.
  • a rotary motion generated by a drive element and transmitted or reduced by the multi-speed transmission is forwarded via the output shaft, for example, the drive of a vehicle axle or of a wheel thereby takes place.
  • this has a first planetary gear set and a second planetary gear set, wherein a rotational movement in the multi-speed transmission can be introduced at the transmission input via the drive shaft.
  • the drive shaft is further preferably connected to the sun gear of the first planetary gear set.
  • the transmission output is preferably connected via the output shaft to the planet carrier of the first planetary gear set, wherein the planet carrier of the second planetary gear set is further preferably connected via the output shaft with the ring gear of the second planetary gear set.
  • the ring gear of the first planetary gear set is connected via a third shaft to the switching element, via a fourth shaft, the switching element is connected to the housing and via a fifth shaft, the switching element is connected to the planet carrier of the second planetary gear set.
  • the switching element either the fourth wave with the third wave, or the third wave with the fifth wave connectable.
  • the sun gear of the second planetary gear set is connected via a sixth shaft to the housing.
  • the first gear can be represented that is connected by the switching element, the fourth shaft to the third shaft.
  • the second gear can be represented by the third element being connected to the fifth shaft by the formwork element.
  • the multi-speed transmission has a first planetary gearset and a second planetary gearset, wherein a rotational movement in the multi-speed transmission can preferably be introduced at the transmission input via a drive shaft.
  • the drive shaft is connected to the sun gear of the first planetary gear set and further to the sun gear of the second planetary gear set.
  • the ring gear of the first planetary gear set is connected via a fourth shaft to the housing.
  • the planet carrier of the first planetary gear set is preferably connected via a third shaft
  • Switching element connected, while via a fifth shaft, the switching element is connected to the ring gear of the second planetary gear set and via a sixth shaft, the switching element is connected to the housing.
  • the switching element are preferably either the third shaft and the fifth shaft or the fifth shaft and the sixth shaft connected to each other.
  • the planet carrier of the second planetary gear set is connected via an output shaft to the transmission output.
  • the first forward gear is thereby representable that the switching element connects the fifth and the sixth shaft with each other.
  • the second gear is represented by the fact that the third shaft is connected to the fifth shaft by the switching element.
  • the gear ratio of the second gear i 2.129.
  • the multi-speed transmission has a first planetary gearset and a second planetary gearset, wherein a rotational movement in the multi-speed transmission can be introduced at the transmission input via a drive shaft.
  • the drive shaft is connected to the ring gear of the first planetary gear set.
  • the planet carrier of the first planetary gear set is preferably connected via an output shaft to the transmission output and further to the ring gear of the second planetary gear set.
  • the sun gear of the first planetary gear set is connected via a fourth shaft to the switching element, wherein at over a fifth shaft, the switching element is connected to the sun gear of the second planetary gear set and via a sixth shaft, the switching element is connected to the housing.
  • the switching element is preferably either the fifth shaft with the fourth shaft or the fourth shaft with the sixth shaft connectable.
  • the first gear can be represented by the fourth shaft being connected to the fifth shaft by the shifting element.
  • the second gear can be represented by the fact that the fourth shaft is connected to the sixth shaft.
  • the multi-speed transmission to a first switching element and second switching element wherein at the transmission input via a drive shaft, a rotational movement in the multi-speed transmission can be introduced.
  • the drive shaft is connected to the first switching element and further to the second switching element, via a third shaft, the first switching element is advantageously connected to the ring gear of the first planetary gear and via a fourth shaft, the first switching element is connected to the housing.
  • the second switching element is connected via a fifth shaft to the sun gear of the planetary gear and via a sixth shaft, the second switching element is connected to the housing.
  • the second switching element By the second switching element, either the fifth shaft with the drive shaft or the fifth shaft with the sixth shaft is connected in a preferred manner.
  • the planet carrier of the planetary gear set is preferably connected via an output shaft to the transmission output.
  • three different ratios between the transmission input and transmission output can be displayed in an advantageous manner.
  • the state ratio of the planetary gear set i 0 i -1, 620.
  • the first gear is preferably represented by the fact that by the first switching element, the drive shaft with the third shaft and through the second switching element, the fifth shaft is connected to the sixth shaft.
  • the second gear is preferably represented by the fact that the third shaft with the fourth shaft and by the second switching element, the drive shaft is connected to the fifth shaft by the first switching element.
  • the third gear can be represented by the fact that the drive shaft is connected to the third shaft by the first switching element and the drive shaft to the fifth shaft by the second switching element.
  • the multi-speed transmission has a first planetary gearset, a second planetary gearset, a first shifting element and a second shifting element.
  • a rotational movement in the multi-speed transmission can be introduced at the transmission input in an advantageous manner via a drive shaft.
  • the drive shaft is connected to the first switching element and further to the planet carrier of the first planetary gear set.
  • the first switching element is preferably connected to the ring gear of the second planetary gear set and the sun gear of the first planetary gear set.
  • the switching element is further connected to the housing, wherein by the first switching element particularly preferably either the drive shaft with the third shaft or the third shaft with the fourth shaft is connectable.
  • the ring gear of the first planetary gear set is connected via a fifth shaft to the second switching element and further to the sun gear of the second planetary gear set.
  • the second switching element is further connected to the housing, wherein the fifth shaft can be connected to the sixth shaft by the second switching element.
  • the planet carrier of the second planetary gear set is connected via an output shaft to the transmission output.
  • the second gear can be represented by the fact that the drive shaft and the third shaft are connected to each other by the first switching element.
  • the third gear can be represented by the fact that the fifth shaft and the sixth shaft are connected to each other by the second switching element.
  • the multi-speed transmission has a first planetary gearset, a second planetary gearset, a first shifting element and a second shifting element.
  • a rotational movement in the multi-speed transmission can be introduced.
  • the drive shaft is preferably connected to the first switching element and further to the sun gear of the first planetary gear set.
  • the first switching element is further preferably connected via a third shaft to the ring gear of the first planetary gear set and further to the second switching element.
  • the first switching element is preferably connected to the housing, wherein either the drive shaft with the third shaft or the third shaft with the fourth shaft is preferably connectable by the first switching element.
  • the planet carrier of the first planetary gear set is connected via an output shaft to the ring gear of the second planetary gear set and further to the transmission output.
  • the second switching element is connected via a fifth shaft to the planet carrier of the second planetary gear set, wherein the third shaft can be connected to the fifth shaft by the second switching element.
  • the sun gear of the second planetary gear set is connected via a sixth shaft to the housing.
  • the first gear is preferably represented by that is connected by the first switching element, the third wave with the fourth wave.
  • the second gear can be represented that is connected by the second switching element, the fifth shaft to the third shaft.
  • the third gear is preferably represented by the first switching element, in which by the first switching element, the drive shaft is connected to the third shaft.
  • the multi-speed transmission on a first planetary gear, a second planetary gear, a first switching element and a second switching element wherein at the transmission input via a drive shaft, a rotational movement in the multi-speed transmission can be introduced.
  • the drive shaft is connected to the sun gear of the first planetary gear set, the sun gear of the second planetary gear set and the second switching element.
  • the planet carrier of the second planetary gear set is preferably connected via an output shaft to the transmission output.
  • the ring gear of the first planetary gear set is connected via a third shaft to the first switching element and further to the planet carrier of the second planetary gear set.
  • the first switching element is further connected via a fourth shaft to the housing, wherein the third shaft can be connected to the fourth shaft by the first switching element.
  • the ring gear of the second planetary gear set is connected via a fifth shaft to the second switching element and the second switching element via a hexagonal shaft connected to the housing.
  • the second switching element is preferably either the fifth shaft with the sixth shaft, or the fifth shaft connected to the drive shaft.
  • the first gear is preferably represented by the third shaft is connected to the fourth shaft by the first switching element.
  • the second gear is preferably represented by the second switching element such that the fifth shaft is connected to the sixth shaft.
  • the third gear is preferably represented by the second switching element such that the drive shaft is connected to the fifth shaft.
  • the multi-speed transmission has a first planetary gearset, a second planetary gearset, a first shift element and a second shift element, wherein a rotational movement in the multi-speed transmission can be introduced at the transmission input via a drive shaft.
  • the drive shaft is connected to the first switching element and further to the sun gear of the first planetary gear set and further to the sun gear of the second planetary gear set.
  • the first switching element via an output shaft to the transmission output and further connected to the planet carrier of the first planetary gear set.
  • the drive shaft is preferably connectable to the output shaft.
  • the ring gear of the first planetary gear set is preferably connected via a third shaft to the second switching element.
  • the second switching element is further connected via a fourth shaft to the housing and via a fifth shaft preferably connected to the planet carrier of the second planetary gear set.
  • the second switching element is preferably either the fourth wave with the third wave or the third wave with the fifth wave connectable.
  • the ring gear of the second planetary gear set is connected via a sixth shaft to the housing.
  • the first gear is preferably represented by the fourth shaft is connected to the third shaft by the second switching element.
  • the second gear is preferably represented by the third shaft is connected to the fifth shaft by the second switching element.
  • the multi-speed transmission on a first planetary gear, a second planetary gear, a first switching element and a second switching element wherein at the transmission input via a drive shaft, a rotational movement in the multi-speed transmission can be introduced.
  • the drive shaft is connected to the first switching element and further to the sun gear of the first planetary gear set.
  • the first switching element is preferably connected via a fourth shaft to the housing and via a third shaft to the ring gear of the first planetary gear set and further to the planet carrier of the second planetary gear set.
  • the first switching element is preferably either the drive shaft to the third shaft, or the third shaft connected to the fourth shaft.
  • the ring gear of the second planetary gear set is connected via an output shaft to the planet carrier of the first planetary gear set and further to the transmission output.
  • the sun gear of the second planetary gear set is connected via a fifth shaft to the second switching element and the second switching element via a sixth shaft to the housing.
  • the second switching element is preferably the fifth shaft connected to the sixth shaft.
  • the first gear is more preferably represented by the fact that the third shaft and the fourth shaft are interconnected by the first switching element.
  • the second gear is more preferably represented by the fact that the fifth shaft and the sixth shaft are interconnected by the second switching element.
  • the third gear is preferably represented by the fact that the drive shaft is connected to the third shaft by the first switching element.
  • the multi-speed transmission has a first planetary gearset, a second planetary gearset, a first shifting element and a second shifting element.
  • a rotational movement in the multi-speed transmission can be introduced via a drive shaft.
  • the drive shaft is connected to the first switching element and further to the sun gear of the first planetary gear set.
  • the first switching element is preferably further connected to the housing and via a third shaft to the ring gear of the first planetary gear set.
  • the first switching element is also connected to the second switching element, wherein by the first switching element in a preferred manner, either the drive shaft with the third shaft, or the third shaft with the fourth shaft is connectable.
  • the planet carrier of the first planetary gear set is connected via a fifth shaft with the ring gear of the second planetary gear set.
  • the planet carrier of the second planetary gear set is preferably connected via an output shaft to the second switching element and further to the transmission output. By the second switching element, the output shaft is connected to the third wave in a preferred manner.
  • the sun gear of the second planetary gear set is preferably connected via a sixth shaft to the housing.
  • the first gear is preferably represented by the third shaft is connected to the fourth shaft by the first switching element.
  • the second gear is advantageously represented by the fact that the third shaft and the output shaft are interconnected by the second switching element.
  • the third gear is preferably represented by the fact that the drive shaft and the third shaft are interconnected by the first switching element.
  • the multi-speed transmission has a first planetary gearset, a second planetary gearset, a first shifting element and a second shifting element.
  • At the transmission input is preferably via a drive shaft, a rotational movement in the multi-speed transmission introduced.
  • the drive shaft is connected to the first switching element and further to the sun gear of the first planetary gear set.
  • the first switching element is preferably connected via a third shaft to the ring gear of the first planetary gear set and a fourth shaft to the housing.
  • the planet carrier of the first planetary gear set is preferably connected via a fifth shaft with the ring gear of the second planetary gear set.
  • the planet carrier of the second planetary gear set is preferably connected via an output shaft to the second switching element and further to the transmission output.
  • the sun gear of the second planetary gear set is connected to the second switching element via a hex shaft and the second switching element is connected to the housing via a seventh shaft.
  • the second switching element is preferably either the sixth shaft with the seventh shaft, or the sixth shaft connected to the output shaft.
  • the third gear can be represented by the fact that the drive shaft is connected to the third shaft by the first switching element.
  • the sixth shaft is connected to the seventh shaft.
  • the fourth gear can be represented that the drive shaft and the third shaft are connected to each other by the first switching element and the sixth shaft and the output shaft are interconnected by the second switching element.
  • the multi-speed transmission has a first planetary gearset, a second planetary gearset, a first shifting element and a second shifting element.
  • the drive shaft is connected to the first switching element and further to the sun gear of the first planetary gear set.
  • the first switching element is connected via a third shaft to the ring gear of the first planetary gear set and a fourth shaft to the housing.
  • the first switching element is preferably either the drive shaft with the third shaft or the third shaft with the fourth shaft connectable.
  • the planet carrier of the first planetary gear set is connected via a fifth shaft to the planet carrier of the second planetary gear set.
  • the ring gear of the second planetary gear set is preferably connected via an output shaft to the transmission output and further to the second switching element.
  • the second switching element is preferably connected via a sixth shaft to the sun gear of the second planetary gear set and a seventh shaft to the housing.
  • By the second switching element is preferably either the output shaft with the sixth shaft, or the sixth shaft connected to the seventh shaft.
  • the first gear can be represented by the third shaft and the fourth shaft are interconnected by the first switching element and the output shaft and the sixth shaft are interconnected by the second switching element.
  • the multi-speed transmission has a first planetary gearset, a second planetary gearset, a first shifting element and a second shifting element.
  • At the transmission input is preferably via a drive shaft, a rotational movement in the multi-speed transmission introduced.
  • the drive shaft is further preferably connected to the first switching element and further to the planet carrier of the first planetary gear set.
  • the first switching element is connected via a third shaft to the sun gear of the first planetary gear set and via a fourth shaft to the housing.
  • the first switching element is preferably either the drive shaft with the third shaft or the third shaft with the fourth shaft connectable.
  • the ring gear of the first planetary gear set via a fifth shaft with the sun gear of the second planetary gear set connected.
  • the transmission output is connected via an output shaft to the planet carrier of the second planetary gear set and further to the second switching element. More preferably, the second switching element via a sixth shaft to the ring gear of the second planetary gear set and further connected via a seventh shaft to the housing.
  • the second switching element is preferably either the seventh shaft with the sixth shaft, or the sixth shaft connected to the output shaft.
  • the first gear is preferably represented by the drive shaft is connected to the third shaft by the second switching element and the sixth shaft is connected to the seventh shaft by the second switching element.
  • the increment between the third gear and the fourth gear is preferably 1.59.
  • the multi-speed transmission on a planetary gear and a switching element At the transmission input, a rotational movement into the multi-speed transmission is preferably via a drive shaft. be conducted.
  • the drive shaft is further preferably connected to the ring gear of the planetary gear set.
  • the planet carrier of the planetary gear set is preferably connected via an output shaft to the transmission output and further to the switching element.
  • the switching element is preferably connected via a third shaft to the sun gear of the planetary gear set and a fourth shaft to the housing. It is connected by the switching element either the output shaft to the third shaft, or the third shaft to the fourth shaft, whereby two different ratios between the transmission input and transmission output can be displayed.
  • the transmission ratios are to be selected such that the incremental steps between the individual gears are largely the same.
  • the increments between the individual gears should not be set too high, since this leads to large speed differences in the transmission or on the shifting elements, resulting in pre-losses and increased wear.
  • the gears in the just described multi-gear transmission arrangements each have the same direction of rotation with each other, this means that there is no reversal of the direction of rotation between the gears.
  • a corresponding number of forward or reverse gears are preferably provided by the described multi-speed transmission, depending on the initiated rotational movement by the drive element / the drive elements.
  • the mentioned ratios are mentioned as examples. There are also other Ganggetnebean glovesen conceivable with deviating gear ratios or state translations.
  • gear stage may be, for example, a spur gear, but also a translation by means of a chain or belt drive is quite conceivable. Also arrangements with bevel gears are conceivable.
  • Figure 1 A schematic representation of a first embodiment of a multi-gear transmission according to the invention
  • Figure 2 is a schematic representation of a second embodiment of a multi-gear transmission according to the invention.
  • Figure 3 is a schematic representation of a third embodiment of a multi-gear transmission according to the invention.
  • Figure 4 is a schematic representation of a fourth embodiment of a multi-gear transmission according to the invention.
  • Figure 5 is a schematic representation of a fifth embodiment of a multi-gear transmission according to the invention.
  • Figure 6 is a schematic representation of a sixth embodiment of a multi-speed transmission according to the invention
  • Figure 7 is a schematic representation of a seventh embodiment of a multi-speed transmission according to the invention.
  • FIG. 8 shows a schematic illustration of an eighth embodiment of a multispeed transmission according to the invention.
  • Figure 9 is a schematic representation of a ninth embodiment of a multi-gear transmission according to the invention.
  • FIG. 10 shows a schematic representation of a tenth embodiment of a multispeed transmission according to the invention.
  • Figure 1 1 is a schematic representation of an eleventh embodiment of a multi-gear transmission according to the invention.
  • Figure 12 is a schematic representation of a twelfth embodiment of a multi-gear transmission according to the invention.
  • Figure 13 is a schematic representation of a thirteenth embodiment of a multi-gear transmission according to the invention.
  • Figure 14 is a schematic representation of a fourteenth embodiment of a multi-gear transmission according to the invention.
  • FIG. 15 to FIG. 18 are identical to FIG. 15 to FIG. 18:
  • FIG. 19 to FIG. 24 are identical to FIG. 19 to FIG. 24:
  • FIG. 25 to FIG. 28 in schematic representations of further arrangements of the second embodiment of a multi-gear transmission according to the invention.
  • FIG. 29 to FIG. 31 is a diagrammatic representation of FIG. 29 to FIG. 31.
  • FIGS. 32 to 34 are identical to FIGS. 32 to 34:
  • FIG. 35 to FIG. 36 is a diagrammatic representation of FIG. 35 to FIG. 36.
  • FIG. 37 to FIG. 42 are identical to FIG. 37 to FIG. 42:
  • FIGS. 43 to 45 are identical to FIGS. 43 to 45:
  • FIG. 46 to FIG. 49 are identical to FIG. 46 to FIG. 49:
  • FIG. 50 to FIG. 52 are identical to FIG. 50 to FIG. 52:
  • FIG. 53 to FIG. 58 in schematic representations of further arrangements of the tenth embodiment of a multi-gear transmission according to the invention.
  • FIG. 59 to FIG. 62 are identical to FIG. 59 to FIG. 62:
  • FIGS. 63 to 65 are identical to FIGS. 63 to 65.
  • FIG. 66 to FIG. 68 are identical to FIG. 66 to FIG. 68:
  • Figure 69 is a schematic representation of a fifteenth embodiment of a multi-speed transmission according to the invention.
  • FIG. 70 shows a schematic representation of a further arrangement of the fifteenth embodiment of a multi-gear transmission according to the invention.
  • the multi-gear transmission 9 has a first planetary gearset PR1, a second planetary gearset PR2 and a first shifting element SE1.
  • the first switching element SE1 is arranged between the first planetary gearset PR1 and the second planetary gearset PR2.
  • a sun gear S1 of the first planetary gear set PR1 is connected to a drive shaft 1.
  • a rotational movement in the multi-speed transmission 9 can be introduced.
  • the first planetary gear set PR1 has a first planet carrier PT1 and a first ring gear H1.
  • planet wheels which are rotatable at the first planetary carrier.
  • ger PT1 are arranged.
  • the planet carrier PT1 of the first planetary gear PR1 is connected via a third shaft 3 with a ring gear H2 of the second planetary PR2.
  • the ring gear H1 of the first planetary gear PR1 is connected via a fourth shaft 4 on one side with the first switching element SE1.
  • the first switching element SE1 is connected via a fifth shaft 5 to a housing G.
  • the first switching element SE1 is connected via an output shaft 2 to a transmission output AB and further to a planet carrier PT2 of the second planetary PR2.
  • a sun gear S2 of the second planetary PR2 is connected via a sixth shaft 6 to the housing G.
  • the first switching element SE1 is designed in the present case as a double switching element. This means that with only one actuator depending on the switching position, the fourth shaft 4 is connectable to the fifth shaft 5, or the fourth shaft 4 is connectable to the output shaft 2.
  • the first gear can be produced by virtue of the fact that the fourth shaft 4 is connected to the fifth shaft 5 by the first shifting element SE1.
  • the second gear can be represented by the fact that the fourth shaft 4 is connected to the output shaft 2 by the first shifting element SE1.
  • the transmission output AB is positioned.
  • the transmission output AB is represented by a spur gear.
  • the two planetary gear sets PR1, PR2 are both designed as a minus planetary gear set. In this case, the two planetary PR1, PR2 are arranged coaxially to a rotation axis, not shown, extending through the drive shaft.
  • FIG. 2 shows a second embodiment of the multi-gear transmission 9 according to the invention in a schematic representation.
  • the multi-speed transmission 9 also has a first planetary gearset PR1, a second planetary gearset PR2 and a first shifting element SE1.
  • a sun gear S1 of the first planetary gear set PR1 is connected to a drive shaft 1.
  • a rotational movement in the multi-speed transmission 9 can be introduced.
  • first planetary PR1, first switching element SE1, second planetary PR2 are arranged.
  • the first switching element SE1 is again arranged between the first planetary gearset PR1 and the second planetary gearset PR2.
  • the transmission input AN and the transmission output AB are in the present embodiment on the same side of the multi-speed transmission 9.
  • the transmission output AB is connected to a planet carrier PT1 of the first planetary PR1 and further with a ring gear H2 of the second planetary PR2.
  • a ring gear H1 of the first planetary gear set PR1 is connected via a third shaft 3 to a first side of the first switching element SE1.
  • the first switching element SE1 is connected at a further side via a fourth shaft 4 with a housing G.
  • the first switching element SE1 is connected via a fifth shaft 5 to a planet carrier PT2 of the second planetary gearset PR2.
  • a sun gear S2 of the second planetary PR2 is connected via a sixth shaft 6 to the housing G. This again causes the sun gear S2 of the second planetary PR2 is fixed, that is, that it does not rotate.
  • the first switching element SE1 is again designed as a double switching element. This means that the first switching element SE1 has only one actuator.
  • the first gear can be represented by the fact that the third shaft 3 is connected to the fourth shaft 4 by the first shifting element SE1. This means that the third shaft 3 can be braked or fixed on the housing G via the first switching element SE1 and the fourth shaft 4.
  • the second gear is through representable that the third shaft 3 is connected to the fifth shaft 5 by the first switching element SE1.
  • the planetary gear sets PR1, PR2, the transmission input AN, the transmission output AB, and the first switching element SE1 are all arranged coaxially to a not shown, passing through the drive shaft 1 axis of rotation.
  • FIG 3 shows a schematic representation of a third embodiment of the multi-speed transmission 9 according to the invention.
  • a sun S1 of the first planetary PR1 via the drive shaft 1 with the transmission input AN and the sun gear S2 of the second planetary gear set PR2.
  • the planet carrier PT1 of the first planetary gearset PR1 is connected via the third shaft 3 to the first switching element SE1.
  • the ring gear H1 of the first planetary PR1 is connected via the fourth shaft 4 to the housing G.
  • the first switching element SE1 is connected at a further side via the fifth shaft 5 with the ring gear H2 of the second planetary PR2.
  • the first switching element SE1 is connected to the housing G via the sixth shaft 6.
  • the planet carrier PT2 of the second planetary PR2 is connected via the output shaft 2 to the transmission output AB.
  • the transmission input AN and the transmission output AB are located at respective opposite ends of the multi-speed transmission 9. Between the transmission input and transmission output AB AB are the first planetary PR1, the first switching element SE1 and the second planetary PR2 arranged in the order just mentioned.
  • the first switching element SE1 is again designed as a double switching element.
  • the third shaft 3 with the fifth shaft 5 is connectable.
  • the second gear of the transmission can be displayed.
  • the fifth shaft 5 can be connected to the sixth shaft 6 by the first switching element SE1. Due to the fact that the hexagonal shaft 6 is connected to the housing G, the fifth shaft 5, and thus the ring gear H2 of the second planetary gear set PR2, are included just described switching state of the first switching element SE1 on the housing G braked or fixed. As a result, the first gear of the multi-speed transmission 9 can be displayed.
  • Figure 4 shows a fourth embodiment of the multi-gear transmission 9 of the invention in a schematic representation.
  • the embodiment shown in Figure 4 differs from the already described embodiments of the multi-speed transmission 9 in that at the transmission input, the drive shaft 1 is connected to the ring gear H1 of the first planetary gear set PR1.
  • the planet carrier PT1 of the first planetary gear PR1 is connected via the output shaft 2 to the transmission output AB and further to the ring gear H2 of the second planetary PR2.
  • the sun gear S1 of the first planetary gear PR1 is connected via the fourth shaft 4 with the first switching element SE1.
  • the planet carrier PT2 of the second planetary PR2 is connected via the third shaft 3 to the housing G, that is, the planet carrier PT2 of the second planetary PR2 is fixed, that is, that it does not rotate.
  • the sun gear S2 of the second planetary gearset PR2 is further connected via the fifth shaft 5 to the first switching element SE1. This is also connected via the sixth shaft 6 to the housing G.
  • the first planetary gear set PR1, the transmission output AB, the second planetary PR2 and the first switching element SE1 are arranged starting at the transmission input AN in the order just mentioned.
  • the first gear of the multi-speed transmission 9 can be represented by the fact that the fifth shaft 5 is connected to the fourth shaft 4 by the first shifting element SE1.
  • the second gear of the multi-speed transmission 9 can be represented by the fact that the fourth shaft 4 is connected to the sixth shaft 6, whereby the fourth shaft 4 is braked or fixed to the housing G.
  • the planetary gear sets PR1, PR2, the transmission output AB and the first switching element SE1 are arranged coaxially to a rotation axis of the drive shaft 1, not shown, as already described above.
  • FIG. 5 shows a schematic representation of a fifth embodiment of the multispeed transmission 9 according to the invention.
  • the multi-speed transmission 9 in the present case, a first switching element SE1, a first planetary gear PR1 and a second switching element SE2.
  • the first shifting element SE1, the first planetary gear set PR1, the transmission output AB and the second shifting element SE2 are arranged in the order just mentioned.
  • the drive shaft 1 is connected to the first switching element SE1 and further to the second switching element SE2.
  • the first switching element SE1 is further connected via the third shaft 3 with the ring gear H1 of the first planetary PR1.
  • the first switching element SE1 is connected via the fourth shaft 4 to the housing G.
  • the planet carrier PT1 of the first planetary PR1 is connected via the output shaft 2 to the transmission output AB.
  • the sun gear S1 of the first planetary gear PR1 is connected to the second switching element SE2.
  • the second switching element SE2 is further connected via the sixth shaft 6 to the housing G.
  • the two switching elements SE1, SE2 are each designed as a double switching element.
  • a total of three different transmission ratios, that is three gears through the multi-speed transmission 9 can be displayed.
  • the first gear can be realized by the first switching element SE1
  • the drive shaft 1 is connected to the third shaft 3 and the second switching element S2
  • the fifth shaft 5 is connected to the sixth shaft 6, that is, that the third wave on the housing G is braked or fixed.
  • the second gear can be represented by the third shaft 3 is connected to the fourth shaft 4 by the first switching element, whereby the third shaft 3 is braked or fixed to the housing G.
  • the drive shaft 1 is connected to the fifth shaft 5 by the second switching element SE2.
  • the third speed of the multi-speed transmission 9 can be represented by the fact that the drive shaft 1 is connected to the third shaft 3 by the first shifting element SE1 and the drive shaft 1 is connected to the fifth shaft 5 by the second shifting element SE2.
  • the switching elements SE1, SE2, the first planetary PR1 and the transmission output AB are arranged coaxially to a rotation axis of the drive shaft 1, not shown.
  • FIG. 6 shows a sixth embodiment of the multispeed transmission 9 according to the invention in a schematic representation.
  • a first shifting element SE1, a first planetary gearset PR1, a second planetary gearset PR2, a transmission output AB and a second shifting element SE2 are arranged in the order just mentioned.
  • the transmission input AN is connected to the first switching element SE1 and further to the planet carrier PT1 of the first planetary gearset PR1.
  • the first switching element SE1 is further connected via the third shaft 3 with the sun gear S1 of the first planetary PR1 and the ring gear H2 of the second planetary PR2.
  • the first switching element SE1 is also connected to the housing G.
  • the planet carrier PT2 of the second planetary PR2 is connected via the output shaft 2 to the transmission output.
  • the ring gear H1 of the first planetary gear PR1 is connected via the fifth shaft 5 with the sun gear S2 of the second planetary PR2 and further with the second switching element SE2.
  • the second switching element SE2 is also connected via the sixth shaft 6 to the housing G.
  • the first switching element SE1 is designed as a double switching element.
  • the second gear can be represented by the first switching element SE1 in that the drive shaft 1 is connected to the third shaft 3.
  • the third gear can be represented by the fact that the fifth shaft 5 is connected to the sixth shaft 6 by the second shifting element SE2.
  • the fifth shaft 5 is braked or fixed to the housing G.
  • the switching elements SE1, SE2, the planetary gear sets PR1, PR2, and the transmission output AB are arranged coaxially to a rotation axis of the drive shaft, not shown.
  • FIG. 7 shows a schematic illustration of a seventh embodiment of the multispeed transmission 9 according to the invention.
  • This embodiment differs from the embodiment shown in FIG. 6 in that the drive shaft 1 transmits the transmission input AN to the first shifting element SE1 and further to the sun gear S1 of the first planetary gearset PR1 combines.
  • the first switching element SE1 is on the one hand further connected to the third shaft 3, wherein the third shaft 3 in turn is further connected to the ring gear H1 of the first planetary gear set PR1 and the second switching element SE2.
  • the first switching element SE1 is also connected via the fourth shaft 4 to the housing G.
  • the planet carrier PT1 of the first planetary gear PR1 is connected via the output shaft 2 to the transmission output AB and the ring gear H2 of the second planetary PR2.
  • the planet carrier PT2 of the second planetary PR2 is connected via the fifth shaft 5 with the second switching element SE2.
  • the sun gear S2 of the second planetary PR2 is connected to the housing G.
  • the first gear can be represented by the third shaft 3 is connected to the fourth shaft 4 through the first switching element SE1, whereby the third shaft 3 and the components and elements connected thereto braked or fixed on the housing G via the fourth shaft 4 are.
  • the second gear can be represented by the fact that the fifth shaft 5 is connected to the third shaft 3 by the second shifting element SE2.
  • the third gear can be represented that the drive shaft 1 is connected to the third shaft 3 by the first switching element SE1.
  • the first shift element SE1, the first planetary gear set PR1, the second planetary gear set PR2, the second shift element SE2 and the transmission output AB are starting at the transmission input AN arranged in the order just mentioned.
  • the transmission input AN and the transmission output AB are arranged at respective opposite ends of the multi-speed transmission 9 in a coaxial manner.
  • the switching element SE1, SE2 and the planetary gear PR1, PR2 are also arranged coaxially with a rotation axis of the drive shaft, not shown.
  • Figure 8 shows an eighth embodiment of the multi-gear transmission 9 of the invention in a schematic representation.
  • the second planetary PR2 and the second switching element SE2 are arranged starting at the transmission input AN in the order just mentioned.
  • the second switching element SE2 is designed as a double switching element.
  • the drive shaft 1 is connected to the sun gear S1 of the first planetary PR1, the sun gear S2 of the second planetary PR2 and further to the second switching element SE2.
  • the planet carrier PT1 of the first planetary PR1 is connected via the output shaft 2 to the transmission output AB.
  • the ring gear H1 of the first planetary gear PR1 is connected via the third shaft 3 to the first switching element SE1 and further to the planet carrier PT2 of the second planetary PR2.
  • the first switching element SE1 is further connected via the fourth shaft 4 to the housing G.
  • the ring gear H2 of the second planetary PR2 is connected via the fifth shaft 5 with the second switching element SE2.
  • the second switching element SE2 is further connected to the housing G.
  • the second switching element SE2 is designed as a double switching element. With the present embodiment of the multi-speed transmission 9 three different ratios between the transmission input and transmission output can be displayed.
  • the first gear can be represented that connected by the first switching element SE1, the third shaft 3 with the fourth shaft 4 and the third shaft 3 is thereby braked or fixed to the housing G.
  • the second gear can be represented by the fact that the fifth shaft 5 by means of the second switching element SE2 the sixth shaft 6 is connected and thereby the fifth shaft 5 is braked or fixed to the housing G.
  • the third gear can be represented by the fact that the drive shaft 1 is connected to the fifth shaft 5 by the second shifting element SE2.
  • the planetary gear sets PR1, PR2, the switching elements SE1, SE2 and the transmission output AB are arranged coaxially to a rotation axis of the drive shaft 1, not shown.
  • FIG. 9 shows a diagrammatic representation of a ninth embodiment of multi-speed transmission 9.
  • a first shifting element SE1, a transmission output AB, a first planetary gear set PR1, a second shifting element SE2 and a second planetary gearset PR2 are arranged starting from a transmission input in the order just mentioned.
  • the first switching element SE1, the sun S1 of the first planetary PR1 and the sun S2 of the second planetary PR2 are interconnected.
  • the first switching element SE1 is further connected via the output shaft 2 to the transmission output AB and the planet carrier PT1 of the first planetary PR1.
  • the ring gear H1 of the first planetary gear PR1 is connected via the third shaft 3 with the second switching element SE2.
  • the second switching element SE2 is designed as a double switching element.
  • the first gear can be represented by the third shaft 3 is connected to the fourth shaft 4 through the second switching element SE2, whereby the third shaft 3 is braked or fixed to the housing G.
  • the second gear of the multi-speed transmission 9 can be represented by the second switching element SE2 in that the third shaft 3 is connected to the fifth shaft 5.
  • the third gear of the multi-speed transmission 9 can be represented by the fact that the drive shaft 1 is connected to the output shaft 2 by the first switching element SE1.
  • the switching elements SE1, SE2, the planetary gear sets PR1, PR2 and the transmission output AB are arranged coaxially to a rotation axis of the drive shaft 1, not shown.
  • Figure 10 shows a tenth embodiment of the multi-gear transmission 9 of the invention in a schematic representation.
  • a first shifting element SE1 a first planetary gearset PR1, a second planetary gearset PR2, a second shifting element SE2 and a transmission output AB are arranged in the order just mentioned.
  • the first switching element SE1 is connected to the sun gear S1 of the first planetary PR1.
  • the first switching element SE1 is further connected via a third shaft 3 to the ring gear H1 of the first planetary gear PR1 and the planet carrier PT2 of the second planetary PR2.
  • the first switching element SE1 is further connected to the housing G.
  • the planet carrier PT1 of the first planetary gear PR1 is connected via the output shaft 2 with the ring gear H2 of the second planetary PR2 and the transmission output AB.
  • the sun gear S2 of the second planetary PR2 is connected via the fifth shaft 5 with the second switching element SE2. This is further connected via the sixth shaft 6 to the housing G.
  • the first gear of the multi-speed transmission 9 can be represented by the third shaft 3 is connected to the fourth shaft 4 through the first switching element SE1, and thus the third shaft 3 is braked or fixed to the housing G.
  • the second gear can be represented by the fact that the fifth shaft 5 is connected to the sixth shaft 6 by the second shift element SE2 and thereby the fifth shaft 5 is braked or fixed to the housing G.
  • the third gear can be represented that the drive shaft 1 is connected to the third shaft 3 by the first switching element SE1.
  • the first switching element SE1 is designed as a double switching element.
  • FIG. 11 shows an eleventh embodiment of the multi-speed transmission 9 according to the invention.
  • the embodiment shown in FIG. 11 differs from the embodiment described in FIG. 10 in that the first shifting element SE1 is connected to the ring gear H1 of the first planetary gearset PR1 via the third shaft 3 and further is connected to the second switching element SE2.
  • the first planet carrier PT1 of the first planetary gearset PR1 via the fifth shaft 5 is connected to the ring gear H2 of the second planetary gear set PR2.
  • the planet carrier PT2 of the second planetary PR2 is connected via the output shaft 2 to the second switching element SE2 and further to the transmission output AB.
  • the sun gear S2 of the second planetary PR2 is connected via the sixth shaft 6 to the housing G.
  • the first gear can be represented by the third shaft 3 is connected to the fourth shaft 4 through the first switching element SE1, whereby the third shaft 3 is braked or fixed to the housing G.
  • the second gear can be represented by the fact that the output shaft 2 is connected to the third shaft 3 by the second switching element SE2.
  • the third gear can be represented that the drive shaft 1 is connected to the third shaft 3 by the first switching element SE1.
  • Figure 12 shows a twelfth embodiment of the multi-gear transmission 9 of the invention in a schematic representation.
  • the first shifting element SE1 is connected to the ring gear H1 of the first planetary gearset PR1.
  • the second planet carrier PT2 of the second planetary PR2 is connected via the output shaft 2 to the second switching element SE2 and beyond with the transmission output AB.
  • the second switching element SE2 is designed as a double switching element.
  • the sun gear S2 of the second planetary gear PR2 is also connected to the second switching element SE2. Via a seventh shaft 7, the second switching element SE2 is connected to the housing G.
  • the multi-speed transmission 9 shown here four different ratios between transmission input and transmission output AB AB.
  • the first gear can be represented that connected by the first switching element SE1, the third shaft 3 with the fourth shaft 4 and thereby the third shaft 3 is braked or fixed to the housing G.
  • the sixth shaft 6 is connected to the seventh shaft 7 by the second switching element, whereby the sixth shaft 6 is braked or fixed to the housing G.
  • the second gear can be represented by the third shaft 3 being connected to the fourth shaft 4 again by the first shifting element SE1.
  • the sixth shaft 6 is connected to the output shaft 2 by the second switching element.
  • the third gear can be represented by the fact that the sixth shaft 6 is connected to the seventh shaft 7 by the second shifting element SE2 as in the first gear.
  • the drive shaft 1 is connected to the third shaft 3 by the first switching element SE1.
  • the fourth gear can be represented that the drive shaft 1 is connected to the third shaft 3 by the first switching element SE1.
  • the output shaft 2 is connected to the sixth shaft 6 through the second switching element SE2.
  • Figure 13 shows a thirteenth embodiment of the transmission according to the invention in a schematic representation.
  • a first shifting element SE1 a first planetary gearset PR1, a second planetary gearset PR2, a transmission output AB and a second shifting element SE2 are arranged coaxially to a rotational axis of the drive shaft 1, not shown, in the order just mentioned.
  • the first switching element SE1 Via the drive shaft 1, the first switching element SE1 is connected to the sun gear S1 of the first planetary PR1.
  • the first switching element SE1 is further connected via the third shaft 3 with the ring gear H1 of the first planetary PR1.
  • the first switching element SE1 designed as a double switching element is connected to the housing G via the fourth shaft 4.
  • the planet carrier PT1 of the first planetary gear PR1 is connected via the fifth shaft 5 with the planet carrier PT2 of the second planetary PR2.
  • the ring gear H2 of the second planetary PR2 is connected via the output shaft 2 to the transmission output AB and further to the second switching element SE2.
  • the sun gear S2 of the second planetary gear set PR2 is via the sixth shaft 6 also connected to the second switching element SE2, wherein the running as a double switching element second switching element SE2 is further connected via the seventh shaft 7 to the housing G.
  • the first gear can be realized that connected by the first switching element SE1, the third shaft 3 with the fourth shaft 4 and thus the third shaft 3 is braked or fixed to the housing G.
  • the output shaft 2 is connected to the sixth shaft 6 through the second switching element SE2.
  • the second gear can be represented that the third shaft 3 is again connected to the fourth shaft 4 by the first switching element SE1.
  • the sixth shaft 6 is connected to the seventh shaft 7 and thereby the sixth shaft 6 on the housing G braked or fixed.
  • the third gear can be represented by the fact that the drive shaft 1 is connected to the third shaft 3 by the first switching element SE1 and at the same time the output shaft is connected to the sixth shaft 6 through the second switching element SE2.
  • the fourth gear can be represented by the fact that the drive shaft 1 is again connected to the third shaft 3 by the first shifting element SE1 and at the same time the sixth shaft 6 is connected to the seventh shaft 7 by the second shifting element SE2.
  • FIG. 14 shows a fourteenth embodiment of the multispeed transmission 9 according to the invention.
  • a first shifting element SE1 a first planetary gearset PR1, a transmission output AB, a second planetary gearset PR2 and a second shifting element SE2 are not coaxial with one another in the order just mentioned arranged rotational axis of the drive shaft 1 is arranged.
  • the drive shaft 1 connects the first switching element SE1 with the planet carrier PT1 of the first planetary PR1.
  • the first switching element SE1 is further connected via the third shaft 3 with the sun gear S1 of the first planetary PR1.
  • the executed as a double switching element first switching element SE1 is also connected via the fourth shaft 4 to the housing G.
  • the ring gear H1 of the first planetary PR1 is about the fifth shaft 5 with the sun gear S2 of the second planetary PR2.
  • the ring gear H2 of the second planetary gear set PR2 is connected via the sixth shaft 6 with the second switching element SE2 designed as a double switching element. This is further connected via the seventh shaft 7 to the housing G and on another side via the output shaft 2 to the planet carrier PT2 of the second planetary PR2 and further to the transmission output AB.
  • the first gear can be represented by the first switching element SE1
  • the drive shaft 1 is connected to the third shaft 3
  • the second switching element SE2 the sixth shaft 6 is connected to the seventh shaft 7, whereby the sixth shaft 6 at the housing G is braked or fixed.
  • the second gear can be represented by the fact that the third shaft 3 is connected to the fourth shaft 4 by the first shifting element SE1 and thereby the third shaft 3 can be braked or immobilized on the housing G.
  • the sixth shaft 6 and the seventh shaft 7 are connected to each other as before in first gear.
  • the third gear can be represented by the fact that the drive shaft 1 is connected to the third shaft 3 by the first shifting element SE1 and at the same time the sixth shaft 6 is connected to the output shaft 2 by the second shifting element SE2.
  • the fourth gear can be represented by the fact that the third shaft 3 is connected to the fourth shaft 4 by the first shifting element SE1, as in the second gear, and the sixth shaft 6 is connected to the output shaft 2 by the second shifting element SE2 as before in the third gear ,
  • FIG. 15 shows a schematic representation of an arrangement of the first embodiment of a multi-gear transmission 9 according to the invention in a drive train.
  • a drive element 8 Via a drive element 8, a rotary motion is transmitted to the drive shaft 1. This is introduced into the multi-speed transmission 9.
  • a first spur gear ST1 At the transmission output AB, a first spur gear ST1 is arranged.
  • a first spur gear SR1 of the first spur gear ST1 is connected to the output shaft 2 of the multi-speed transmission 9.
  • a second spur gear SR2 of the first spur gear ST1 is connected to a vehicle axle 10. This is the, by the drive element 8 in the Multi-speed transmission 9 introduced and by this over- or under-set, rotary motion on the vehicle axle 10 and on the associated wheels 1 1 transferable. In this case, carried by the first spur gear ST1 another translation of the rotational movement.
  • Figure 1 6 shows a schematic representation of another arrangement of the first embodiment of the multi-speed transmission according to the invention 9. It could be saved by the second planetary PR2, characterized in that on the planet carrier PT1 of the first planetary gear set a first spur gear ST1 is arranged.
  • a first spur gear SR1 is connected to the planet carrier PT1 of the first planetary gear set PR1. This is in engagement with a second spur gear SR2, wherein the second spur gear SR2 is connected to the vehicle axle 10.
  • a second spur gear ST2 is arranged on the known output shaft 2.
  • a first spur gear SR3 of the second spur gear ST2 is connected to the output shaft 2 and engages with a second spur gear SR4.
  • the second spur gear SR4 of the second spur gear ST2 is also connected to the vehicle axle 10.
  • two different transmission ratios can be displayed in the same way. In this case, a balance between the output via the first spur gear ST1 and the output via the second spur gear ST2 while driving in the multi-speed transmission 9, whereby the vehicle axle 10 is driven.
  • FIG. 17 shows in a schematic representation a further arrangement of the first embodiment of the multispeed transmission 9 according to the invention.
  • the vehicle axle 10 is further connected to wheels 1 1.
  • Figure 18 shows a schematic representation of another arrangement of the first embodiment of the multi-speed transmission 9 according to the invention. This differs from the arrangement shown in Figure 1 6 in that between the drive member 8 and the multi-speed transmission 9, a third spur gear ST3 is arranged. This results in a further reduction or translation of the rotational movement before the multi-speed transmission 9.
  • FIG. 19 shows in a schematic representation a further arrangement of the second embodiment of the multi-gear transmission 9 according to the invention.
  • a first helical gear ST1 is provided on the transmission output AB of the multi-gear transmission 9.
  • the output shaft 2 of the multi-speed transmission 9 is connected to a first spur gear SR1 of the first spur gear ST1.
  • This first spur gear SR1 is engaged with a second spur gear SR2 of the first spur gear ST1 and is connected to the vehicle axle 10, whereby the vehicle axle 10 and the wheels 11 connected thereto are drivable.
  • FIG. 20 shows in a schematic representation a further arrangement of the second embodiment of the multispeed transmission 9 according to the invention.
  • a further translation is thus provided by the second spur gear ST2.
  • FIG. 21 shows in a schematic representation a further arrangement of the second embodiment of the multi-gear transmission 9 according to the invention. This differs from the arrangement shown in FIG. drive element 8 and the multi-speed transmission 9, a second spur gear ST2 is provided. As a result, before the multi-speed transmission 9 is a translation of the speed.
  • FIG. 22 shows a schematic representation of a further arrangement of the second embodiment of the multi-gear transmission 9 according to the invention.
  • the second planetary gear PR2 could be saved by providing a second helical gear ST2 on the fifth shaft 5.
  • a first spur gear SR3 of the second spur gear ST2 is connected, wherein this is in engagement with a second spur gear SR4 of the second spur gear ST2.
  • the vehicle axle 10 is connected to both the first spur gear ST1, and with the second spur gear ST2.
  • a balance is established between the two spur gears ST1, ST2 when driving, so that two different transmission ratios can also be represented with this arrangement.
  • FIG. 23 shows in a schematic representation a further arrangement of the second embodiment of the multispeed transmission 9 according to the invention.
  • the arrangement shown here differs from the arrangement shown in FIG. 22 in that the respectively second spur gear SR2, SR4 of the first spur gear ST1 and the second spur gear ST2 are not connected to the vehicle axle 10, but with an intermediate shaft ZW, wherein on the intermediate shaft ZW a third spur gear ST3 is provided, of which a first spur gear SR5 is connected to the intermediate shaft ZW.
  • the first spur gear SR5 of the third spur gear ST3 meshes with a second spur gear SR6 of the third spur gear ST3 and is connected to the vehicle axle 10.
  • a further gear stage between multi-speed transmission 9 and vehicle axle 10 is provided.
  • FIG. 24 shows a schematic representation of a further arrangement of the second embodiment of the multi-gear transmission 9 according to the invention.
  • the arrangement shown in FIG. 24 differs from the arrangement shown in FIG. Order in that here between the drive element 8 and multi-speed transmission 9, a third spur gear ST3 is provided.
  • FIG. 25 shows in a schematic representation a further arrangement of the third embodiment of the multi-gear transmission 9 according to the invention.
  • a rotational movement is introduced into the multi-gear transmission 9.
  • a first spur gear ST1 is provided, through which the rotational movement of the transmission output AB to the vehicle axle 10 and the associated wheels 1 1 is transferable.
  • FIG. 26 shows in a schematic representation a further arrangement of the third embodiment of the multispeed transmission 9 according to the invention.
  • the second spur gear SR4 of the second spur gear ST2 is further connected to the vehicle axle 10, whereby the rotational movement of the drive element 8 on the vehicle axle 10 and the associated wheels 1 1 is transferable.
  • FIG. 27 shows in a schematic representation a further arrangement of the third embodiment of the multi-gear transmission 9 according to the invention.
  • the arrangement shown here differs from the arrangement shown in FIG. 25 in that a second spur gear ST2 is provided between drive element 8 and multi-gear transmission 9.
  • a second spur gear ST2 is provided between drive element 8 and multi-gear transmission 9.
  • Figure 28 shows a schematic representation of another arrangement of the third embodiment of the multi-speed transmission according to the invention 9. It could thereby be dispensed with the first planetary PR1 that between the drive element 8 and multi-speed transmission 9, a second spur gear ST2 and a third spur gear ST3 are provided.
  • a second spur gear SR4 of the second spur gear ST2 connected to the drive shaft 1 of the multi-gear 9
  • a second spur SR6 of the third spur gear ST3 is connected to the third shaft 3 of the multi-gear 9.
  • a balance of equilibrium arises between the second spur gear ST2 and the third spur gear ST3.
  • two different ratios between the drive element and vehicle axle can also be realized in this arrangement.
  • FIG. 29 shows in a schematic representation a further arrangement of the fourth embodiment of the multispeed transmission 9 according to the invention.
  • the output shaft 2 is connected to the transmission output AB with a first spur gear SR1 of a first spur gear ST1.
  • the first spur gear SR1 engages with a second spur gear SR2 of the first spur gear ST1, the second spur gear SR2 being connected to the vehicle axle 10 and thereby transmitting a rotary motion generated by the driving member to the vehicle axle 10 and the associated wheels 11, respectively.
  • FIG. 30 shows a schematic representation of a further arrangement of the fourth embodiment of the multispeed transmission 9 according to the invention.
  • the arrangement shown here differs from the arrangement shown in FIG. 29 in that the second spur gear SR2 is connected to an intermediate shaft ZW instead of the vehicle axle 10 , which is further connected to a first spur gear SR3 of a second spur gear ST2.
  • Connected to the first spur gear SR3 is a second spur gear SR4 of the second spur gear ST2, the second spur gear SR4 being connected to the vehicle axle 10 and the wheels 11 connected thereto.
  • FIG. 31 shows in a schematic representation a further arrangement of the fourth embodiment of the multi-gear transmission 9 according to the invention. This differs from the arrangement shown in FIG. 29 in that a second spur gear ST2 is provided between the drive element 8 and the multi-gear transmission 9. As a result, the rotational movement generated by the drive element 8 already undergoes a translation before it is introduced into the multi-speed transmission 9.
  • FIG. 32 shows, in a schematic representation, a further arrangement of the fifth embodiment of the multi-gear transmission 9 according to the invention. In this case, a rotational movement into the multi-gear transmission 9 is initiated by the drive element 8. At the transmission output, a first spur gear ST1 is provided.
  • the output shaft 2 is connected to a first spur gear SR1 of the first spur gear ST1.
  • the first spur gear SR1 engages with a second spur gear SR2 of the first spur gear ST1 and is connected to the vehicle axle 10.
  • FIG. 33 shows in a schematic representation a further arrangement of the fifth embodiment of the multi-gear transmission 9 according to the invention.
  • the first spur gear SR3 engages with a second spur gear SR4 of the second spur gear ST2 and is connected to the vehicle axle 10.
  • a further translation of the rotational movement of the drive element 8 is provided by the second spur gear ST2.
  • FIG. 34 shows in a schematic representation a further arrangement of the fifth embodiment of the multispeed transmission 9 according to the invention. This differs from the arrangement shown in FIG. 32 in that a second spur gear ST2 is provided between the drive element 8 and the multi-speed transmission 9. Thus, there is already a translation of the rotational movement of the drive element, before it is introduced into the multi-speed transmission 9.
  • FIG. 35 shows in a schematic representation a further arrangement of the sixth embodiment of the multi-gear transmission 9 according to the invention.
  • a rotational movement is initiated by the drive element 8 into the multi-gear transmission 9 and translated accordingly.
  • the output shaft 2 is connected to a first spur gear SR1 of a first spur gear ST1.
  • the first Spur gear SR1 engages with a second spur gear SR2 of the first spur gear ST1 and is connected to an intermediate shaft ZW.
  • Also connected to this intermediate shaft is a first spur gear SR3 of a second spur gear ST2.
  • a second spur gear SR4 of the second spur gear ST2 is engaged with the first spur gear SR3.
  • the second spur gear SR4 is connected to the vehicle axle 10.
  • the rotational movement of the drive element is thus transmitted via the multi-speed transmission 9, the first helical gear ST1 and the second helical gear ST2 to the vehicle axle 10 and the associated wheels 1 1.
  • FIG. 36 shows in a schematic representation a further arrangement of the sixth embodiment of the multispeed transmission 9 according to the invention.
  • the output shaft 2 is connected to a first spur gear SR3 of a second spur gear ST2.
  • the first spur gear SR3 engages with a second spur gear SR4 of the second spur gear ST2 and is connected to the vehicle axle 10.
  • FIG. 37 shows in a schematic representation a further arrangement of the seventh embodiment of the multi-gear transmission 9 according to the invention.
  • a rotational movement into the multi-gear transmission 9 is initiated by the drive element 8.
  • the output shaft 2 is connected to a first spur gear SR1 of a first spur gear ST1.
  • the first spur gear SR1 engages with a second spur gear SR2 of the first spur gear ST1 and is connected to the vehicle axle 10.
  • the introduced by the drive member 8 rotational movement is translated by the multi-speed transmission 9 and the spur gear ST1 accordingly and transmitted to the vehicle axle 10 and the associated wheels 1 1.
  • FIG. 38 shows, in a schematic illustration, a further arrangement of the seventh embodiment of the multispeed transmission 9 according to the invention.
  • the arrangement shown here differs from the arrangement shown in FIG. 37 in that the second spur gear SR2 of the first spur gear ST1 is not connected to the vehicle axle 10 but to an intermediate shaft ZW. Also connected to the intermediate shaft ZW is a first spur gear SR3 of a second spur gear ST2, wherein a second spur gear SR4 of the second spur gear ST2 is connected to the vehicle axle 10.
  • a further reduction or transmission of the rotational movement takes place here in comparison with the arrangement shown in FIG.
  • FIG. 39 shows in a schematic representation a further arrangement of the seventh embodiment of the multi-gear transmission 9 according to the invention. This differs from the embodiment shown in FIG. 37 in that a second spur gear ST2 is arranged between the drive element 8 and the multi-gear transmission 9. Thus takes place already on the side of the transmission input AN of the multi-speed transmission, a translation of the rotational movement through the second spur gear ST2 before the rotational movement is introduced into the multi-speed transmission 9.
  • FIG. 40 shows in a schematic representation a further arrangement of the seventh embodiment of the multi-gear transmission 9 according to the invention.
  • the design around the second planetary gearset PR2 could be reduced by the fact that the third shaft 3 can still be connected to the fifth shaft 5 via the second shifting element SE2
  • the fifth shaft 5 is now connected instead of with the planet carrier PT2 of the second planetary PR2 with a first spur gear SR3 of a second spur gear ST2.
  • the first spur gear SR3 engages with a second spur gear SR4 of the second spur gear ST2 and is connected to the vehicle axle 10.
  • the output shaft 2 now only connects the planet carrier PT1 of the first planetary gearset PR1 with a first spur gear SR1 of a first spur gear ST1, wherein the first spur gear SR1 is engaged with a second spur gear SR2 of the first spur gear.
  • the second spur gear SR2 of the first spur gear ST1 is also connected to the vehicle axle 10.
  • FIG. 41 shows in a schematic representation a further arrangement of the seventh embodiment of the multi-speed transmission 9 according to the invention.
  • a second spur gear SR6 of the third spur gear ST3 is engaged with the first spur gear SR5, and the second spur gear SR6 is connected to the vehicle axle 10.
  • Compared to the arrangement shown in Figure 40 thus takes place between the multi-speed transmission 9 and the vehicle axle 10, a further translation by the third spur gear ST3 instead.
  • Figure 42 shows a schematic representation of another arrangement of the seventh embodiment of the multi-speed transmission 9.
  • the arrangement shown here differs from the arrangement shown in Figure 40 in that in the present arrangement between the drive element 8 and the multi-speed transmission 9, a third spur gear ST3 is arranged.
  • this third spur gear ST3 thus takes place a translation of the introduced by the drive member 8 rotational movement before it is introduced into the multi-speed transmission 9.
  • FIG. 43 shows in a schematic representation a further arrangement of the eighth embodiment of the multi-gear transmission 9 according to the invention.
  • a rotational movement is introduced into the multi-gear transmission 9 via the drive element 8.
  • the output shaft 2 is connected to a first spur gear SR1 of a first spur gear ST1.
  • the first spur gear SR1 in one handle is a second spur gear SR2 of the first spur gear ST1, wherein the second spur gear SR2 is connected to the vehicle axle 10 and thus a rotational movement on the vehicle axle 10 and the associated wheels 1 1 is transferable.
  • FIG. 44 shows in a schematic representation a further arrangement of the eighth embodiment of the multi-gear transmission 9 according to the invention.
  • the arrangement shown here differs from the arrangement shown in FIG. 43 in that the second spur gear SR2 of the first spur gear ST1 has an intermediate shaft ZW instead of the vehicle axle 10 is connected, said intermediate shaft ZW is further connected to a first spur gear SR3 of a second spur gear ST2.
  • a second spur gear SR4 of the second spur gear ST2 is engaged with the first spur gear SR3, the second spur gear SR4 being connected to the vehicle axle 10.
  • a further translation of the rotational movement of the drive element 8 is thus provided between the multi-speed transmission 9 and the vehicle axle 10 by the arrangement of the second spur gear ST2.
  • FIG. 45 shows in a schematic representation a further arrangement of the eighth embodiment of the multi-gear transmission 9 according to the invention. This differs from the embodiment shown in FIG. 43 in that a second spur gear ST2 is provided between the drive element 8 and the multi-gear transmission 9. This means that the rotational movement of the drive element 8 undergoes a translation before it is introduced into the multi-speed transmission 9.
  • FIG. 46 shows, in a schematic representation, a further arrangement of the ninth embodiment of the multi-gear transmission 9 according to the invention.
  • the drive element 8 initiates a rotational movement into the multi-gear transmission 9.
  • the output shaft 2 is connected to a first spur gear SR1 of a first spur gear ST1.
  • a second spur gear SR2 of the first spur gear ST1 is engaged with the first spur gear SR1, and the second spur gear SR2 is further connected to the vehicle axle 10. This is a by the drive member 8 generated rotary motion on the vehicle axle 10 and the associated wheels 1 1 transferable.
  • FIG. 47 shows in a schematic representation a further arrangement of the ninth embodiment of the multispeed transmission 9 according to the invention.
  • the intermediate shaft ZW is further connected to a first spur gear SR3 of a second spur gear ST2 and is engaged with a second spur gear SR4 of the second spur gear ST2.
  • the second spur gear SR4 of the second spur gear ST2 is connected to the vehicle axle 10.
  • the arrangement shown here thus differs from the arrangement shown in FIG. 46 in that, due to the arrangement of the second spur gear, a further transmission ratio acts on the rotational movement generated by the drive element 8 between the multi-speed transmission 9 and the vehicle axle 10.
  • FIG. 48 shows in a schematic representation a further arrangement of the ninth embodiment of the multi-gear transmission 9 according to the invention.
  • the arrangement shown here differs from the arrangement shown in FIG. 46 in that a second spur gear ST2 is provided between drive element 8 and multi-gear transmission 9.
  • a second spur gear ST2 is provided between drive element 8 and multi-gear transmission 9.
  • FIG. 49 shows in a schematic representation a further arrangement of the ninth embodiment of the multi-gear transmission 9 according to the invention.
  • This arrangement results in that the second planetary PR2 can be omitted.
  • an equilibrium in the multi-speed transmission 9 arises in the driving operation, which is why three different transmission ratios can also be represented by this arrangement.
  • the transmission output AB is now on one of the transmission Input AN arranged on opposite side of the multi-speed transmission 9. At the transmission output AB, the transmission of the rotational movement to the vehicle axle 10 takes place by means of the first spur gear ST1.
  • FIG. 50 shows in a schematic representation a further arrangement of the tenth embodiment of the multi-gear transmission 9 according to the invention.
  • a rotational movement is introduced into the multi-gear transmission 9.
  • the output shaft 2 is connected to a first spur gear SR1 of a first spur gear ST1 and engages with a second spur gear SR2 of the first spur gear ST1.
  • the second spur gear SR2 is further connected to the vehicle axle 10.
  • the multi-speed transmission 9 and the first spur gear ST1 is a rotational movement of the drive element, taking into account the respective gear ratios to the vehicle axle 10 and the associated wheels 1 1 transferable.
  • FIG. 51 shows a schematic representation of a further arrangement of the tenth embodiment of the multispeed transmission 9 according to the invention.
  • the first spur gear SR3 is engaged with a second spur gear SR4 of the second spur gear ST2, and the second spur gear SR4 is connected to the vehicle axle 10.
  • a second spur gear ST2 arranged with a corresponding translation.
  • FIG. 52 shows in a schematic representation a further arrangement of the tenth embodiment of the multi-gear transmission 9 according to the invention.
  • This differs from the embodiment shown in FIG. 50 in that a second spur gear ST2 is arranged between the drive element 8 and the multi-gear transmission 9.
  • the rotational movement which is provided by the drive element 8 undergoes a first translation before the rotational movement is introduced into the multi-speed transmission 9.
  • the rotational movement of the multi-speed transmission 9 is transmitted to the vehicle axle 10 and the associated wheels 1 1.
  • Figure 53 shows a schematic representation of another arrangement of the eleventh embodiment of the multi-gear transmission 9 of the invention.
  • a rotational movement of the drive element 8 is introduced into the multi-speed transmission 9 and translated accordingly.
  • the output shaft 2 is connected to a first spur gear SR1 of a first spur gear ST1, wherein the first spur gear SR1 is engaged with a second spur gear SR2 of the first spur gear ST1.
  • the second spur gear SR2 of the first spur gear ST1 is connected to the vehicle axle 10, whereby the rotary motion generated by the drive member 8 by means of the multi-gear 9 and the first spur gear ST1 on the vehicle axle 10 and the associated wheels 1 1 is transferable.
  • FIG. 54 shows a schematic representation of a further arrangement of the eleventh embodiment of the multi-gear transmission 9 according to the invention.
  • the embodiment shown here differs from the embodiment shown in FIG. 53 in that the second spur gear SR2 of the first spur gear ST1 instead of the vehicle axle 10 now has a Intermediate shaft ZW is connected, which is further connected to a first spur gear SR3 of a second spur gear ST2.
  • the first spur gear SR3 is engaged with a second spur gear of the second spur gear ST2.
  • the second spur gear SR4 of the second spur gear ST2 is also connected to the vehicle axle 10.
  • a further translation is thus provided by the second spur gear ST2.
  • the rotational movement of the drive element 8 is thus on the multi-speed transmission 9, the first spur gear ST1 and the second spur gear ST2 on the vehicle axle 10 and the associated wheels 1 1 transferable.
  • FIG. 55 shows in a schematic representation a further arrangement of the eleventh embodiment of the multi-gear transmission 9 according to the invention from the arrangement shown in Figure 53 in that between the drive member 8 and the multi-speed transmission 9, a second spur gear ST2 is provided. As a result, a translation of the rotational movement generated by the drive element 8 takes place before it is introduced into the multi-speed transmission 9.
  • FIG. 56 shows in a schematic representation a further arrangement of the eleventh embodiment of the multi-gear transmission 9 according to the invention.
  • this arrangement of the multi-gear transmission 9 has only one first planetary gearset PR1.
  • the second planetary PR2 could be omitted by the fact that the planet carrier PT1 of the first planetary PR1 via the fifth shaft 5 is connected to a first spur gear SR3 of a second spur gear ST2, wherein the first spur SR3 with a, connected to the vehicle axle 10, the second spur gear SR4 of the second spur gear ST2 is engaged.
  • the output shaft 2 is connected, as before, to the first spur gear SR1 of the first spur gear, wherein the first spur gear SR1 is engaged with the second spur gear SR2, which is also connected to the vehicle axle 10.
  • the arrangement of the spur gear ST1, ST2 is in a driving operation in the multi-speed transmission 9 a balance, which also three different ratios between the drive member 8 and the vehicle axle 10 and the associated wheels 1 1 are displayed.
  • FIG. 57 shows in a schematic representation a further arrangement of the eleventh embodiment of the multi-gear transmission 9 according to the invention.
  • the arrangement shown in FIG. 57 differs from the arrangement shown in FIG. 56 in that the second spur gears SR2, SR4 of the two spur gear ST1, ST2 instead are connected to the vehicle axle 10 with an intermediate shaft ZW.
  • a first spur gear SR5 of a third spur gear ST3 is likewise connected to the latter, the first spur gear SR5 being in engagement with a second spur gear SR6 of the third spur gear ST3 and being connected to the vehicle axle 10.
  • the arrangement shown here thus differs from the arrangement shown in Figure 56 in that between the multi-speed transmission 9 and vehicle axle 10 with the third spur gear ST3 another translation stage is provided.
  • FIG. 58 shows in a schematic representation a further arrangement of the eleventh embodiment of the multi-gear transmission 9 according to the invention.
  • the arrangement shown here differs from the arrangement shown in FIG. 56 in that a third spur gear ST3 is arranged between the drive element 8 and the multi-gear transmission 9. This has the consequence that the rotational movement generated by the drive element 8 already undergoes a translation before it is introduced into the multi-speed transmission 9.
  • FIG. 59 shows in a schematic representation a further arrangement of the twelfth embodiment of the multi-gear transmission 9 according to the invention.
  • a rotational movement is generated by the drive element 8 and introduced into the multi-gear transmission 9.
  • the output shaft 2 is connected to a first spur gear SR1 of a first spur gear ST1.
  • the first spur gear SR1 engages with a second spur gear SR2 of the first spur gear ST1 and is connected to the vehicle shaft 10.
  • FIG. 60 shows in a schematic representation a further arrangement of the twelfth embodiment of the multispeed transmission 9 according to the invention.
  • the arrangement shown here differs with respect to the arrangement shown in FIG. 59 in that the second spur gear SR2 of the first spur gear ST1 instead of the vehicle axle 10 is connected to an intermediate shaft ZW, which is further connected to a first spur gear SR3 of a second spur gear ST2.
  • the first spur gear SR3 engages with a second spur gear SR4 of the second spur gear ST2 and is connected to the vehicle axle 10.
  • a further transmission of the rotational movement introduced by the drive element is thus saturated between the multi-speed transmission 9 and the vehicle axle 10 by the second spur gear ST2.
  • FIG. 60 shows in a schematic representation a further arrangement of the twelfth embodiment of the multispeed transmission 9 according to the invention.
  • the arrangement shown here differs with respect to the arrangement shown in FIG. 59 in that the second spur gear SR2 of the first spur gear ST1 instead of the vehicle axle 10 is connected to
  • FIG. 61 shows in a schematic representation a further arrangement of the twelfth embodiment of the multi-gear transmission 9 according to the invention. This differs from the arrangement shown in FIG. 59 in that a second spur gear ST2 is arranged between the drive element 8 and the multi-gear transmission 9. As a result, the rotational movement generated by the drive element 8 undergoes a first translation before it is introduced into the multi-speed transmission 9.
  • FIG. 62 shows in a schematic representation a further arrangement of the twelfth embodiment of the multi-gear mechanism 9 according to the invention.
  • the arrangement shown here differs from the arrangement shown in FIG. 59 in that the fifth shaft 5, which transmits the planet carrier PT1 of the first planetary gearset PR1 to the ring gear H2 of the second planetary PR2 connects, is interrupted by a second spur gear ST2.
  • the drive shaft 1 and output shaft 2 are in a parallel arrangement to each other.
  • the first planetary gear set PR1 and the second planetary PR2 are also arranged axially offset with respect to their respective axis of rotation.
  • FIG. 63 shows in a schematic representation a further arrangement of the thirteenth embodiment of the multi-gear transmission 9 according to the invention.
  • a rotational movement is introduced into the multi-gear transmission 9 by the drive element 8.
  • the output shaft 2 is connected inter alia to a first spur gear SR1 of a first spur gear ST1.
  • the first spur gear SR1 engages with a second spur gear SR2 of the first spur gear ST1 and is connected to an intermediate shaft ZW.
  • This is further connected to a first spur gear SR3 of a second spur gear ST2, which engages with a second spur gear SR4 of the second spur gear ST2.
  • the second spur gear SR4 of the second spur gear ST2 is connected to the vehicle axle 10.
  • FIG. 64 shows in a schematic representation a further arrangement of the thirteenth embodiment of the multi-gear transmission 9 according to the invention. This differs from the arrangement shown in FIG. 63 in that the second spur gear ST2 is arranged between the drive element 8 and the multi-gear transmission 9. This means that the rotational movement generated by the drive element 8 already undergoes a translation before it is introduced into the multi-speed transmission 9. Further, in contrast to the arrangement shown in Figure 63, the intermediate shaft ZW is missing, which has the consequence that the second spur gear SR2 of the first spur gear ST1 is connected to the vehicle axle 10 instead of the intermediate shaft ZW.
  • FIG. 65 shows in a schematic representation a further arrangement of the thirteenth embodiment of the multi-gear transmission 9 according to the invention.
  • the arrangement shown here differs from the arrangement shown in FIG. 64 in that the drive element 8 is connected directly to the drive shaft 1.
  • the second spur gear ST2 is now arranged between the first planetary gearset PR1 and the second planetary gearset PR2.
  • the drive shaft 1 and the output shaft 2 are now in a parallel arrangement to each other. This also has the consequence that also the first planetary gear PR1 and the second planetary PR2 are offset in relation to their respective axis of rotation parallel to each other.
  • Figure 66 shows a schematic representation of another arrangement of the fourteenth embodiment of the multi-gear transmission 9 according to the invention.
  • the output shaft 2 is connected to the transmission output AB with a first spur gear SR1 of a first spur gear ST1.
  • the first spur gear SR1 engages with a second spur gear SR2 of the first spur gear ST1, the second one Spur gear SR2 is connected to an intermediate shaft ZW.
  • This is further connected to a first spur gear SR3 of a second spur gear ST2.
  • the first spur gear SR3 is engaged with a second spur gear SR4 of the second spur gear ST2, and the second spur gear SR4 is connected to the vehicle axle 10.
  • a rotational movement introduced by the drive element 8 is thus transferable by the multi-speed transmission 9 and the spur gear ST1, ST2 to the vehicle axle 10 and the wheels 11 associated therewith, taking into account the respective transmission ratio.
  • FIG. 67 shows in a schematic representation a further arrangement of the fourteenth embodiment of the multi-gear transmission 9 according to the invention.
  • the arrangement shown here differs from the arrangement shown in FIG. 66 in that the second spur gear ST2 is arranged between the drive element 8 and the multi-gear transmission 9.
  • the arrangement shown here has no intermediate shaft, since the second spur gear SR2 of the first spur gear ST1 is connected directly to the vehicle axle 10 instead of the intermediate shaft ZW not shown here.
  • FIG. 68 shows in a schematic representation a further arrangement of the fourteenth embodiment of the multispeed transmission 9 according to the invention.
  • the arrangement shown here differs from the arrangement shown in FIG. 66 in that the second spur gear SR2 of the first spur gear ST1 is directly connected to the first spur gear ST1 instead of an intermediate shaft ZW the vehicle axle 10 is connected.
  • the second spur gear ST2 is disposed between the first planetary gear set PR1 and the second planetary gear set PR2.
  • the fifth shaft 5, which connects the ring gear H1 of the first planetary gearset PR1 to the sun gear S2 of the second planetary gearset PR2, is interrupted by the second spur gear ST2.
  • FIG. 69 shows a schematic representation of a fifteenth embodiment of a multi-gear transmission 9 according to the invention.
  • the illustrated multi-gear transmission 9 has a first planetary gearset PR1, a transmission input AN, a transmission output AB and a first shifting element SE1.
  • a drive shaft 1 a ring gear H1 of the first planetary PRI is connected to the transmission input AN.
  • a planet carrier PT1 of the first planetary gearset PR1 is connected to the transmission output AB and further to a first side of the first switching element SE1.
  • Via third shaft 3, a sun gear S1 of the first planetary PR1 is also connected to the first switching element SE1.
  • the first switching element SE1 is further connected via a fourth shaft 4 with a housing G.
  • the transmission input AN, the first planetary PR1, the transmission output AB and the first switching element SE1 are arranged starting at the transmission input AN in the order just mentioned.
  • the first planetary gear PR1, the transmission output AB and the first switching element SE1 are arranged coaxially to a common, not shown here, rotation axis.
  • the first planetary gear set PR1 is designed as a minus planetary gear set.
  • the first switching element SE1 is designed as a double switching element.
  • the first switching element SE1 of the first gear can be produced, that the third shaft 3 is connected to the fourth shaft 4, whereby the third shaft 3 is braked or fixed to the housing G.
  • the second gear can be represented by the first switching element SE1 in that the output shaft 2 is connected to the third shaft 3.
  • Figure 70 shows a schematic representation of a further arrangement of the fifteenth embodiment of the multi-speed transmission 9 according to the invention
  • Transmission output AB the output shaft 2 is connected to a first spur gear SR1 of a first spur gear ST1, wherein the first spur gear SR1 is engaged with a second spur gear SR2 of the first spur gear ST1 connected to a vehicle axle 10.
  • a second spur gear ST2 is arranged, through which a rotational movement generated by the drive element 8 already undergoes a translation before the rotary motion is introduced into the multi-speed transmission 9.
  • the initiated by the drive member 8 rotational movement is translated and transmitted to the vehicle axle 10 and the associated wheels 1 1.
  • the drive shaft AW is connected to the transmission input AN to the drive element 8.
  • the rotational movement of the drive element 8 is transmitted to a first spur gear ST1, wherein the second spur gear ST2 of the first spur gear ST1 is connected to an intermediate shaft ZW and further to a first spur gear ST3 of a second spur gear ST2.
  • a second spur gear ST4 of the second spur gear ST2 engages with the first spur gear ST3 and transmits the rotational movement to the vehicle axle 10 or the wheels 11 associated therewith.
  • the drive element 8, the multi-speed transmission 9, and the respective spur gear ST1, ST2, ST3 can be arranged in any arrangement above, below, in front of or behind the vehicle axle 10.

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

Abstract

L'invention concerne une transmission multi-vitesse (9) destinée à des véhicules ferroviaires, la transmission multi-vitesse (9) comprenant au moins une entrée de transmission (AN), au moins une sortie de transmission (AB), au moins un ensemble d'engrenages planétaires (PR1, PR2), au moins un élément de commutation (SE1, SE2) et un boîtier (G), un ensemble d'engrenages planétaire (PR1, PR2) comportant une roue solaire (S1, S2), au moins un porte-satellites (PT1, PT2) pourvus des engrenages planétaires et une couronne de train planétaire (H1, H2), et un élément d'entraînement (8) permettant d'introduire un mouvement de rotation dans la transmission multi-vitesse (9). L'invention est caractérisée en ce que l'actionnement de l'au moins un élément de commutation (SE1, SE2) permet au moins deux rapports de transmission différents entre l'entrée de transmission (AN) et la sortie de transmission (AB).
EP15727375.6A 2014-07-04 2015-06-02 Transmission multi-vitesse pour véhicules ferroviaires Withdrawn EP3164622A1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102014213012.3A DE102014213012A1 (de) 2014-07-04 2014-07-04 Mehrganggetriebe für Schienenfahrzeuge
PCT/EP2015/062246 WO2016000897A1 (fr) 2014-07-04 2015-06-02 Transmission multi-vitesse pour véhicules ferroviaires

Publications (1)

Publication Number Publication Date
EP3164622A1 true EP3164622A1 (fr) 2017-05-10

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US (1) US20170204942A1 (fr)
EP (1) EP3164622A1 (fr)
CN (1) CN106471281A (fr)
DE (1) DE102014213012A1 (fr)
WO (1) WO2016000897A1 (fr)

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DE102014213012A1 (de) 2016-01-07
US20170204942A1 (en) 2017-07-20
CN106471281A (zh) 2017-03-01
WO2016000897A1 (fr) 2016-01-07

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