WO2026025334A1 - Differential transmission for a vehicle - Google Patents

Differential transmission for a vehicle

Info

Publication number
WO2026025334A1
WO2026025334A1 PCT/CN2024/108735 CN2024108735W WO2026025334A1 WO 2026025334 A1 WO2026025334 A1 WO 2026025334A1 CN 2024108735 W CN2024108735 W CN 2024108735W WO 2026025334 A1 WO2026025334 A1 WO 2026025334A1
Authority
WO
WIPO (PCT)
Prior art keywords
planetary gearset
differential transmission
planet carrier
coupling element
sun 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.)
Pending
Application number
PCT/CN2024/108735
Other languages
French (fr)
Inventor
Yechen ZHANG
Martin Brehmer
Matthias Reisch
Qing Zhou
Haihua Huang
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
Priority to PCT/CN2024/108735 priority Critical patent/WO2026025334A1/en
Publication of WO2026025334A1 publication Critical patent/WO2026025334A1/en
Pending legal-status Critical Current
Anticipated expiration legal-status Critical

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
    • F16H48/00—Differential gearings
    • F16H48/06—Differential gearings with gears having orbital motion
    • F16H48/10—Differential gearings with gears having orbital motion with orbital spur 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
    • F16H48/00—Differential gearings
    • F16H48/06—Differential gearings with gears having orbital motion
    • F16H48/10—Differential gearings with gears having orbital motion with orbital spur gears
    • F16H2048/104—Differential gearings with gears having orbital motion with orbital spur gears characterised by two ring 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
    • F16H48/00—Differential gearings
    • F16H48/06—Differential gearings with gears having orbital motion
    • F16H48/10—Differential gearings with gears having orbital motion with orbital spur gears
    • F16H2048/106—Differential gearings with gears having orbital motion with orbital spur gears characterised by two sun gears

Definitions

  • the present disclosure relates to a differential transmission for a vehicle. Furthermore, the present disclosure relates to a driving arrangement comprising such a differential transmission, and to a vehicle comprising such a driving arrangement.
  • Vehicles e.g., passenger cars, exhibit a differential transmission to allow for rotation of wheels at different speeds. Furthermore, in the course of the electrification of the drivetrains of vehicles, electric axles have been developed, in which an electric motor and such a differential transmission are combined for driving the vehicle.
  • the present disclosure relates to a differential transmission for a vehicle.
  • the vehicle may be a passenger car or an arbitrary other vehicle.
  • the differential transmission may allow for two driving axles and/or wheels coupled to the differential transmission to rotate at different speeds, e.g., when driving with the vehicle around a curve.
  • the differential transmission comprises first and second output shafts.
  • Each of the output shafts of the differential transmission may be mechanically couplable to a driving axle, which may respectively support a wheel.
  • the output shafts may be arranged coaxially to each other. In an embodiment, the entire differential transmission is arranged coaxially to both output shafts.
  • the differential transmission may further comprise an input shaft, which may be arranged coaxially to one or both of the output shafts and which may be provided as a hollow shaft radially outside of one of the output shafts.
  • the input shaft may be mechanically couplable to a motor, e.g., an electric motor, for supplying a torque into the differential transmission.
  • the differential transmission may be configured to transmit the torque provided at the input shaft to the output shafts for driving the vehicle. Therefore, the differential transmission of the present disclosure may exhibit, besides the differential functionality, a functionality for transmitting a torque of a motor from the input shaft to the output shafts for driving the vehicle.
  • the differential transmission may provide a gear ration in between the input and the output shafts.
  • the gear ratio may be larger than 1, optionally larger than 5, in an embodiment larger than 10.
  • the differential transmission comprises a first planetary gearset with a sun gear, a planet carrier and a ring gear as well as a second planetary gearset with a sun gear, a planet carrier and a ring gear.
  • the first planetary gearset is mechanically coupled to the first output shaft.
  • one of the sun gear and the planet carrier of the first planetary gearset is mechanically coupled to the first output shaft.
  • the second planetary gearset is mechanically coupled to the second output shaft via a connecting element.
  • one of the planet carrier and the ring gear of the second planetary gearset is mechanically coupled to the second output shaft via the connecting element.
  • the connecting element may be integrally formed with either the ring gear or the planet carrier of the second planetary gearset or may be provided as a separate part, which may be torque-proofly connected to the corresponding element. Additionally or alternatively, the connecting element may be integrally formed with the second output shaft or may be provided as a separate element, which may be torque-proofly connected to said output shaft.
  • the ring gear of the first planetary gearset is torque-proofly connected to the sun gear of the second planetary gearset via a coupling element.
  • the coupling element may be formed by multiple parts, which may be torque-proofly connected to each other. Additionally or alternatively, the coupling element may be integrally formed from a single part.
  • the coupling element may form the ring gear of the first planetary gearset and the sun gear of the second planetary gearset. Alternatively, one or both of the ring gear of the first planetary gearset and the sun gear of the second planetary gearset may be provided as separate parts, which may be torque-proofly connected to the coupling element.
  • the coupling element comprises a bearing portion, which may be integrally formed with the coupling element or may be provided as a separate part. If it is provided as a separate part, it may be torque-proofly connected to the coupling element.
  • the bearing portion of the coupling element engages, e.g., contacts, the planet carrier of the first planetary gearset and the connecting element, which mechanically couples the second planetary gearset with the second output shaft. More precisely, the bearing portion of the coupling element engages both the planet carrier and the connecting element in such a way that an axial movement of the coupling element is limited, e.g., prevented. In other words, the coupling element is supported in the axial direction via the bearing portion engaging both the planet carrier of the first planetary gearset and the connecting element. In an embodiment, this is the only axial support of the coupling element.
  • the first planetary gearset and the second planetary gearset are displaced with respect to each other in the axial direction of the differential transmission.
  • the first planetary gearset and the second planetary gearset may be arranged behind each other in the axial direction, while being mechanically coupled with each other via the coupling element.
  • the first planetary gearset and the second planetary gearset may be stacked onto each other, i.e., arranged behind one another.
  • This embodiment provides the technical advantage that the coupling element may be axially supported in the above-described manner in a simple and low complex way.
  • the first and the second planetary gearsets are aligned with each other in the axial direction, while being stacked onto each other in the radial direction.
  • the coupling element comprises a ring gear section comprising the ring gear of the first planetary gearset and a sun gear section comprising the sun gear of the second planetary gearset.
  • the coupling element may be integrally formed and the ring and sun gear sections may therefore be portions of said integrally formed coupling element.
  • the ring gear section may be configured with a larger diameter than the sun gear section.
  • the coupling element may exhibit a step portion in radial direction in between the ring gear section and the sun gear section. Therefore, in a cross-sectional view, the coupling element may exhibit a Z- like configuration. This design has the advantage that the radial extension of the differential transmission may be relatively compact.
  • the bearing portion of the coupling element may extend radially inward from the sun gear section towards the planet carrier of the first planetary gearset. Due to the provision of the bearing portion at the sun gear section having a smaller diameter than the ring gear section, the bearing portion is moved radially inward towards the planet carrier of the first planetary gearset. This has the advantage that the radial extent of the bearing portion is reduced, thereby improving the mechanical properties of the transmission.
  • the connecting element which mechanically couples the second planetary gearset with the second output shaft, has an axial portion extending towards the planet carrier of the first planetary gearset.
  • the axial portion may be provided radially inward of the sun gear section of the coupling element.
  • the connecting element may exhibit a first radial portion for connecting the axial portion with the ring gear of the second planetary gearset, for example.
  • the first radial portion may be provided behind the coupling element in an axial direction of the differential transmission when viewed from the first planetary gearset.
  • the extension towards the planet carrier of the axial portion of the connecting element may be provided to form a gap in between the planet carrier of the first planetary gearset and said connecting element. Within said gap, the bearing portion of the coupling element may be provided.
  • the connecting element exhibits a second radial portion, which may be mechanically coupled to the axial portion, and which may comprise a contact surface facing the planet carrier of the first planetary gearset.
  • the contact surface may be arranged in parallel to an opposite surface of the planet carrier of the first planetary gearset.
  • the gap may be formed by two parallel surfaces of the planet carrier and the connecting element, respectively.
  • the bearing portion and the gap are designed in such a way that the bearing portion is contacted by both the planet carrier and the connecting element for limiting the axial movement of the coupling element.
  • the bearing portion of the coupling element is formed by a separate part mounted to the coupling element.
  • the separate part may be a stamping part, which may be riveted and/or pressed and/or attached by other means to the coupling element.
  • the manufacturing of the coupling element may be less complex and cheaper.
  • the material of the bearing portion may be chosen differently from the material of the remaining coupling element.
  • the bearing portion is integrally formed with the coupling element.
  • the planet carrier of the first planetary gearset comprises an abutment portion for engaging the bearing portion of the coupling element.
  • multiple abutment portion are provided, which may be spaced equidistantly around a circumference of the planet carrier of the first planetary gearset.
  • Adjacent the abutment portion a lubrication channel for allowing a lubricant to flow in a radial outward direction through the lubrication channel to a planet gear on the planet carrier of the first planetary gearset may be provided.
  • the planet carrier may exhibit one or more abutment portions, which protrude from the planet carrier, for engaging the bearing portion of the coupling element.
  • the planet carrier may comprise one or more lubricant channels provided adjacent the abutment portions for allowing a flow of a lubricant in a radial direction towards a planet gear of the planet carrier of the first planetary gearset.
  • the lubricant may be oil.
  • a guiding element may be provided, which may comprise an opening for accommodating the abutment portion. If the planet carrier comprises multiple abutment portions, the guiding element may comprise multiple openings, each being configured to accommodate one of the abutment portions of the planet carrier. The opening may be formed as a though passage such that the abutment portion may extend all the way through the guiding element. Furthermore, the guiding element may be configured to guide a lubricant flowing radially outward through the lubricant channel for supplying the lubricant to a planet gear of the planet carrier of the first planetary gearset. In an embodiment, the guiding element may border the lubricant channel.
  • the lubricant channel may be bordered by a side surface of the planet carrier, two adjacent abutment portions of the planet carrier and the guiding element. These components/parts together may form the lubricant channel configured to guide the lubricant in between the abutment portions along the planet carrier towards one or more planet gears of the planet carrier of the first planetary gearset.
  • the differential transmission further comprises a stationary element, which may be provided by a housing.
  • the differential transmission may comprise an input shaft, which may be configured as the input shaft described above.
  • the housing may house the entire differential transmission but may exhibit openings for the input shaft and the output shafts.
  • the sun gear of the first planetary gearset may be mechanically coupled, e.g., torque-proofly connected, to the input shaft.
  • the planet carrier of the first planetary gearset may be mechanically coupled, e.g., torque-proofly connected, to the first output shaft.
  • the planet carrier of the second planetary gearset may be mechanically coupled, e.g., torque-proofly connected, to the stationary element.
  • the ring gear of the second planetary gearset may be mechanically coupled to the second output shaft, e.g., torque-proofly connected to the second output shaft.
  • the above-described axial support of the coupling element may be implemented in a particularly easy fashion.
  • the present disclosure further relates to a driving arrangement comprising a motor, e.g., an electric motor, and a differential transmission according to one of the previously described embodiments.
  • the motor is mechanically coupled, e.g., torque-proofly connected, to the input of the differential transmission.
  • the motor and the differential transmission are arranged coaxially with respect to each other.
  • the motor may be provided coaxially and radially outside of one of the outputs of the differential transmission. In axial direction, the motor may be provided in front of the input of the differential transmission.
  • the present disclosure relates to a vehicle comprising such a driving arrangement. Concerning the understanding and the advantages of the individual features, it is referred to the above description in connection with the differential transmission according to the present disclosure.
  • Figure 1 shows a vehicle comprising a driving arrangement according to an embodiment.
  • Figure 2 shows the driving arrangement of Figure 1 comprising a differential transmission according to an embodiment.
  • Figure 3 shows the differential transmission of the driving arrangement of Figure 2 according to an embodiment.
  • Figure 4 shows a cross-sectional view of the differential transmission of Figure 3 according to an embodiment.
  • Figure 5 shows a planet carrier of the differential transmission of Figure 4.
  • Figure 6 shows a guiding element of the differential transmission of Figure 4.
  • FIG 1 shows a vehicle 100 comprising a driving arrangement 1 according to an embodiment.
  • the vehicle 100 is a passenger car.
  • the driving arrangement 1 is an electric axle of the passenger car 100 comprising a differential transmission 10 and an electric motor 2.
  • the motor 2 and the differential transmission 10 are arranged coaxially to each other.
  • the driving arrangement 1 further comprises a first driving axle 3 and a second driving axle 4, which are each mechanically coupled to a wheel 5 of the vehicle 100.
  • the axles 3 and 4 are coaxially arranged to the motor 2 and the differential transmission 10 as shown in Figure 2.
  • the differential transmission 10 of the driving arrangement 1 of the vehicle 100 serves two functions. Firstly, it provides a differential mechanism for allowing the wheels 5 and therefore the drive axles 3 and 4 to rotate at different rotational speeds.
  • the gear ratio is larger than 5, e.g., larger than 10.
  • the driving arrangement 1 is configured to transmit a torque of the motor 2 via the differential transmission 10 to both axles 3 and 4 and thus the wheels 5 for driving the vehicle 100.
  • FIG 3 shows the differential transmission 10 of the driving arrangement 1 of Figure 2 according to an embodiment.
  • the differential transmission 10 comprises an input shaft 11 and two output shafts 12 and 13.
  • the output shafts 12 and 13 are coaxially aligned with each other and are each torque-proofly mechanically connected to a drive axle 3 and 4, respectively.
  • the input shaft 11 is configured as a hollow shaft and is provided coaxially but radially outside of the first output shaft 12.
  • the input shaft 11 is torque-proofly mechanically connected to the motor 2 for supplying a motor torque to the differential transmission 10.
  • the torque is then transmitted with the gear ratio of the transmission 10 to the output shafts 12 and 13 and thus the drive axles 3 and 4.
  • the differential transmission 10 comprises a housing 16, which forms a stationary element.
  • the housing 16 houses the entire differential transmission 10 but exhibits openings for the input shaft 11 and the output shafts 12 and 13, which respectively extend out of the housing 16.
  • the differential transmission 10 comprises a first planetary gearset 14 and a second planetary gearset 15.
  • the first planetary gearset 14 comprises a sun gear 17, a planet carrier 18 and a ring gear 19.
  • the second planetary gearset 15 comprises a sun gear 20, a planet carrier 21 and a ring gear 22.
  • both the first and the second planetary gearsets 14 and 15 are formed as minus-planetary gearsets.
  • the first and the second planetary gearsets 14 and 15 are displaced with respect to each other in an axial direction of the differential transmission 10, i.e., in a direction of the output shafts 12 and 13. More precisely, the first and the second planetary gearsets 14 and 15 are stacked in a radial direction of the differential transmission 10 but are provided behind each other in an axial direction of the differential transmission 10.
  • the sun gear 17 of the first planetary gearset 14 is torque-proofly connected to the input shaft 11. Furthermore, the planet carrier 18 of the first planetary gearset 14 is torque-proofly connected to the first output shaft 12. Furthermore, the ring gear 19 of the first planetary gearset 14 is torque-proofly connected to the sun gear 20 of the second planetary gearset 15.
  • the differential transmission 10 comprises a coupling element 30, which forms both the ring gear 19 and the sun gear 20.
  • the planet carrier 21 of the second planetary gearset 15 is torque-proofly connected to the housing 16. Furthermore, the ring gear 22 of the second planetary gearset 15 is torque-proofly connected to the second output shaft 13.
  • Both the first planet carrier 18 of the first planetary gearset 14 and the second planet carrier 21 of the second planetary gearset 15 comprise multiple planet gears 23 and 24, respectively.
  • the number of planet gears 24 of the second planetary gearset 15 is larger than the number of planet gears 23 of the first planetary gearset 14.
  • the differential transmission 10 of the present embodiment comprises eight planet gears 24 on the second planet carrier 21 of the second planetary gearset 15 and four planet gears 23 on the first planet carrier 18 of the first planetary gearset 14.
  • Figure 4 shows a cross-sectional view of the differential transmission 10 of Figure 3 according to an embodiment.
  • the sun gear 17 of the first planetary gearset 14, the planet gears 23 of the first planetary gearset 14, the housing 16 and the input shaft 11 are not shown.
  • the coupling element 30, which torque-proofly connects the ring gear 19 of the first planetary gearset 14 with the sun gear 20 of the second planetary gearset 15 comprises a ring gear section 31, which forms the ring gear 19, and a sun gear section 32, which forms the sun gear 20.
  • the ring gear section 31 and the sun gear section 32 are torque-proofly connected, while the ring gear section 31 exhibits a larger diameter than the sun gear section 32. Accordingly, the coupling element 30 exhibits a step radially inward from the first planetary gearset 14 to the second planetary gearset 15.
  • the side surfaces 33 and 34 are connected to each other with multiple bridges 35 extending in the axial direction of the differential transmission 10.
  • the bridges 35 are provided in between support structures 36 for supporting axles (not shown) for the planet gears 23 of the first planetary gearset 14.
  • the planet carrier 18 exhibits a fixing portion 37 for fixing the planet carrier 18 to the first output shaft 12.
  • the planet carrier 18 is fixed to the first output shaft 12 via the fixing portion 37 and the extends radially outward via the side surface 33 up to the bridge 35 provided at the radial outer end.
  • the step portion of the coupling element 30 is provided radially outside of the bridges 35 of the planet carrier 18 and approximately at the same axial height of the side surface 33 of planet carrier 18. This implies that, in the axial direction of the differential transmission 10, the sun gear section 32 of the coupling element 30 extends away from the side surface 33 of the planet carrier 18.
  • the planet carrier 21 with its planet gears 24 as well as the ring gear 22 of the second planet carrier 15 are provided approximately at the same axial height of the sun gear section 32 of the coupling element 30. However, in the radial direction, the planet carrier 21 with the planet gears 24 of the second planetary gearset 15 is provided radially outward of the sun gear section 32 of the coupling element 30.
  • the ring gear 22 of the second planetary gearset 15 is provided radially outward of the planet gears 24 of the second planetary gearset 15. As described above in connection with Figure 3, the ring gear 22 of the second planetary gearset 15 is torque-proofly connected to the second output shaft 13, which is also shown in Figure 4.
  • the first output shaft 12 is supported within the second output shaft 13 via a bearing 38. Accordingly, the first and the second output shafts 12 and 13 overlap with each other in an axial direction of the differential transmission 10. The overlap is configured in such a way that the second output shaft 13 extends all the way up to the side surface 33 of the planet carrier 18 and therefore also axially overlaps the fixing portion 37.
  • the differential transmission 10 comprises a connecting element 39, which torque-proofly connects the ring gear 22 of the second planetary gearset 15 with the second output shaft 13.
  • the connecting element 39 comprises a first radial portion 40 extending radially inward from the ring gear 22 of the second planetary gearset 15, an axial portion 41 and a second radial portion 42.
  • the first radial portion 40 is, in axial direction of the differential transmission 10, provided behind the planet gears 24 of the second planetary gearset 15 when viewed from the planet carrier 18 of the first planetary gearset 14. It extends radially downward to a position below the sun gear section 32 of the coupling element 30.
  • the axial portion 41 extends in axial direction towards the side surface 33 of the planet carrier 18.
  • the second radial portion 42 extends further radially inward towards the second output shaft 13 and is connected thereto in a torque-proofly manner.
  • the first radial portion 40, the axial portion 41 and the second radial portion 42 are formed integrally with each other.
  • the second radial portion 42 forms a contact surface 43 facing towards the side surface 33 of the planet carrier 18 and being oriented parallel thereto.
  • the planet carrier 18 comprises on its side surface 33 several abutment portions 44, which are provided in between the supporting structures 36 for the planet gears 23. In between said abutment portions 44, voids forming oil channels 45 are provided. The abutment portions 44 and the oil channels 45 are provided at the radial height of the second radial portion 42 of the connecting element 39. In between the abutment portions 44 and the contact surface 43 of the second radial portion 42 of the connecting element 40 a gap is provided.
  • the coupling element 30 comprises a bearing portion 46.
  • the bearing portion 46 is a stamping part being pressed and/or riveted to the inner face of the sun gear section 32 of the coupling element 30.
  • the bearing portion 46 is torque-proofly connected with the sun gear section 32 of the coupling element 30. It extends radially inward into the gap between the abutment portions 44 of the planet carrier 18 and the contact surface 43 of the connecting element 40.
  • the bearing portion 46, the abutment portion 44 and the contact surface 43 are designed in such a way that the bearing portion 46 engages both the abutment surfaces 44 and the contact surface 43. Accordingly, the axial movement of the coupling element 30 is limited by the bearing portion 46 engaging the abutment portions 44 of the planet carrier 18 and the contact surface 43 of the connecting element 39.
  • the provision of the oil channels 45 allow for a passage of oil from an area around the fixing portion 37 of the planet carrier 18 through the oil channels 45 to planet gears 23 of the planet carrier 18 of the first planetary gearset 14.
  • the oil may pass along the side surface 33 through the oil passages 45 to the planet gears 23.
  • the oil channels 45 are bordered by a guiding element 47 shown in Figure 6.
  • the guiding element 47 exhibits a ring shape having openings 48 for accommodating the abutment portions 44 of the planet carrier 18.
  • the guiding element 47 is mounted to the side surface 33 of the planet carrier 18, in the present embodiment via screws 49, such that the abutment portions 44 extend through the openings 48.
  • the guiding element 47 forms the oil channels 45 in between the abutment portions 44 and is configured to guide oil coming from an area around the fixing portion 37 of the planet carrier 18 into the supporting structures 36 and therefore to the planet gears 23 of the first planetary gearset 14.

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Abstract

The present disclosure relates to a differential transmission (10) for a vehicle (100) comprising a first and a second output shaft (12, 13), a first planetary gearset (14) as well as a second planetary gearset (15). The first planetary gearset (14) is mechanically coupled to the first output shaft (12) and the second planetary gearset (15) is mechanically coupled to the second output shaft (13) via a connecting element (39). A ring gear (19) of the first planetary gearset (14) is torque-proofly connected to a sun gear (22) of the second planetary gearset (15) via a coupling element (30) having a bearing portion (46). The bearing portion (46) of the coupling element (30) engages a planet carrier (18) of the first planetary gearset (14) and the connecting element (39) to limit a movement of the coupling element (30) in an axial direction.

Description

Differential transmission for a vehicle Technical field
The present disclosure relates to a differential transmission for a vehicle. Furthermore, the present disclosure relates to a driving arrangement comprising such a differential transmission, and to a vehicle comprising such a driving arrangement.
Prior art
Vehicles, e.g., passenger cars, exhibit a differential transmission to allow for rotation of wheels at different speeds. Furthermore, in the course of the electrification of the drivetrains of vehicles, electric axles have been developed, in which an electric motor and such a differential transmission are combined for driving the vehicle.
Summary of the invention
The present disclosure relates to a differential transmission for a vehicle. The vehicle may be a passenger car or an arbitrary other vehicle. The differential transmission may allow for two driving axles and/or wheels coupled to the differential transmission to rotate at different speeds, e.g., when driving with the vehicle around a curve. The differential transmission comprises first and second output shafts. Each of the output shafts of the differential transmission may be mechanically couplable to a driving axle, which may respectively support a wheel. The output shafts may be arranged coaxially to each other. In an embodiment, the entire differential transmission is arranged coaxially to both output shafts. The differential transmission may further comprise an input shaft, which may be arranged coaxially to one or both of the output shafts and which may be provided as a hollow shaft radially outside of one of the output shafts. The input shaft may be mechanically couplable to a motor, e.g., an electric motor, for supplying a torque into the differential transmission. The differential transmission may be configured to transmit the torque provided at the input shaft to the output shafts for driving the vehicle. Therefore, the differential transmission of the present disclosure may exhibit, besides the differential functionality, a functionality for transmitting a torque of a motor from the input shaft to the output shafts for driving the vehicle. The differential  transmission may provide a gear ration in between the input and the output shafts. The gear ratio may be larger than 1, optionally larger than 5, in an embodiment larger than 10.
The differential transmission comprises a first planetary gearset with a sun gear, a planet carrier and a ring gear as well as a second planetary gearset with a sun gear, a planet carrier and a ring gear. The first planetary gearset is mechanically coupled to the first output shaft. For example, one of the sun gear and the planet carrier of the first planetary gearset is mechanically coupled to the first output shaft. Furthermore, the second planetary gearset is mechanically coupled to the second output shaft via a connecting element. For example, one of the planet carrier and the ring gear of the second planetary gearset is mechanically coupled to the second output shaft via the connecting element. The connecting element may be integrally formed with either the ring gear or the planet carrier of the second planetary gearset or may be provided as a separate part, which may be torque-proofly connected to the corresponding element. Additionally or alternatively, the connecting element may be integrally formed with the second output shaft or may be provided as a separate element, which may be torque-proofly connected to said output shaft.
The ring gear of the first planetary gearset is torque-proofly connected to the sun gear of the second planetary gearset via a coupling element. The coupling element may be formed by multiple parts, which may be torque-proofly connected to each other. Additionally or alternatively, the coupling element may be integrally formed from a single part. The coupling element may form the ring gear of the first planetary gearset and the sun gear of the second planetary gearset. Alternatively, one or both of the ring gear of the first planetary gearset and the sun gear of the second planetary gearset may be provided as separate parts, which may be torque-proofly connected to the coupling element. The coupling element comprises a bearing portion, which may be integrally formed with the coupling element or may be provided as a separate part. If it is provided as a separate part, it may be torque-proofly connected to the coupling element.
The bearing portion of the coupling element engages, e.g., contacts, the planet carrier of the first planetary gearset and the connecting element, which mechanically couples the second planetary gearset with the second output shaft. More precisely, the bearing  portion of the coupling element engages both the planet carrier and the connecting element in such a way that an axial movement of the coupling element is limited, e.g., prevented. In other words, the coupling element is supported in the axial direction via the bearing portion engaging both the planet carrier of the first planetary gearset and the connecting element. In an embodiment, this is the only axial support of the coupling element.
By providing an axial support for the coupling element via the bearing portion engaging both the planet carrier and the connecting element, a differential transmission with good reliability is provided. This due to the fact that the location and arrangement of the axial support of the coupling element reduces the risk of relative movements and stresses in the differential transmission, inter alia due to a limitation of a tilting of the coupling element.
In an embodiment, the first planetary gearset and the second planetary gearset are displaced with respect to each other in the axial direction of the differential transmission. For example, the first planetary gearset and the second planetary gearset may be arranged behind each other in the axial direction, while being mechanically coupled with each other via the coupling element. At the same time, in the radial direction of the differential transmission, the first planetary gearset and the second planetary gearset may be stacked onto each other, i.e., arranged behind one another. This embodiment provides the technical advantage that the coupling element may be axially supported in the above-described manner in a simple and low complex way. In an alternative embodiment, the first and the second planetary gearsets are aligned with each other in the axial direction, while being stacked onto each other in the radial direction.
In an embodiment, the coupling element comprises a ring gear section comprising the ring gear of the first planetary gearset and a sun gear section comprising the sun gear of the second planetary gearset. As described above, the coupling element may be integrally formed and the ring and sun gear sections may therefore be portions of said integrally formed coupling element. The ring gear section may be configured with a larger diameter than the sun gear section. In other words, the coupling element may exhibit a step portion in radial direction in between the ring gear section and the sun gear section. Therefore, in a cross-sectional view, the coupling element may exhibit a Z- like configuration. This design has the advantage that the radial extension of the differential transmission may be relatively compact. Furthermore, the bearing portion of the coupling element may extend radially inward from the sun gear section towards the planet carrier of the first planetary gearset. Due to the provision of the bearing portion at the sun gear section having a smaller diameter than the ring gear section, the bearing portion is moved radially inward towards the planet carrier of the first planetary gearset. This has the advantage that the radial extent of the bearing portion is reduced, thereby improving the mechanical properties of the transmission.
In an embodiment, the connecting element, which mechanically couples the second planetary gearset with the second output shaft, has an axial portion extending towards the planet carrier of the first planetary gearset. The axial portion may be provided radially inward of the sun gear section of the coupling element. In addition, the connecting element may exhibit a first radial portion for connecting the axial portion with the ring gear of the second planetary gearset, for example. The first radial portion may be provided behind the coupling element in an axial direction of the differential transmission when viewed from the first planetary gearset. The extension towards the planet carrier of the axial portion of the connecting element may be provided to form a gap in between the planet carrier of the first planetary gearset and said connecting element. Within said gap, the bearing portion of the coupling element may be provided.
In an embodiment, the connecting element exhibits a second radial portion, which may be mechanically coupled to the axial portion, and which may comprise a contact surface facing the planet carrier of the first planetary gearset. The contact surface may be arranged in parallel to an opposite surface of the planet carrier of the first planetary gearset. Accordingly, the gap may be formed by two parallel surfaces of the planet carrier and the connecting element, respectively. In an embodiment, the bearing portion and the gap are designed in such a way that the bearing portion is contacted by both the planet carrier and the connecting element for limiting the axial movement of the coupling element.
According to an embodiment, the bearing portion of the coupling element is formed by a separate part mounted to the coupling element. The separate part may be a stamping part, which may be riveted and/or pressed and/or attached by other means to the coupling element. By providing the bearing portion as a separate part, the  manufacturing of the coupling element may be less complex and cheaper. Furthermore, the material of the bearing portion may be chosen differently from the material of the remaining coupling element. In an alternative embodiment, the bearing portion is integrally formed with the coupling element.
In an embodiment, the planet carrier of the first planetary gearset comprises an abutment portion for engaging the bearing portion of the coupling element. In an embodiment, multiple abutment portion are provided, which may be spaced equidistantly around a circumference of the planet carrier of the first planetary gearset. Adjacent the abutment portion, a lubrication channel for allowing a lubricant to flow in a radial outward direction through the lubrication channel to a planet gear on the planet carrier of the first planetary gearset may be provided. In other words, in this embodiment, the planet carrier may exhibit one or more abutment portions, which protrude from the planet carrier, for engaging the bearing portion of the coupling element. In addition, the planet carrier may comprise one or more lubricant channels provided adjacent the abutment portions for allowing a flow of a lubricant in a radial direction towards a planet gear of the planet carrier of the first planetary gearset. The lubricant may be oil. This embodiment has the advantage that the axial support of the coupling element and the lubrication of the planet gears on the first planetary gearset are efficiently combined with each other.
A guiding element may be provided, which may comprise an opening for accommodating the abutment portion. If the planet carrier comprises multiple abutment portions, the guiding element may comprise multiple openings, each being configured to accommodate one of the abutment portions of the planet carrier. The opening may be formed as a though passage such that the abutment portion may extend all the way through the guiding element. Furthermore, the guiding element may be configured to guide a lubricant flowing radially outward through the lubricant channel for supplying the lubricant to a planet gear of the planet carrier of the first planetary gearset. In an embodiment, the guiding element may border the lubricant channel. For example, the lubricant channel may be bordered by a side surface of the planet carrier, two adjacent abutment portions of the planet carrier and the guiding element. These components/parts together may form the lubricant channel configured to guide the  lubricant in between the abutment portions along the planet carrier towards one or more planet gears of the planet carrier of the first planetary gearset.
In an embodiment, the differential transmission further comprises a stationary element, which may be provided by a housing. Furthermore, the differential transmission may comprise an input shaft, which may be configured as the input shaft described above. The housing may house the entire differential transmission but may exhibit openings for the input shaft and the output shafts. The sun gear of the first planetary gearset may be mechanically coupled, e.g., torque-proofly connected, to the input shaft. The planet carrier of the first planetary gearset may be mechanically coupled, e.g., torque-proofly connected, to the first output shaft. The planet carrier of the second planetary gearset may be mechanically coupled, e.g., torque-proofly connected, to the stationary element. Furthermore, the ring gear of the second planetary gearset may be mechanically coupled to the second output shaft, e.g., torque-proofly connected to the second output shaft. In a differential transmission according to this embodiment, the above-described axial support of the coupling element may be implemented in a particularly easy fashion.
The present disclosure further relates to a driving arrangement comprising a motor, e.g., an electric motor, and a differential transmission according to one of the previously described embodiments. The motor is mechanically coupled, e.g., torque-proofly connected, to the input of the differential transmission. In an embodiment, the motor and the differential transmission are arranged coaxially with respect to each other. The motor may be provided coaxially and radially outside of one of the outputs of the differential transmission. In axial direction, the motor may be provided in front of the input of the differential transmission. Furthermore, the present disclosure relates to a vehicle comprising such a driving arrangement. Concerning the understanding and the advantages of the individual features, it is referred to the above description in connection with the differential transmission according to the present disclosure.
Brief description of the figures
Figure 1 shows a vehicle comprising a driving arrangement according to an embodiment.
Figure 2 shows the driving arrangement of Figure 1 comprising a differential transmission according to an embodiment.
Figure 3 shows the differential transmission of the driving arrangement of Figure 2 according to an embodiment.
Figure 4 shows a cross-sectional view of the differential transmission of Figure 3 according to an embodiment.
Figure 5 shows a planet carrier of the differential transmission of Figure 4.
Figure 6 shows a guiding element of the differential transmission of Figure 4.
Detailed description of embodiments
Figure 1 shows a vehicle 100 comprising a driving arrangement 1 according to an embodiment. In the present embodiment, the vehicle 100 is a passenger car. The driving arrangement 1 is an electric axle of the passenger car 100 comprising a differential transmission 10 and an electric motor 2. As shown in Figure 2, the motor 2 and the differential transmission 10 are arranged coaxially to each other. The driving arrangement 1 further comprises a first driving axle 3 and a second driving axle 4, which are each mechanically coupled to a wheel 5 of the vehicle 100. The axles 3 and 4 are coaxially arranged to the motor 2 and the differential transmission 10 as shown in Figure 2. The differential transmission 10 of the driving arrangement 1 of the vehicle 100 serves two functions. Firstly, it provides a differential mechanism for allowing the wheels 5 and therefore the drive axles 3 and 4 to rotate at different rotational speeds. Secondly, it functions as a gear to transmit a torque of the motor 2 to the drive axles 3 and 4 and therefore the wheels 5 with a certain gear ratio. In the present embodiment, the gear ratio is larger than 5, e.g., larger than 10. The driving arrangement 1 is configured to transmit a torque of the motor 2 via the differential transmission 10 to both axles 3 and 4 and thus the wheels 5 for driving the vehicle 100.
Figure 3 shows the differential transmission 10 of the driving arrangement 1 of Figure 2 according to an embodiment. The differential transmission 10 comprises an input shaft  11 and two output shafts 12 and 13. The output shafts 12 and 13 are coaxially aligned with each other and are each torque-proofly mechanically connected to a drive axle 3 and 4, respectively. The input shaft 11 is configured as a hollow shaft and is provided coaxially but radially outside of the first output shaft 12. The input shaft 11 is torque-proofly mechanically connected to the motor 2 for supplying a motor torque to the differential transmission 10. The torque is then transmitted with the gear ratio of the transmission 10 to the output shafts 12 and 13 and thus the drive axles 3 and 4. The differential transmission 10 comprises a housing 16, which forms a stationary element. The housing 16 houses the entire differential transmission 10 but exhibits openings for the input shaft 11 and the output shafts 12 and 13, which respectively extend out of the housing 16.
The differential transmission 10 comprises a first planetary gearset 14 and a second planetary gearset 15. The first planetary gearset 14 comprises a sun gear 17, a planet carrier 18 and a ring gear 19. Likewise, the second planetary gearset 15 comprises a sun gear 20, a planet carrier 21 and a ring gear 22. In the present embodiment, both the first and the second planetary gearsets 14 and 15 are formed as minus-planetary gearsets. In the embodiment of Figure 3, the first and the second planetary gearsets 14 and 15 are displaced with respect to each other in an axial direction of the differential transmission 10, i.e., in a direction of the output shafts 12 and 13. More precisely, the first and the second planetary gearsets 14 and 15 are stacked in a radial direction of the differential transmission 10 but are provided behind each other in an axial direction of the differential transmission 10.
As derivable from Figure 3, the sun gear 17 of the first planetary gearset 14 is torque-proofly connected to the input shaft 11. Furthermore, the planet carrier 18 of the first planetary gearset 14 is torque-proofly connected to the first output shaft 12. Furthermore, the ring gear 19 of the first planetary gearset 14 is torque-proofly connected to the sun gear 20 of the second planetary gearset 15. For providing this torque-proof connection, in the present embodiment, the differential transmission 10 comprises a coupling element 30, which forms both the ring gear 19 and the sun gear 20. The planet carrier 21 of the second planetary gearset 15 is torque-proofly connected to the housing 16. Furthermore, the ring gear 22 of the second planetary gearset 15 is torque-proofly connected to the second output shaft 13. Both the first planet carrier 18  of the first planetary gearset 14 and the second planet carrier 21 of the second planetary gearset 15 comprise multiple planet gears 23 and 24, respectively. In the present embodiment, the number of planet gears 24 of the second planetary gearset 15 is larger than the number of planet gears 23 of the first planetary gearset 14. The differential transmission 10 of the present embodiment comprises eight planet gears 24 on the second planet carrier 21 of the second planetary gearset 15 and four planet gears 23 on the first planet carrier 18 of the first planetary gearset 14.
Figure 4 shows a cross-sectional view of the differential transmission 10 of Figure 3 according to an embodiment. In Figure 4, only an upper half of the differential transmission 10 is shown. Furthermore, in Figure 4, the sun gear 17 of the first planetary gearset 14, the planet gears 23 of the first planetary gearset 14, the housing 16 and the input shaft 11 are not shown. As derivable from Figure 4, the coupling element 30, which torque-proofly connects the ring gear 19 of the first planetary gearset 14 with the sun gear 20 of the second planetary gearset 15 comprises a ring gear section 31, which forms the ring gear 19, and a sun gear section 32, which forms the sun gear 20. The ring gear section 31 and the sun gear section 32 are torque-proofly connected, while the ring gear section 31 exhibits a larger diameter than the sun gear section 32. Accordingly, the coupling element 30 exhibits a step radially inward from the first planetary gearset 14 to the second planetary gearset 15.
The planet carrier 18 of the first planetary gearset 14, which is shown in detail in Figure 5, exhibits two circular side surfaces 33 and 34, which have equal diameter, and which are provided parallel but spaced apart from each other. The side surfaces 33 and 34 are connected to each other with multiple bridges 35 extending in the axial direction of the differential transmission 10. In the circumferential direction, the bridges 35 are provided in between support structures 36 for supporting axles (not shown) for the planet gears 23 of the first planetary gearset 14. Furthermore, the planet carrier 18 exhibits a fixing portion 37 for fixing the planet carrier 18 to the first output shaft 12. As derivable from the cross-sectional view of Figure 4, the planet carrier 18 is fixed to the first output shaft 12 via the fixing portion 37 and the extends radially outward via the side surface 33 up to the bridge 35 provided at the radial outer end. The step portion of the coupling element 30 is provided radially outside of the bridges 35 of the planet carrier 18 and approximately at the same axial height of the side surface 33 of planet carrier 18. This  implies that, in the axial direction of the differential transmission 10, the sun gear section 32 of the coupling element 30 extends away from the side surface 33 of the planet carrier 18.
As shown in Figure 4, the planet carrier 21 with its planet gears 24 as well as the ring gear 22 of the second planet carrier 15 are provided approximately at the same axial height of the sun gear section 32 of the coupling element 30. However, in the radial direction, the planet carrier 21 with the planet gears 24 of the second planetary gearset 15 is provided radially outward of the sun gear section 32 of the coupling element 30. The ring gear 22 of the second planetary gearset 15 is provided radially outward of the planet gears 24 of the second planetary gearset 15. As described above in connection with Figure 3, the ring gear 22 of the second planetary gearset 15 is torque-proofly connected to the second output shaft 13, which is also shown in Figure 4. As derivable from Figure 4, the first output shaft 12 is supported within the second output shaft 13 via a bearing 38. Accordingly, the first and the second output shafts 12 and 13 overlap with each other in an axial direction of the differential transmission 10. The overlap is configured in such a way that the second output shaft 13 extends all the way up to the side surface 33 of the planet carrier 18 and therefore also axially overlaps the fixing portion 37.
In addition, the differential transmission 10 comprises a connecting element 39, which torque-proofly connects the ring gear 22 of the second planetary gearset 15 with the second output shaft 13. The connecting element 39 comprises a first radial portion 40 extending radially inward from the ring gear 22 of the second planetary gearset 15, an axial portion 41 and a second radial portion 42. The first radial portion 40 is, in axial direction of the differential transmission 10, provided behind the planet gears 24 of the second planetary gearset 15 when viewed from the planet carrier 18 of the first planetary gearset 14. It extends radially downward to a position below the sun gear section 32 of the coupling element 30. The axial portion 41 extends in axial direction towards the side surface 33 of the planet carrier 18. Furthermore, the second radial portion 42 extends further radially inward towards the second output shaft 13 and is connected thereto in a torque-proofly manner. The first radial portion 40, the axial portion 41 and the second radial portion 42 are formed integrally with each other. In  addition, the second radial portion 42 forms a contact surface 43 facing towards the side surface 33 of the planet carrier 18 and being oriented parallel thereto.
As shown in Figure 5, the planet carrier 18 comprises on its side surface 33 several abutment portions 44, which are provided in between the supporting structures 36 for the planet gears 23. In between said abutment portions 44, voids forming oil channels 45 are provided. The abutment portions 44 and the oil channels 45 are provided at the radial height of the second radial portion 42 of the connecting element 39. In between the abutment portions 44 and the contact surface 43 of the second radial portion 42 of the connecting element 40 a gap is provided.
The coupling element 30 comprises a bearing portion 46. In the present embodiment, the bearing portion 46 is a stamping part being pressed and/or riveted to the inner face of the sun gear section 32 of the coupling element 30. The bearing portion 46 is torque-proofly connected with the sun gear section 32 of the coupling element 30. It extends radially inward into the gap between the abutment portions 44 of the planet carrier 18 and the contact surface 43 of the connecting element 40. In the present embodiment, the bearing portion 46, the abutment portion 44 and the contact surface 43 are designed in such a way that the bearing portion 46 engages both the abutment surfaces 44 and the contact surface 43. Accordingly, the axial movement of the coupling element 30 is limited by the bearing portion 46 engaging the abutment portions 44 of the planet carrier 18 and the contact surface 43 of the connecting element 39.
At the same time, the provision of the oil channels 45 allow for a passage of oil from an area around the fixing portion 37 of the planet carrier 18 through the oil channels 45 to planet gears 23 of the planet carrier 18 of the first planetary gearset 14. The oil may pass along the side surface 33 through the oil passages 45 to the planet gears 23. The oil channels 45 are bordered by a guiding element 47 shown in Figure 6. The guiding element 47 exhibits a ring shape having openings 48 for accommodating the abutment portions 44 of the planet carrier 18. The guiding element 47 is mounted to the side surface 33 of the planet carrier 18, in the present embodiment via screws 49, such that the abutment portions 44 extend through the openings 48. The guiding element 47 forms the oil channels 45 in between the abutment portions 44 and is configured to guide oil coming from an area around the fixing portion 37 of the planet carrier 18 into  the supporting structures 36 and therefore to the planet gears 23 of the first planetary gearset 14.
Reference signs
1           driving arrangement
2           motor
3, 4        driving axle
5          wheel
10         differential transmission
11          input shaft
12, 13    output shafts
14, 15    planetary gearset
16     housing
17, 20    sun gear
18, 21    planet carrier
19, 22    ring gear
23, 24    planet gear
30       coupling element
31, 32     gear section
33, 34     side surface
35         bridge
36         supporting structure
37         fixing portion
38         bearing
39         connecting element
40, 42    radial portion
41          axial portion
43         contact surface
44         abutment portion
45         oil channel
46         bearing portion
47         guiding element
48         opening
49         screw
100        vehicle

Claims (10)

  1. A differential transmission (10) for a vehicle (100) comprising a first and a second output shaft (12, 13) , a first planetary gearset (14) with a sun gear (17) , a planet carrier (18) and a ring gear (19) as well as a second planetary gearset (15) with a sun gear (20) , a planet carrier (21) and a ring gear (22) , wherein the first planetary gearset (14) is mechanically coupled to the first output shaft (12) and the second planetary gearset (15) is mechanically coupled to the second output shaft (13) via a connecting element (39) , wherein the ring gear (19) of the first planetary gearset (14) is torque-proofly connected to the sun gear (22) of the second planetary gearset (15) via a coupling element (30) having a bearing portion (46) , and wherein the bearing portion (46) of the coupling element (30) engages the planet carrier (18) of the first planetary gearset (14) and the connecting element (39) to limit a movement of the coupling element (30) in an axial direction of the differential transmission (10) .
  2. The differential transmission (10) of claim 1, wherein the first planetary gearset (14) and the second planetary gearset (15) are displaced with respect to each other in the axial direction of the differential transmission (10) .
  3. The differential transmission (10) according to claim 2, wherein the coupling element (30) comprises a ring gear section (31) comprising the ring gear (19) of the first planetary gearset (14) and a sun gear section (32) comprising the sun gear (20) of the second planetary gearset (15) , wherein the ring gear section (31) has a larger diameter than the sun gear section (32) , and wherein the bearing portion (46) extends radially inward from the sun gear section (32) toward the planet carrier (18) of the first planetary gearset (14) .
  4. The differential transmission (10) according to one of claims 2 and 3, wherein the connecting element (39) has an axial portion (41) extending toward the planet carrier (18) of the first planetary gearset (14) to form a gap in between said planet carrier (18) and said connecting element (39) for accommodating the bearing portion (46) of the coupling element (30) .
  5. The differential transmission (10) according to one of the preceding claims, wherein the bearing portion (46) of the coupling element (30) is formed by a separate part mounted to the coupling element (30) .
  6. The differential transmission (10) according to one of the preceding claims, wherein the planet carrier (18) of the first planetary gearset (14) comprises an abutment portion (44) engaging the bearing portion (46) of the coupling element (30) and a lubricant channel (45) adjacent the abutment portion (44) for allowing a lubricant to flow in a radially direction through the lubricant channel (45) to a planet gear (23) on the planet carrier (18) of the first planetary gearset (14) .
  7. The differential transmission (10) according to claim 6, further comprising a guiding element (47) with an opening (48) for accommodating the abutment portion (44) , the guiding element (47) bordering the lubricant channel (45) and being configured to guide lubricant flowing radially outward to a planet gear (23) of the planet carrier (18) of the first planetary gearset (14) .
  8. The differential transmission (10) according to one of the preceding claims, further comprising a stationary element (16) and an input shaft (11) mechanically couplable to a motor (2) , wherein the sun gear (17) of the first planetary gearset (14) is mechanically coupled to the input shaft (11) , the planet carrier (18) of the first planetary gearset (14) is mechanically coupled to the first output shaft (12) , the planet carrier (21) of the second planetary gearset (15) is mechanically coupled to the stationary element (16) and the ring gear (22) of the second planetary gearset (15) is mechanically coupled to the second output shaft (13) .
  9. A driving arrangement (1) comprising a motor (2) and a differential transmission (10) according to one of the preceding claims, the motor (2) being mechanically coupled to the input shaft (11) of the differential transmission (10) .
  10. A vehicle (100) comprising a driving arrangement (1) according to claim 9.
PCT/CN2024/108735 2024-07-31 2024-07-31 Differential transmission for a vehicle Pending WO2026025334A1 (en)

Priority Applications (1)

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Application Number Priority Date Filing Date Title
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WO2026025334A1 true WO2026025334A1 (en) 2026-02-05

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Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US11255419B2 (en) * 2017-07-25 2022-02-22 Magna powertrain gmbh & co kg Axle drive
US20230213092A1 (en) * 2019-10-25 2023-07-06 Zf Friedrichshafen Ag Transmission, drive train and vehicle having a transmission
DE102022211895A1 (en) * 2022-02-24 2023-08-24 Zf Friedrichshafen Ag Powertrain, electric drive axle and vehicle
US20240200649A1 (en) * 2022-12-19 2024-06-20 Zf Friedrichshafen Ag Transmission for a Vehicle, and Power Train Having Such a Transmission

Patent Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US11255419B2 (en) * 2017-07-25 2022-02-22 Magna powertrain gmbh & co kg Axle drive
US20230213092A1 (en) * 2019-10-25 2023-07-06 Zf Friedrichshafen Ag Transmission, drive train and vehicle having a transmission
DE102022211895A1 (en) * 2022-02-24 2023-08-24 Zf Friedrichshafen Ag Powertrain, electric drive axle and vehicle
US20240200649A1 (en) * 2022-12-19 2024-06-20 Zf Friedrichshafen Ag Transmission for a Vehicle, and Power Train Having Such a Transmission

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