WO2019091719A1 - Transmission pour véhicule automobile - Google Patents

Transmission pour véhicule automobile Download PDF

Info

Publication number
WO2019091719A1
WO2019091719A1 PCT/EP2018/078274 EP2018078274W WO2019091719A1 WO 2019091719 A1 WO2019091719 A1 WO 2019091719A1 EP 2018078274 W EP2018078274 W EP 2018078274W WO 2019091719 A1 WO2019091719 A1 WO 2019091719A1
Authority
WO
WIPO (PCT)
Prior art keywords
transmission
switching element
gear
shaft
rotatably connected
Prior art date
Application number
PCT/EP2018/078274
Other languages
German (de)
English (en)
Inventor
Philipp Notheis
Leschek Debernitz
Niko Zwerger
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 WO2019091719A1 publication Critical patent/WO2019091719A1/fr

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
    • F16H57/00—General details of gearing
    • F16H57/04—Features relating to lubrication or cooling or heating
    • F16H57/0434—Features relating to lubrication or cooling or heating relating to lubrication supply, e.g. pumps ; Pressure control
    • F16H57/0441—Arrangements of pumps
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B60—VEHICLES IN GENERAL
    • B60K—ARRANGEMENT OR MOUNTING OF PROPULSION UNITS OR OF TRANSMISSIONS IN VEHICLES; ARRANGEMENT OR MOUNTING OF PLURAL DIVERSE PRIME-MOVERS IN VEHICLES; AUXILIARY DRIVES FOR VEHICLES; INSTRUMENTATION OR DASHBOARDS FOR VEHICLES; ARRANGEMENTS IN CONNECTION WITH COOLING, AIR INTAKE, GAS EXHAUST OR FUEL SUPPLY OF PROPULSION UNITS IN VEHICLES
    • B60K1/00—Arrangement or mounting of electrical propulsion units
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B60—VEHICLES IN GENERAL
    • B60K—ARRANGEMENT OR MOUNTING OF PROPULSION UNITS OR OF TRANSMISSIONS IN VEHICLES; ARRANGEMENT OR MOUNTING OF PLURAL DIVERSE PRIME-MOVERS IN VEHICLES; AUXILIARY DRIVES FOR VEHICLES; INSTRUMENTATION OR DASHBOARDS FOR VEHICLES; ARRANGEMENTS IN CONNECTION WITH COOLING, AIR INTAKE, GAS EXHAUST OR FUEL SUPPLY OF PROPULSION UNITS IN VEHICLES
    • B60K17/00—Arrangement or mounting of transmissions in vehicles
    • B60K17/34—Arrangement or mounting of transmissions in vehicles for driving both front and rear wheels, e.g. four wheel drive vehicles
    • B60K17/344—Arrangement or mounting of transmissions in vehicles for driving both front and rear wheels, e.g. four wheel drive vehicles having a transfer gear
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B60—VEHICLES IN GENERAL
    • B60K—ARRANGEMENT OR MOUNTING OF PROPULSION UNITS OR OF TRANSMISSIONS IN VEHICLES; ARRANGEMENT OR MOUNTING OF PLURAL DIVERSE PRIME-MOVERS IN VEHICLES; AUXILIARY DRIVES FOR VEHICLES; INSTRUMENTATION OR DASHBOARDS FOR VEHICLES; ARRANGEMENTS IN CONNECTION WITH COOLING, AIR INTAKE, GAS EXHAUST OR FUEL SUPPLY OF PROPULSION UNITS IN VEHICLES
    • B60K17/00—Arrangement or mounting of transmissions in vehicles
    • B60K17/34—Arrangement or mounting of transmissions in vehicles for driving both front and rear wheels, e.g. four wheel drive vehicles
    • B60K17/356—Arrangement or mounting of transmissions in vehicles for driving both front and rear wheels, e.g. four wheel drive vehicles having fluid or electric motor, for driving one or more wheels
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B60—VEHICLES IN GENERAL
    • B60K—ARRANGEMENT OR MOUNTING OF PROPULSION UNITS OR OF TRANSMISSIONS IN VEHICLES; ARRANGEMENT OR MOUNTING OF PLURAL DIVERSE PRIME-MOVERS IN VEHICLES; AUXILIARY DRIVES FOR VEHICLES; INSTRUMENTATION OR DASHBOARDS FOR VEHICLES; ARRANGEMENTS IN CONNECTION WITH COOLING, AIR INTAKE, GAS EXHAUST OR FUEL SUPPLY OF PROPULSION UNITS IN VEHICLES
    • B60K1/00—Arrangement or mounting of electrical propulsion units
    • B60K2001/001—Arrangement or mounting of electrical propulsion units one motor mounted on a propulsion axle for rotating right and left wheels of this axle
    • 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
    • B60Y2400/70—Gearings
    • B60Y2400/73—Planetary gearings
    • 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
    • F16H3/02—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion without gears having orbital motion
    • F16H3/08—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion without gears having orbital motion exclusively or essentially with continuously meshing gears, that can be disengaged from their shafts
    • F16H3/087—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion without gears having orbital motion exclusively or essentially with continuously meshing gears, that can be disengaged from their shafts characterised by the disposition of the gears
    • F16H3/093—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion without gears having orbital motion exclusively or essentially with continuously meshing gears, that can be disengaged from their shafts characterised by the disposition of the gears with two or more countershafts
    • F16H2003/0931—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion without gears having orbital motion exclusively or essentially with continuously meshing gears, that can be disengaged from their shafts characterised by the disposition of the gears with two or more countershafts each countershaft having an output gear meshing with a single common gear on the output 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
    • F16H2200/0021—Transmissions for multiple ratios specially adapted for electric vehicles
    • 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
    • F16H2200/20—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
    • F16H2200/203—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
    • F16H3/00—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion
    • F16H3/02—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion without gears having orbital motion
    • F16H3/08—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion without gears having orbital motion exclusively or essentially with continuously meshing gears, that can be disengaged from their shafts
    • F16H3/087—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion without gears having orbital motion exclusively or essentially with continuously meshing gears, that can be disengaged from their shafts characterised by the disposition of the gears
    • F16H3/089—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion without gears having orbital motion exclusively or essentially with continuously meshing gears, that can be disengaged from their shafts characterised by the disposition of the gears all of the meshing gears being supported by a pair of parallel shafts, one being the input shaft and the other the output shaft, there being no countershaft involved
    • 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

Definitions

  • the invention relates to a transmission for an electric vehicle, with an electric machine having a drive shaft, a first switching element, a second switching element and a transmission, wherein by operating the first switching element and / or the second switching element, a gear of the gearbox can be inserted.
  • the invention relates to a drive train with the transmission according to the invention. Moreover, the invention relates to an electric vehicle with the transmission or the drive train.
  • the prior art already discloses a large number of differently designed transmissions which are used in electric vehicles.
  • the electric vehicles have in common that they have only an electric drive. This means that the electric vehicles have no internal combustion engine.
  • the electric drive can be realized by providing at least one electric machine.
  • WO 2011 034 762 A2 discloses an electric vehicle with a double-clutch transmission. In the electric vehicle, three switching stages can be realized.
  • the object of the invention is to provide a transmission for an electric vehicle, which is improved over the known transmissions.
  • the object is achieved by a transmission of the aforementioned type, which is characterized in that the electrical machine is always connected to a fluid pump drive technology.
  • the transmission according to the invention has the advantage that a simply constructed drive of the pump is realized.
  • a recuperation is possible due to the technical connection of the electrical machine with the fluid pump in a sail mode of the electric vehicle. This is possible because the fluid pump realizes the necessary for the recuperation rotational movement.
  • the transmission according to the invention also has the advantage that the fluid pump, which can be designed as an oil pump, is permanently driven. This is possible because in the technical connection between the electric machine and the pump, no switching element is arranged, so that the technical connection between the electric machine and the fluid pump is permanent. As a result, the fluid pump is driven as long as the drive shaft of the electric machine is rotated regardless of whether a gear is engaged or not.
  • the fluid pump can promote a fluid, such as oil, even if no gear is engaged in the manual transmission.
  • the fluid pump can promote the oil in time before the gear is engaged.
  • a wheel set in the manual transmission can be lubricated with oil, even if no gear is engaged and / or before a gear is engaged.
  • the wheelset can be cooled.
  • the transmission is designed and intended to be installed in an electric vehicle. This means that the transmission, in particular the transmission components, has no connection for an internal combustion engine. In particular, a drive of the gearbox and / or a transmission output shaft can be made purely electrically.
  • a shaft is not exclusive to understand, for example, a cylindrical, rotatably mounted machine element for transmitting torque, but these are also general connecting elements to understand that connect individual components together, in particular fasteners that connect a plurality of components rotatably together.
  • the electric machine consists at least of a stator and a rotatably mounted rotor and is set up in a motor operation to convert electrical energy into mechanical energy in the form of speed and torque, and in a generator operation mechanical energy into electrical To transform energy in the form of electricity and voltage.
  • the rotor may be rotatably connected to the drive shaft and / or attached to the drive shaft.
  • the electric machine can always be connected to the fluid pump in terms of drive technology without translation. This allows a simple design gear realized.
  • the transmission may include a summing gear and another electric machine.
  • the electric machine and the other electric machine can always be connected to the fluid pump by means of the summation with the fluid pump.
  • a component of the summation gear can always be connected to the fluid pump in terms of drive technology.
  • Another component of the summation can be connected by means of the drive shaft with the electric machine, in particular always, drive technology.
  • a branch of the drive shaft via which the drive shaft is connected in terms of drive engineering with other components of the transmission described in more detail below, can be connected upstream of the summing gear in terms of drive technology.
  • Another component of the summation can be connected by means of another drive shaft with the other electric machine, in particular always, drive technology.
  • the first and the second switching element may be arranged one above the other in the radial direction. This makes it possible to produce a compact in the axial direction gear.
  • the first switching element and the second switching element can be arranged offset from one another in the axial direction. In this case, a compact in the radial direction gear can be realized.
  • the first and / or the second switching element can each be designed as a clutch.
  • the first and / or second switching element can each as be carried out a dry clutch or a wet clutch.
  • the switching elements can be designed as a wet clutch and in an axial arrangement as a dry clutch in a radial arrangement. In this case, the dry clutch, in particular when used in a dry clutch described below, have low drag losses.
  • the first switching element and the second switching element may be part of a double clutch.
  • the dual clutch can be arranged and / or configured such that the dual clutch drivingly connected to the drive shaft drives the fluid pump, in particular directly. This can be done, for example, by a plate carrier of the double clutch, which is connected to the drive shaft as well as to the fluid pump, in particular always, in terms of drive technology.
  • a plate carrier of the double clutch which is connected to the drive shaft as well as to the fluid pump, in particular always, in terms of drive technology.
  • Such an arrangement and design of the double clutch allows a compact gear.
  • the dual clutch advantageously has short switching times.
  • the combination of high mass inertias and high differential numbers can be compensated by means of the double clutch.
  • the drive shaft can drive the fluid pump directly. This means that no other components of the transmission are technically arranged between the fluid pump and the electric machine.
  • the first switching element and / or the second switching element by means of the fluid pump, in particular using a control device be actuated.
  • the fluid pump in particular using a control device
  • the transmission may comprise at least one actuator, by means of which the first switching element and / or the second switching element can be actuated.
  • the transmission may have a first actuator, by means of which the first switching element can be actuated, and a second actuator, by means of which the second switching element can be actuated. Since the operation of the first and / or the second switching element in this embodiment no longer by the Fluid pump must be made, the fluid pump can be made small, since they only need to promote oil for lubrication and / or cooling of the wheelset.
  • the transmission may include a transmission output shaft, a first shaft, and a second shaft.
  • the drive shaft can be rotatably connected by means of the first switching element with the first shaft and by means of the second switching element with the second shaft.
  • the first shaft and the second shaft can be connected to the transmission output shaft, in particular always, in terms of drive technology.
  • the transmission may include the transmission output shaft, the first shaft, and the second shaft.
  • a further drive shaft of a further electric machine can be connected in a rotationally fixed manner to the second shaft by means of the first switching element and to the second shaft by means of the second switching element.
  • the first shaft and the second shaft may be connected to the transmission output shaft in terms of drive technology.
  • the electric machine in particular exclusively, serves to drive the fluid pump.
  • the drive of the fluid pump is independent of the required due to the driving condition speed of the transmission output shaft.
  • the fluid pump can be prevented that at slow speeds of the electric vehicle by the fluid pump is supplied to a low flow rate.
  • the volume flow required for cooling and / or lubricating the clutch and / or the wheel set and / or the electric machine can always be provided by the fluid pump.
  • the electric machine can be made small and compact. As a result, by the separate arrangement of the electric machine, the oil budget of the transmission can be efficiently controlled or regulated as needed.
  • the further electric machine can always be connected to a plurality of fluid pumps in terms of drive technology.
  • the first shaft may be arranged coaxially with the second shaft.
  • the second shaft may be arranged as a hollow shaft which encloses at least a part of the first shaft.
  • the first and second shafts respectively correspond to an input shaft of the manual transmission.
  • the first and second shaft have no interface or connectivity by means of which they are connected directly or indirectly with an internal combustion engine.
  • a first gear of the gearbox may be rotatably connected to the first shaft and may be in engagement with a non-rotatably connected in the transmission output shaft second gear of the gearbox.
  • a third gear of the gearbox may be rotatably connected to the second shaft and may be in engagement with a non-rotatably connected to the transmission output shaft fourth gear of the gearbox.
  • rotationally fixed connection a connection between two elements, which is designed and arranged such that the two interconnected elements always have the same speed. This is not the case if, for example, between the two interconnected elements, a switching element is arranged, which is in the open state.
  • the rotationally fixed connection can be realized for example by a spline.
  • the transmission may have a countershaft and another countershaft.
  • a first gear of the gearbox can be rotatably connected to the first shaft and in engagement with a rotatably connected to the countershaft fifth gear of the gearbox and engaged with a rotatably connected to the other countershaft fifth other gear of the gearbox.
  • a third gear of the gearbox can be rotatably connected to the second shaft and in engagement with a rotatably connected to the countershaft sixth gear of the gearbox and with a rotatably connected to the other countershaft sixth other gear of the gearbox.
  • a seventh gear of the gearbox may be rotatably connected to the transmission output shaft. In this case, the seventh gear in engagement with a non-rotatably connected to the countershaft eighth gear of the shift gear and one with the other countershaft rotatably connected eight other gear of the gearbox be.
  • Such a transmission has the advantage that a force distribution of 50% each can take place on the two countershafts. As a result, the gear width can be reduced and the transmission can be built short. Moreover, it is an advantage of the two-organ design that the first shaft and / or the second shaft and / or the transmission output shaft are not subjected to bending.
  • the transmission in the radial direction made smaller than the transmission in two-way design.
  • the transmission has wider gears than the Zweivorgelegewellenbauweise and is thus formed axially longer.
  • the aforementioned gears can be designed as spur gears.
  • the gears may have helical teeth, which is advantageous in terms of acoustics.
  • the transmission may have a planetary gear set.
  • a sun gear of the planetary gear set be connected to the electric machine drive technology.
  • the drive shaft may extend through the fluid pump and be rotatably connected to the sun gear of the planetary gear set.
  • a bridge of the planetary gear set may be rotatably connected to a transmission output shaft and a ring gear of the planetary gear set may be rotatably connected by means of the first switching element with a housing and rotatably connected by means of the second switching element with one of the two other wheelset elements of the planetary gear set.
  • the ring gear can be rotatably connected by means of the second switching element with the web.
  • the ring gear can be rotatably connected to the sun gear.
  • the drive shaft can be rotatably connected by means of the second switching element with the ring gear.
  • a sun gear of the planetary gear set may be connected to a further electric machine in terms of drive technology.
  • a further drive shaft of the further electric machine can be connected to the sun gear of the planetary gear set in a rotationally fixed manner.
  • the web of the planetary gear set may be rotatably connected to the transmission output shaft and the ring gear of the planetary gear set may be rotatably connected by means of the first switching element with the housing and rotatably connected by means of the second switching element with one of the two other wheelset elements of the planetary gear set.
  • the ring gear can be rotatably connected by means of the second switching element with the web.
  • the ring gear can be rotatably connected to the sun gear.
  • the further drive shaft can be rotatably connected by means of the second switching element with the ring gear.
  • the electric machine is used in this embodiment, in particular exclusively, to drive the fluid pump.
  • the volume flow required for cooling and / or lubricating the clutch and / or the wheel set and / or the electric machine can always be provided by the fluid pump.
  • the electric machine can be made small and compact. As a result, by the separate arrangement of the electric machine, the oil budget of the transmission can be efficiently controlled or regulated as needed.
  • the further electric machine can always be connected to a plurality of fluid pumps in terms of drive technology.
  • the planetary gear has the advantage that a high efficiency can be realized. Further advantages of the planetary gearbox are the radial bearing, the compact design and the good acoustics.
  • at least two gears, in particular exactly two gears can be realized by the gearbox.
  • a first gear can be realized by closing the second switching element, wherein the first switching element is open.
  • a second gear can be realized by closing the first switching element, wherein the second switching element is open.
  • the two courses have a different translation.
  • the second gear has the advantage that the electric machine can work efficiently at high speeds.
  • alternative transmissions may have more than two gears.
  • a forward driving operation of the electric vehicle can be realized.
  • a reverse driving operation of the electric vehicle can be realized in that the drive shaft rotates in a different, in particular reverse, direction of rotation than in a forward drive operation.
  • the drive shaft must be driven by the electric machine in a different direction of rotation.
  • a drive train for an electric vehicle with the transmission according to the invention and an axle differential and / or another axle differential is a drive train for an electric vehicle with the transmission according to the invention and an axle differential and / or another axle differential.
  • the transmission output shaft with the axle differential and / or the other axle differential in particular always, be connected by drive technology.
  • the axle differential is connected to two wheels of the electric vehicle, in particular always, in terms of drive technology.
  • the other axle differential is connected to two other wheels of the electric vehicle, in particular always, driving technology.
  • the drive train is designed such that only a purely electric drive of the gearbox can take place. The drive train thus has no internal combustion engine.
  • the transmission output shaft can be directly or indirectly connected to the axle differential drive technology.
  • Such a compound lends itself to a longitudinal drive train, in which the transmission output shaft runs parallel to the direction of travel of the electric vehicle.
  • the transmission output shaft can be connected by means of a bevel gear with the axle differential.
  • a bevel gear with the axle differential.
  • the transmission output shaft can be connected by means of a gear set with the axle differential.
  • the wheels of the wheelset may have a beveloid toothing.
  • the transmission output shaft can also be connected by means of a hang-on coupling with another axle differential.
  • the transmission output shaft can be connected by means of the bevel gear and the hang-on clutch with the other axle differential.
  • the dual clutch can also be electrically operated, so that no pump is required for the double clutch.
  • Fig. 1 is an illustration of the transmission according to the invention according to a first
  • Fig. 2 is an illustration of the transmission according to the invention according to a second
  • Fig. 3 is an illustration of the transmission according to the invention according to a third
  • Embodiment 4 shows a representation of the transmission according to the invention according to a fourth embodiment
  • Fig. 5 is an illustration of the transmission according to the invention according to a fifth
  • Fig. 7 is an illustration of the transmission according to the invention according to a seventh
  • Fig. 8 is an illustration of the transmission according to the invention according to an eighth
  • Fig. 12 is an illustration of the transmission according to the invention according to a twelfth embodiment
  • Fig. 13 is an illustration of the transmission according to the invention according to a thirteenth embodiment
  • Fig. 14 is an illustration of the transmission according to the invention according to a fourteenth embodiment
  • Fig. 15 is an illustration of the transmission according to the invention according to a fifteenth embodiment
  • Fig. 16 is an illustration of the transmission according to the invention according to a sixteenth embodiment
  • 17 is an illustration of an alternative drive of a fluid pump of the transmission according to the invention.
  • 20 shows a drive train according to a second embodiment with the transmission according to the invention
  • 21 shows a drive train according to a third embodiment with the transmission according to the invention
  • Fig. 22 shows a drive train according to a fourth embodiment with the transmission according to the invention.
  • the transmission 1 shown in Figure 1 has an electric machine 2 with a drive shaft 3, a first switching element K1, a second switching element K2 and a transmission 6 on. By operating the first switching element K1 and / or the second switching element K2, a gear of the gearbox 6 can be inserted.
  • the transmission 1 has a fluid pump 7 for conveying oil.
  • the electric machine 2 is always connected to the fluid pump 7 in terms of drive technology.
  • the first switching element K1 and the second switching element K2 are part of a double clutch 4.
  • the drive shaft 3 is always connected with the dual-clutch transmission.
  • the double clutch 4 is in turn directly connected to the fluid pump 7 by drive technology.
  • a disk carrier 5 of the dual clutch 4 is directly connected to the fluid pump 7 by a drive.
  • the electric machine 2 is always connected by means of the dual clutch 4 with the fluid pump 7 in terms of drive technology.
  • the transmission 1 has a first shaft 11 and a second shaft 12.
  • the first shaft 11 and the second shaft 12 are arranged coaxially with a transmission center axis M.
  • the second shaft 12 encloses a part of the first shaft 11.
  • the drive shaft 3 is connected by means of the first switching element K1 with the first shaft 11 rotatably connected.
  • the drive shaft 3 by means of the second switching element K2 with the second shaft 12 rotatably connected.
  • the first switching element K1 and the second switching element K2 are arranged offset from one another in the radial direction.
  • the first switching element K1 is arranged in the radial direction above the second switching element K2.
  • the transmission 6 has two sets of wheels.
  • a first wheel set is formed by a first gear 13 and a second gear 14.
  • the first gear 13 is rotatably connected to the first shaft 11.
  • the second gear 14 is connected to the drive output shaft 10 rotatably connected and is in engagement with the first gear 13.
  • a second set of wheels is formed by a third gear 15 and a fourth gear 16.
  • the third gear 15 is rotatably connected to the second shaft 12 and the fourth gear 16 is rotatably connected to the transmission output shaft 10 and is engaged with the third gear 15 in engagement.
  • the two wheelsets have different translations.
  • Figure 2 shows a transmission 1 according to a second embodiment. It differs from the transmission 1 illustrated in FIG. 1 in that a further electric machine 33 with a further drive shaft 32 is present.
  • the further electric machine 33 is arranged such that the further drive shaft 32 is rotatably connected by means of the first switching element K1 with the first shaft 11.
  • the further drive shaft 32 by means of the second switching element K2 with the second shaft 12 rotatably connected.
  • the electric machine 2 drives the fluid pump 7.
  • the fluid pump 7 is not connected to the other electric machine 33 in terms of technology.
  • FIG. 3 shows a transmission 1 according to a third exemplary embodiment.
  • the transmission 1 differs from the transmission 1 illustrated in FIG. 1 in the design of the gearbox 6.
  • the gearbox 6 has a countershaft 17 and another countershaft 18.
  • the transmission 6 has three sets of wheels.
  • the first gear 11 rotatably connected to the first gear 13 with a fifth gear 24 of the gearbox 6 and with a fifth other gear 25 of the gearbox 6 is respectively engaged.
  • the fifth gear 24 is rotatably connected to the countershaft 17 and the fifth other gear 25 is rotatably connected to the other countershaft 18.
  • a rotationally fixedly connected to the transmission output shaft 10 seventh gear 28 with an eighth gear 29 and an eighth other gear 30 is respectively engaged.
  • the eighth gear 29 is rotatably connected to the countershaft 17 and the eighth other gear 30 is rotatably connected to the other countershaft 18.
  • FIG. 4 shows a transmission 1 according to a fourth exemplary embodiment. It differs from the transmission 1 shown in FIG. 3 in that a further electric machine 33 with a further drive shaft 32 is present.
  • the further electric machine 33 is arranged such that the further drive shaft 32 is rotatably connected by means of the first switching element K1 with the first shaft 11.
  • the further drive shaft 32 by means of the second switching element K2 with the second shaft 12 rotatably connected.
  • the electric machine 2 drives the fluid pump 7.
  • the fluid pump 7 is not connected to the other electric machine 33 in terms of technology.
  • Figure 5 shows a transmission 1 according to a fifth embodiment.
  • the transmission 1 shown in Figure 5 differs from the transmission 1 shown in Figure 1 in the arrangement of the first switching element K1 and the second switching element K2.
  • the first switching element K1 is arranged offset in the axial direction relative to the second switching element K2.
  • the first switching element K1 and the second switching element K2 have the same outer diameter.
  • Figure 6 shows a transmission 1 according to a sixth embodiment. It differs from the transmission illustrated in FIG. 5 in that a further electric machine 33 with a further drive shaft 32 is present.
  • the further electric machine 33 is arranged such that the further drive shaft 32 by means of the first switching element K1 with the first shaft 11 is rotatably connected.
  • the further drive shaft 32 by means of the second switching element K2 with the second shaft 12 rotatably connected.
  • the electric machine 2 drives the fluid pump 7.
  • the fluid pump 7 is not connected to the other electric machine 33 in terms of technology.
  • Figure 7 shows a transmission 1 according to a seventh embodiment.
  • the transmission 1 shown in Figure 7 differs from the transmission 1 shown in Figure 3 in the arrangement of the first switching element K1 and the second switching element K2.
  • the first switching element K1 is arranged offset in the axial direction to the second switching element K2.
  • the first switching element K1 and the second switching element K2 have the same outer diameter.
  • Figure 8 shows a transmission 1 according to an eighth embodiment. It differs from the transmission 1 illustrated in FIG. 7 in that a further electric machine 33 with a further drive shaft 32 is present.
  • the further electric machine 33 is arranged such that the further drive shaft 32 is rotatably connected by means of the first switching element K1 with the first shaft 11.
  • the further drive shaft 32 by means of the second switching element K2 with the second shaft 12 rotatably connected.
  • the electric machine 2 drives the fluid pump 7.
  • the fluid pump 7 is not connected to the other electric machine 33 in terms of technology.
  • FIG. 9 shows a ninth exemplary embodiment of the transmission 1 according to the invention.
  • the transmission 1 differs as follows from the transmissions 1 shown in FIGS. 1 to 8.
  • the manual transmission 6 has a planetary gear transmission PS.
  • the electric machine EM is connected by means of the dual clutch 4 and the fluid pump 7 with the planetary gearbox PS in terms of drive technology.
  • a web of the planetary gearset PS is rotatably connected to the transmission output shaft 10.
  • a ring gear of the planetary gearset PS is rotatably connected by means of the first switching element K1 with a housing G.
  • the housing G may be the transmission housing or the housing of the electric vehicle. In both cases, the housing G does not rotate during operation of the transmission 1.
  • the ring gear by means of the second switching element K2 rotatably connected to the sun gear of the planetary gear set PS.
  • the ring gear In a closed second switching element K2, the ring gear is rotatably connected to the sun gear of the planetary gearset PS, whereby a direct gear is realized.
  • the ring gear of the planetary gearset PS by means of the second switching element K2 with the drive shaft 3 rotatably connected.
  • the first switching element K1 is arranged in the radial direction above the second switching element K2.
  • FIG. 10 shows a tenth exemplary embodiment of the transmission 1 according to the invention. It differs from the transmission 1 shown in FIG. 9 in that a further electric machine 33 with a further drive shaft 32 is present.
  • the further drive shaft 32 is rotatably connected directly to the sun gear of the planetary PS.
  • the electric machine 2 drives the fluid pump 7.
  • the fluid pump 7 is not connected to the other electric machine 33 in terms of technology.
  • FIG 11 shows a transmission 1 according to an eleventh embodiment.
  • the transmission 1 shown in Figure 11 differs from the transmission 1 shown in Figure 9 in the coupling of the ring gear.
  • the ring gear of the planetary gearset PS by means of the second switching element K2 with the web of the planetary gear set PS rotatably connected.
  • the drive shaft 3 is no longer rotatably connected in this embodiment by means of the second switching element K2 with the ring gear.
  • the drive shaft 3 extends through the fluid pump 7 and with the sun gear of the planetary gearset PS technically connected, in particular rotatably connected.
  • FIG. 12 shows a twelfth exemplary embodiment of the transmission 1 according to the invention. It differs from the transmission 1 shown in FIG. 11 in that a further electric machine 33 with a further drive shaft 32 is present.
  • the further drive shaft 32 is rotatably connected directly to the sun gear of the planetary PS.
  • the electric machine 2 drives the fluid pump 7.
  • the fluid pump 7 is not connected to the further electric machine 33 in terms of drive technology.
  • Figure 13 shows a Getnebe 1 according to a thirteenth embodiment.
  • the transmission 1 shown in Figure 13 differs from the transmission 1 shown in Figure 9 in the arrangement of the first switching element K1 and the second switching element K2.
  • the first switching element K1 and the second switching element K2 are arranged offset from one another in the axial direction.
  • FIG. 14 shows a fourteenth embodiment of the transmission 1 according to the invention. It differs from the transmission 1 shown in FIG. 13 in that a further electric machine 33 with a further drive shaft 32 is present.
  • the further drive shaft 32 is rotatably connected directly to the sun gear of the planetary gearset PS.
  • the electric machine 2 drives the fluid pump 7.
  • the fluid pump 7 is not connected to the other electric machine 33 in terms of technology.
  • FIG. 15 shows a transmission 1 according to a fifteenth embodiment.
  • the transmission 1 shown in Figure 15 differs from the transmission shown in Figure 11 in the arrangement of the first switching element K1 and the second switching element K2.
  • the first switching element K1 and the second switching element K2 are arranged offset from one another in the axial direction.
  • FIG. 16 shows a sixteenth embodiment of the transmission 1 according to the invention. It differs from the transmission 1 shown in FIG. 15 in that a further electric machine 33 with a further drive shaft 32 is present.
  • the further drive shaft 32 is rotatably connected directly to the sun gear of the planetary PS.
  • the electric machine 2 drives the fluid pump 7. However, the fluid pump 7 is not connected to the other electric machine 33 in terms of technology.
  • FIG. 17 shows an alternative drive of the fluid pump 7.
  • the drive shown in FIG. 17 can be used instead of the drives for the fluid pump 7 shown in FIGS. 1, 3, 5, 7, 9, 11, 13 and 15.
  • the gearbox 1 has, in addition to the electric machine 2, another electric machine 9.
  • the transmission 1 has a summing gear 8.
  • a component of the summing 8 is connected to the fluid pump 7 drive technology and other component of the summation 8 is connected to the drive shaft 3 in terms of drive technology.
  • Another component of the summation 8 is connected to another drive shaft 19 of the other electric machine 9 in terms of drive technology.
  • FIG. 18 shows a switching matrix of the transmission illustrated in FIGS. 1 to 16.
  • each of the transmission has exactly two gears, namely a first gear G1 and a second gear G2.
  • the first gear G1 can be realized by closing the second switching element K2, wherein the first switching element K1 is open.
  • the second gear G2 can be realized by closing the first switching element K1, wherein the second switching element K2 is open.
  • FIG. 19 shows an electric vehicle 22 with a drive train 20 according to a first embodiment.
  • the drive train 20 has the transmission 1 shown in FIG and an axle differential 21.
  • the transmission output shaft 10 by means of a bevel gearbox 23 of the drive train 20 with the axle differential 21 is connected by drive technology.
  • the axle differential 21 in turn is connected to two vehicle wheels of the electric vehicle 22.
  • FIG. 19 shows a drive train 20 transverse to the direction of travel F of the electric vehicle 22, in particular a transverse transmission 1.
  • FIG. 20 shows an electric vehicle 22 with a drive train 20 according to a second embodiment.
  • the drive train 20 differs from the drive train 20 shown in FIG. 19 in that the drive train 20, in particular the transmission 1, is longitudinal to the travel direction F of the electric vehicle 22.
  • Another difference is that the transmission output shaft 10 directly and thus not by means of a bevel gear 23 with the axle differential 21 is connected by drive technology.
  • FIG. 21 shows an electric vehicle 22 with a drive train 20 according to a third embodiment.
  • the drive train 20 has the transmission 1 shown in FIG. 9 and an axle differential 21.
  • the transmission output shaft 10 is connected by means of a wheel 34 of the drive train 20 with the axle differential 21.
  • the wheels of the wheelset 34 have beveloid teeth.
  • the axle differential 21 in turn is connected to two vehicle wheels of the electric vehicle 22 in terms of drive technology.
  • the transmission output shaft 10 is connected by means of a hang-on clutch 35 with another axle differential 36.
  • the other axle differential 36 is connected to two other vehicle wheels of the electric vehicle 22 in terms of drive technology.
  • the drive train 20 shown in FIG. 22 runs along the direction of travel F of the electric vehicle 22.
  • FIG. 22 shows an electric vehicle 22 with a drive train 20 according to a fourth embodiment.
  • the drive train 20 differs from the drive train 20 shown in FIG. 21 in that the drive train 20, in particular the transmission 1, is transverse to the travel direction F of the electric vehicle 22.
  • Another Difference is that the transmission output shaft 10 by means of the bevel gear 23 with the axle differential 21 is connected by drive technology.
  • the transmission output shaft 10 is connected by means of the bevel gear 23 and the hang-on clutch 35 with the other axle differential 36.

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

Abstract

L'invention concerne une transmission pour un véhicule électrique, laquelle comprend une machine électrique comportant un arbre primaire, un premier élément de passage de vitesse, un second élément de passage de vitesse et une boîte de vitesses manuelle, l'actionnement du premier élément de passage de vitesse et/ou du second élément de passage de vitesse permettant d'enclencher une vitesse de la boîte de vitesses manuelle. La transmission se caractérise en ce que la machine électrique est en permanence reliée en entraînement à une pompe à fluide.
PCT/EP2018/078274 2017-11-10 2018-10-16 Transmission pour véhicule automobile WO2019091719A1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102017220073.1A DE102017220073A1 (de) 2017-11-10 2017-11-10 Getriebe für ein Elektrofahrzeug
DE102017220073.1 2017-11-10

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WO2019091719A1 true WO2019091719A1 (fr) 2019-05-16

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WO2021208972A1 (fr) * 2020-04-15 2021-10-21 Valeo Powertrain (shanghai) Co., Ltd. Système de chaîne cinématique pour véhicule à propulsion électrique

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JP2020118175A (ja) * 2019-01-21 2020-08-06 永順通科技有限公司Ｙｏｎｇ Ｓｈｕｎ Ｔｕｎｇ Ｔｅｃｈｎｏｌｏｇｉｅｓ Ｃｏ．， Ｌｔｄ． ハブ変速機モータ
DE102019208856A1 (de) * 2019-06-18 2020-12-24 Zf Friedrichshafen Ag Elektrofahrzeuggetriebe
DE102019119954B4 (de) * 2019-07-24 2023-04-20 Schaeffler Technologies AG & Co. KG Antriebsvorrichtung für ein Kraftfahrzeug mit gemeinsamem starren Hohlrad und gemeinsamem starren Planetenradträger
FR3102525B1 (fr) * 2019-10-25 2021-10-08 Valeo Embrayages Système de propulsion pour un véhicule.
DE102021209593A1 (de) * 2021-09-01 2023-03-02 Zf Friedrichshafen Ag Antriebseinheit für ein Elektrofahrzeug
FR3131711A1 (fr) * 2022-01-08 2023-07-14 Valeo Embrayages Systeme de propulsion pour vehicule electrique

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