WO2024094546A1 - Différentiel à engrenage cylindrique à denture droite pour véhicule automobile - Google Patents

Différentiel à engrenage cylindrique à denture droite pour véhicule automobile Download PDF

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Publication number
WO2024094546A1
WO2024094546A1 PCT/EP2023/080012 EP2023080012W WO2024094546A1 WO 2024094546 A1 WO2024094546 A1 WO 2024094546A1 EP 2023080012 W EP2023080012 W EP 2023080012W WO 2024094546 A1 WO2024094546 A1 WO 2024094546A1
Authority
WO
WIPO (PCT)
Prior art keywords
gear
planetary gear
differential
planetary
planet
Prior art date
Application number
PCT/EP2023/080012
Other languages
German (de)
English (en)
Inventor
Carsten Gitt
Tobias Haerter
Jochen Stoesser
Andreas Kolb
Original Assignee
Mercedes-Benz Group 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 Mercedes-Benz Group AG filed Critical Mercedes-Benz Group AG
Publication of WO2024094546A1 publication Critical patent/WO2024094546A1/fr

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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
    • F16H48/11—Differential gearings with gears having orbital motion with orbital spur gears having intermeshing planet 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 invention relates to a transmission device for a motor vehicle according to the preamble of patent claim 1. Furthermore, the invention relates to a motor vehicle, in particular a motor vehicle, with such a transmission device.
  • a spur gear differential is known from DE 102014203 522 A1.
  • DE 102015214 035 B4 discloses an electronic drive unit for a motor vehicle.
  • a transmission device for a motor vehicle is known from DE 102018 128 836 B3.
  • the object of the present invention is to provide a transmission device for a motor vehicle and a motor vehicle with such a transmission device, so that a particularly compact and lightweight design and a particularly high torque density of the transmission device can be realized.
  • a first aspect of the invention relates to a transmission device for a motor vehicle, also referred to simply as a vehicle, which is preferably designed as a motor vehicle, in particular as a passenger car.
  • a motor vehicle also referred to simply as a vehicle
  • the motor vehicle in its fully manufactured state has the transmission device and can be driven via the transmission device, in particular by means of a drive motor of the motor vehicle.
  • vehicle wheels also referred to simply as wheels
  • axle can be driven via the transmission device.
  • Vehicle axle of the motor vehicle in order to drive the motor vehicle as a whole.
  • the transmission device has a spur gear differential, which is also referred to as a spur gear differential.
  • the spur gear differential is thus a differential gear, also simply referred to as a differential, which is designed as a spur gear differential.
  • the vehicle wheels mentioned can be driven via the spur gear differential, in particular by a drive shaft of the motor vehicle.
  • the spur gear differential for example, has the function, which is well known from the prior art, of dividing and transmitting a drive torque provided or available by the drive shaft to the vehicle wheels, in particular to side shafts via which the vehicle wheels can be driven.
  • the spur gear differential for example, has the function of allowing different speeds of the vehicle wheels and thus the side shafts when the motor vehicle is cornering, such that the vehicle wheel on the outside of the curve can or does rotate at a higher speed than the vehicle wheel on the inside of the curve, in particular while the vehicle wheels can or are driven by the drive shaft via the spur gear differential.
  • the side shafts mentioned can, for example, be part of the spur gear differential.
  • a first of the vehicle wheels can be driven by a first of the side shafts
  • a second of the vehicle wheels can be driven by a second of the side shafts.
  • the side shafts can be arranged coaxially to one another.
  • the vehicle wheels are arranged on opposite sides of the vehicle in the transverse direction of the motor vehicle, also referred to simply as the vehicle.
  • the spur gear differential has a first sun gear, which is designed as a first output of the spur gear differential and as a first spur gear.
  • the first sun gear has a first pitch circle diameter.
  • the first sun gear has a first pitch circle diameter.
  • the first sun gear is connected, in particular permanently, in a rotationally fixed manner to the first side shaft, so that, for example, the first side shaft can be driven by the first sun gear and so that, for example, the first vehicle wheel can be driven by the first sun gear via the first side shaft.
  • the spur gear differential also has a second sun gear, which is designed as a second output of the spur gear differential and as a second spur gear.
  • the second sun gear is connected, in particular permanently, in a rotationally fixed manner to the second side shaft, so that the second side shaft can be driven by the second Sun gear is drivable.
  • the second vehicle wheel can thus be driven by the second sun gear via the second side shaft.
  • the sun gears are arranged coaxially to one another.
  • the second sun gear is arranged coaxially to a rotational axis of the first sun gear.
  • the first sun gear is, for example, rotatable about a first sun gear axis of rotation, in particular relative to a housing of the transmission device.
  • the first sun gear is at least partially arranged in the housing.
  • the second sun gear is, for example, rotatable about a second sun gear axis of rotation relative to the housing in which, for example, the second sun gear is at least partially arranged, wherein, because the sun gears are arranged coaxially to one another, the sun gear axes of rotation coincide.
  • the first side shaft is arranged coaxially to the first sun gear
  • the second side shaft is arranged coaxially to the second sun gear.
  • the feature that two components are connected to one another in a rotationally fixed manner can be understood to mean that the two components are formed in one piece, thus formed from a single piece and are thereby connected to one another in a rotationally fixed manner, so that the two components formed in one piece are formed as a monoblock, i.e. are formed by a monoblock.
  • the components formed in one piece are formed by a one-piece and thus integrally manufactured, integral body.
  • the two components connected to one another in a rotationally fixed manner are formed separately from one another and are connected to one another in a rotationally fixed manner, in particular by a joining technique.
  • the components connected to one another in a rotationally fixed manner are or will be rotatable or rotated about a component rotation axis common to the components, in particular relative to the housing, in particular when the components are driven, so that the components can rotate or rotate together or simultaneously at the same angular velocity about the component rotation axis, in particular relative to the housing.
  • relative rotations between the components about the component rotation axis are prevented.
  • the second sun gear designed as a second spur gear, has a second pitch circle diameter which is different from the first pitch circle diameter.
  • the first pitch circle diameter is larger than the second pitch circle diameter or vice versa.
  • the second Sun gear has a second pitch circle diameter which is different from the first pitch circle diameter, so that, for example, the first pitch circle diameter is larger than the second pitch circle diameter or vice versa.
  • the transmission device also has a planetary gear set, which is also referred to as a planetary arrangement or orbiting planetary arrangement.
  • a planetary gear set which is also referred to as a planetary arrangement or orbiting planetary arrangement.
  • the sun gears are coupled to one another in such a way that the sun gears can rotate in opposite directions.
  • the vehicle wheels mentioned are ground contact elements of the motor vehicle, also referred to as the vehicle, which can be or is supported on a ground such as a roadway via the ground contact elements in the vertical direction of the motor vehicle.
  • the vehicle wheels and thus the motor vehicle are driven so that the motor vehicle is driven along the ground while the motor vehicle is supported on the ground via the ground contact elements (vehicle wheels) in the vertical direction of the vehicle, the vehicle wheels roll, in particular directly, on the ground.
  • the motor vehicle is now at least partially raised in such a way that the vehicle wheels do not touch the ground and are, so to speak, floating in the air, and then, for example, the first vehicle wheel and thus the first side shaft and the first sun gear are rotated about the first sun gear axis of rotation in a first direction of rotation, the second sun gear and the second side shaft are thereby driven via the planetary gear set, as is well known from conventional differential gears, and the second vehicle wheel is driven via the second side shaft in such a way that the second sun gear and thus, for example, the second side shaft are rotated about the second sun gear axis of rotation and thus about the first sun gear axis of rotation in a second direction of rotation opposite to the first direction of rotation, thus in the opposite direction to the first
  • the planetary gear set has a planet carrier, which is preferably arranged coaxially to the sun gears.
  • the planet carrier is rotatable, for example, about a planet carrier rotation axis relative to the housing, wherein the planet carrier can be arranged at least partially in the housing.
  • the planet carrier rotation axis coincides with the sun gear rotation axes, so that the planet carrier is preferably arranged coaxially to the sun gears.
  • the planetary gear set also has at least one first differential planet gear, which engages in the first sun gear, thus meshes with the first sun gear or is in engagement with the first sun gear.
  • the first differential planet gear has a third pitch circle diameter.
  • the first differential planetary gear has a third pitch circle diameter.
  • the planetary gear set has at least one further or several further first differential planetary gears, wherein the previous and following statements regarding the at least one first differential planetary gear can also be readily applied to the respective further first differential planetary gear and vice versa.
  • first differential planetary gear is mentioned above and below, this is to be understood as meaning the at least one first differential planetary gear, unless otherwise stated.
  • the first differential planetary gear is held on the planet carrier so as to be rotatable about a first planetary axis of rotation relative to the planet carrier.
  • the first planetary axis of rotation preferably runs parallel to the respective sun gear axis of rotation and/or parallel to the planet carrier axis of rotation, wherein the first planetary axis of rotation is preferably spaced apart from the respective sun gear axis of rotation and/or from the planet carrier axis of rotation.
  • the planetary gear set also has at least one second differential planet gear. It is conceivable that the planetary gear set has at least one further second or several further second differential planet gears, wherein the previous and following statements on the at least one second differential planet gear can also be easily applied to the respective further second differential planet gear and vice versa.
  • the second differential planet gear is mentioned above and below, this is to be understood as the at least one second differential planet gear, unless otherwise stated.
  • the second differential planet gear engages with the second sun gear. It is therefore provided that the second differential planet gear meshes with the second sun gear or is in engagement with the second sun gear.
  • the second differential planet gear is held on the planet carrier so as to be rotatable about a second planetary axis of rotation running parallel to the first planetary axis of rotation and spaced apart from the first planetary axis of rotation.
  • the second planetary axis of rotation runs parallel to the respective sun gear axis of rotation and/or parallel to the planet carrier axis of rotation, wherein it is preferably provided that the second planetary axis of rotation is spaced from the respective sun gear axis of rotation and/or from the planet carrier axis of rotation.
  • the planetary gear set also has at least one gear arranged coaxially to the first differential planet gear, connected in a rotationally fixed manner to the first differential planet gear and engaging in the second differential planet gear, thus engaging with the second differential planetary gear or meshing with the second differential planetary gear and thereby coupling the differential planetary gears to one another, which has a fourth pitch circle diameter that is different from the third pitch circle diameter.
  • the coupling planetary gear has a fourth pitch circle diameter that is different from the third pitch circle diameter.
  • the first differential planetary gear and the second differential planetary gear form, for example, a differential planetary gear group, it being conceivable that the spur gear differential has at least one further or several further differential planetary gear groups, the previous and following statements on the first differential planetary gear group being readily transferable to the respective further differential planetary gear group and vice versa.
  • the coupling planetary gear and the first differential planetary gear form a differential stage planetary gear which is held on the planetary carrier so as to be rotatable about the first planetary axis of rotation relative to the planetary carrier.
  • the differential planetary gears and the coupling planetary gear are further spur gears of the spur gear differential.
  • the first differential stage planetary gear has the first differential planetary gear as the first stage planet and the coupling planetary gear as the second stage planet.
  • the first differential planetary gear is also referred to as the first stage planet and the coupling planetary gear is also referred to as the second stage planet.
  • the spur gear differential has at least one further or several further differential stage planetary gears, wherein the previous and following statements regarding the first differential stage planetary gear can also be easily transferred to the respective further differential stage planetary gear and vice versa.
  • the differential stage planetary gear and the second differential planetary gear are arranged on different axes. This means in particular that the first planetary axis of rotation and the second planetary axis of rotation run parallel to one another and are spaced apart from one another, in particular in the radial direction of the planetary gear set and/or in the circumferential direction of the planetary gear set running around the axial direction of the planetary gear set.
  • a first ratio between the first pitch circle diameter and the second Pitch circle diameter and a second ratio between the third pitch circle diameter and the fourth pitch circle diameter are equal.
  • the first ratio is a first quotient which has the first pitch circle diameter in its first numerator and the second pitch circle diameter in its first denominator.
  • the second ratio is a second quotient which has the third pitch circle diameter in its second numerator and the fourth pitch circle diameter in its second denominator.
  • the quotients are equal.
  • the first sun gear and the second sun gear are collectively referred to as outputs or output sun gears, with the first sun gear being a first of the output sun gears and the second sun gear being a second of the output sun gears.
  • the invention makes it possible to divide the aforementioned drive torque equally, i.e. half, between the output sun gears and thus to transmit it, thus realizing a so-called 50:50 torque distribution.
  • the output sun gears are designed to be slightly different in terms of their pitch circle diameters, i.e. different sizes.
  • this can avoid unfavorable, extreme profile shifts and the resulting adverse effects on the load-bearing behavior of the gear teeth of the spur gear differential.
  • the transmission device can be designed to be particularly weight- and space-efficient, and a high torque density can be achieved.
  • the first differential planetary gear has a first toothing with a first number of teeth and a first toothing module, wherein the first toothing engages in the first sun gear.
  • the first toothing has first teeth with a respective first tooth height, wherein preferably the first tooth heights are the same.
  • the coupling planetary gear has a second toothing with a second number of teeth and a second toothing module, wherein the second toothing engages in the second differential planetary gear.
  • the second Toothing has second teeth with a respective second tooth height, wherein preferably the second tooth heights are equal.
  • the first differential planetary gear engages with the first sun gear, but preferably the first differential planetary gear does not engage with the coupling planetary gear, the second sun gear, or the second differential planetary gear.
  • the coupling planetary gear engages with the second differential planetary gear, but preferably the coupling planetary gear does not engage with the first differential planetary gear or the first sun gear, and preferably the coupling planetary gear does not engage with the second sun gear.
  • the second differential planetary gear engages with the second sun gear and the coupling planetary gear, wherein preferably the second differential planetary gear does not engage with the first sun gear or the first differential planetary gear.
  • a further embodiment of the invention is characterized in that the first number of teeth and the second number of teeth are the same, the first tooth module and the second tooth module differ from one another, and the respective first tooth height and the respective second tooth height differ from one another. This allows the installation space requirement to be kept particularly low.
  • first toothing and the second toothing are oriented rotationally to one another, in particular when viewed around the first planetary axis of rotation, such that a respective gap, also referred to as a tooth gap, of the first toothing is aligned with a respective gap, also referred to as a tooth gap, of the second toothing of the coupling planet.
  • a respective gap also referred to as a tooth gap
  • the or all tooth gaps of the first toothing are aligned with the or all tooth gaps of the second toothing, in particular in the axial direction of the differential stage planetary gear and thus viewed along the first planetary axis of rotation.
  • first step planet and the second step planet are formed integrally with one another, thus being formed from a single piece.
  • first step planet and the second step planet are not formed separately from one another and connected to one another.
  • Components are not formed, but preferably the first step planet and the second step planet are formed integrally with each other, so that the first step planet and the second step planet are formed as a monoblock or are formed by a monoblock.
  • first step planet and the second step planet are formed by a one-piece and thus integrally manufactured body, which is formed from a single piece.
  • a further embodiment of the invention is characterized in that, viewed in the axial direction of the first stepped planet and the second stepped planet and thus along the first planetary axis of rotation, a transition region is provided, formed or arranged between the first stepped planet, which has a first width running in the axial direction of the first stepped planet, and the second stepped planet, which has a second width running in the axial direction of the second stepped planet and thus along the first planetary axis of rotation, also referred to as the coupling width, wherein the transition region has a third width, also referred to as the transition width.
  • the first width and the second width are the same.
  • the first width and the second width differ from one another.
  • first width and the third width can be the same, or the third width and the first width can differ from one another.
  • second width and the third width are the same, or the third width and the second width differ from one another.
  • transition region is free of a toothing, or that a toothing, also referred to as transition toothing, is provided in the transition region, which can, for example, be formed integrally with the first toothing and/or integrally with the second toothing.
  • a tool outlet of a gear cutting tool for producing the first toothing of the first differential planetary gear and/or for producing the second toothing of the coupling planetary gear in the transition region there is a tool outlet of a gear cutting tool for producing the first toothing of the first differential planetary gear and/or for producing the second toothing of the coupling planetary gear.
  • a radial outer contour of the differential stage planetary gear in particular a radial outer contour and thus an outer contour of the differential stage planetary gear pointing outwards in the radial direction of the differential stage planetary gear, does not fall below a first tip circle diameter of the second toothing of the coupling planetary gear in the transition region, but rather deviates from the first tip circle diameter of the second Toothing of the coupling planetary gear increases or grows, in particular continuously, to a second tip diameter of the first toothing of the first differential planetary gear.
  • the second tip diameter is larger than the first tip diameter.
  • the respective previously mentioned width runs in the axial direction of the first stepped planet and the second stepped planet, thus in the axial direction of the differential stage planetary gear and thus along the first planetary axis of rotation. This ensures a particularly compact design, particularly in the axial direction of the differential stage planetary gear and thus of the transmission device as a whole.
  • the third width of the transition region is, in particular significantly, smaller than the first width of the first stepped planet, in particular of the first toothing, and, in particular significantly, smaller than the second width of the second stepped planet, in particular of the second toothing.
  • the first width is a first toothing width of the first toothing
  • the second width is a second toothing width of the second toothing.
  • the third width is significantly smaller than the first width and significantly smaller than the second width.
  • the third width is at most 90 percent, in particular at most 80 percent, most particularly at most 70 percent and most particularly at most 60 percent, of the first width and the second width if the first width and second width are the same, and that the third width is, for example, at most 90 percent, in particular at most 80 percent, most particularly at most 70 percent and most particularly at most 60 percent, of the smaller of the first width and the second width if the first width and the second width are different.
  • the third width is less than 50 percent, in particular less than 40 percent, most particularly less than 30 percent, of the first width and the second width or the smaller of the first width and the second width.
  • a further embodiment of the invention is characterized in that the first differential planetary gear and the coupling planetary gear are formed separately from one another and are connected to one another, in particular in a rotationally fixed manner, wherein the one of the first and second stepped planets whose pitch circle diameter or pitch circle diameter is smaller than the pitch circle diameter or pitch circle diameter of the other of the first and second stepped planets has a for example, has a projection designed as a pin, also referred to as an extension, on which the other of the first and second stepped planets is arranged and fastened.
  • the third pitch circle diameter is larger than the fourth pitch circle diameter
  • the first stepped planet is a large planet and the second stepped planet is a small planet.
  • the first stepped planet is a small planet and the second stepped planet is a large planet.
  • the small planet has the projection designed as a pin, for example, also referred to as an extension, on which the large planet is arranged and fastened.
  • the large planet has a hub in which, for example, at least one length region of the projection of the small planet is arranged, so that the large planet is arranged via its hub on the length region of the projection of the small planet.
  • the large planet is fastened to the projection via the hub in a rotationally fixed manner and is therefore connected to the small planet in a rotationally fixed manner. This makes it possible to achieve a particularly space-saving and cost-effective design.
  • first stepped planet and the second stepped planet are immediately or directly adjacent to one another in the axial direction of the first stepped planet and the second stepped planet and thus viewed along the first planetary axis of rotation.
  • the first sun gear has a third toothing with a third number of teeth and a third toothing module, the third toothing engaging in the first differential planet gear, in particular in its first toothing.
  • the third toothing has third teeth with a respective third tooth height, it is preferably provided that the third tooth heights are the same.
  • the second sun gear has a fourth toothing with a fourth number of teeth and a fourth toothing module, the fourth toothing engaging in the second differential planet gear, in particular in its fifth toothing.
  • the fourth toothing has fourth teeth with a respective fourth tooth height, it is preferably provided that the fourth tooth heights are the same.
  • the third number of teeth and the fourth number of teeth differ from one another, if the third gear module and the fourth gear module are equal, and if the respective third tooth height and the respective fourth tooth height are equal.
  • ordinal numerals such as “first”, “first”, “second”, “secondary” etc. are not necessarily used to indicate or imply a number or set of elements to which the ordinal numerals refer, but rather to be able to unambiguously refer to elements or concepts to which the ordinal numerals are assigned or to which the ordinal numerals refer.
  • the transmission device has a planetary gear, which is provided in particular in addition to the spur gear differential, which has at least one stepped planetary gear provided in addition to the differential step planetary gear and in particular also in addition to the second differential planetary gear and preferably also in addition to the sun gears and is held on the planet carrier so as to be rotatable, in particular about the second planetary axis of rotation relative to the planet carrier, which has a first planetary gear and a second planetary gear.
  • the second planetary gear is also referred to as the third step planet
  • the second planetary gear is also referred to as the fourth step planet.
  • the third step planet and the fourth step planet are preferably spur gears.
  • the third step planet and the fourth step planet are connected to one another in a rotationally fixed manner. It is conceivable that the third step planet and the fourth step planet are formed integrally with one another, thus made from a single piece, or the third step planet and the fourth step planet are formed separately from one another and connected to one another in a rotationally fixed manner.
  • the planetary gear also has a third planetary gear provided in addition to the first sun gear and in addition to the second sun gear and preferably also in addition to the differential stage planetary gear and in addition to the second differential stage planetary gear and preferably also in addition to the stepped planetary gear.
  • Sun gear which is a drive sun gear or is also referred to as a drive sun gear.
  • the third sun gear is preferably a spur gear.
  • One of the planet gears of the stepped planet gear of the planetary gear is in engagement, and thus meshes with the drive sun gear.
  • first planet gear and the second planet gear are of different sizes, in particular have different pitch circle diameters and/or different pitch circle diameters, so that, for example, the first planet gear has a fifth pitch circle diameter and/or a fifth pitch circle diameter, and so that, for example, the second planet gear has a sixth pitch circle diameter and/or a sixth pitch circle diameter.
  • the fifth pitch circle diameter and the sixth pitch circle diameter differ from one another.
  • the fifth pitch circle diameter and the sixth pitch circle diameter differ from one another.
  • the fifth pitch circle diameter or the fifth pitch circle diameter is larger than the sixth pitch circle diameter or the sixth pitch circle diameter.
  • one planetary gear has the fifth pitch circle diameter or the fifth pitch circle diameter, so that, for example, the other planetary gear of the stepped planetary gear of the planetary gear has the sixth pitch circle diameter or sixth pitch circle diameter.
  • one planetary gear is larger than the other planetary gear.
  • one planetary gear is the larger of the planetary gears, so that the other planetary gear is the smaller of the planetary gears.
  • the first planetary gear is one planetary gear, most preferably, the other planetary gear is the second planetary gear.
  • the larger planetary gear of the stepped planetary gear of the planetary gear is in engagement with the drive sun gear.
  • the planetary gear also has a ring gear which is or can be connected to the aforementioned housing in a rotationally fixed manner.
  • the ring gear can be permanently connected to the housing in a rotationally fixed manner.
  • the ring gear is at least partially arranged in the housing.
  • the other planet gear, in particular the smaller planet gear is in engagement with the ring gear, thus engaging with the ring gear or meshing with the ring gear.
  • the stepped planet gear of the planetary gear is, in particular permanently, connected to the second differential planet gear in a rotationally fixed manner, or that the stepped planet gear of the planetary gear is, in particular the second planetary axis of rotation, relative to the second Differential planetary gear.
  • the stepped planetary gear of the planetary gear is arranged coaxially to the second differential planetary gear.
  • the stepped planetary gear is thus held on the planetary carrier so as to be rotatable about the second planetary axis of rotation relative to the planetary carrier.
  • the second differential planetary gear is connected to the ring gear, to one planetary gear and to the other planetary gear of the planetary gear that engages the ring gear in a direction that runs in the axial direction of the second differential planetary gear and thus runs parallel to the second planetary axis of rotation or coincides with the second planetary axis of rotation, with the ring gear and the other planetary gear of the planetary gear connecting in the same direction to the one planetary gear of the planetary gear that engages the drive sun gear, whereby the ring gear and the other planetary gear of the planetary gear are arranged in the axial direction of the second differential planetary gear and thus viewed along the second planetary axis of rotation, between the second differential planetary gear of the spur gear differential and the one planetary gear of the planetary gear that engages the drive sun gear.
  • a further embodiment of the invention is characterized in that the first pitch circle diameter of the first sun gear is larger than the second pitch circle diameter of the second sun gear, which adjoins the first sun gear in an arrangement direction running in the axial direction of the sun gears, wherein the first sun gear adjoins the third sun gear in the same arrangement direction.
  • the first sun gear is arranged between the second sun gear and the third sun gear in the axial direction of the sun gears and thus along the respective sun gear rotation axis, whereby the transmission device can have a particularly compact design, particularly in the axial direction.
  • planet carrier walls of the planet carrier to whose planet carrier walls bolts are fastened, in particular in a rotationally fixed manner, to which the differential stage planet gear of the spur gear differential, the second differential planet gear of the spur gear differential and preferably the Step planetary gear of the planetary gear are held rotatably, in the axial direction of the planetary gear and the spur gear differential and thus viewed along the respective sun gear axis of rotation are located exclusively on the outside, thus adjoining on both sides to the ring gear, the second differential planet gear of the spur gear differential, the differential step planet gear of the spur gear differential and the sun gears of the spur gear differential and preferably to the step planet gear of the planetary gear, so that the planet carrier walls which are opposite one another in particular in the axial direction of the planet carrier are arranged outside the planetary gear and outside the spur gear differential in the axial direction of the gear device and thus viewed along the respective sun gear axis of rotation.
  • first differential planetary gear is arranged in phase with the stepped planetary gear.
  • the smaller planetary gear of the planetary gear is arranged between the larger planetary gear of the planetary gear and the second differential planetary gear of the spur gear differential, or preferably, viewed in the axial direction of the second differential planetary gear of the spur gear differential and thus along the second planetary axis of rotation, the larger planetary gear of the planetary gear is arranged between the smaller planetary gear of the planetary gear and the second differential planetary gear of the spur gear differential.
  • a second aspect of the invention relates to a motor vehicle, also referred to simply as a vehicle, which is preferably designed as a motor vehicle, in particular as a passenger car.
  • the motor vehicle according to the second aspect of the invention has a transmission device according to the first aspect of the invention.
  • Advantages and advantageous embodiments of the first aspect of the invention are to be regarded as advantages and advantageous embodiments of the second aspect of the invention and vice versa.
  • Fig. 1 is a schematic front view of a first embodiment of a transmission device for a motor vehicle
  • Fig. 2 is a schematic side view of the first embodiment of the transmission device
  • Fig. 3 is a schematic side view of a second embodiment of the transmission device
  • Fig. 4 is a schematic front view of a first embodiment of a differential stage planetary gear of a spur differential of the transmission device
  • Fig. 5 shows a second embodiment of the differential stage planetary gear
  • Fig. 6 is a schematic front view of a third embodiment of the
  • Fig. 7 is a schematic side view of the third embodiment of the transmission device.
  • Fig. 8 is a schematic front view of a fourth embodiment of the transmission device.
  • Fig. 9 is a schematic side view of the fourth embodiment of the transmission device;
  • Fig. 10 shows a partial schematic longitudinal sectional view of a third embodiment of the differential stage planetary gear;
  • Fig. 11 shows a partial schematic longitudinal sectional view of a fourth embodiment of the differential stage planetary gear
  • Fig. 12 shows a partial schematic longitudinal sectional view of a fifth embodiment of the differential stage planetary gear.
  • FIG. 1 and 2 show, in a schematic front view and in a schematic and sectional side view, a first embodiment of a transmission device 10 for a motor vehicle, preferably designed as a motor vehicle, in particular as a passenger car, and also simply referred to as a vehicle.
  • the motor vehicle has, for example, at least or exactly two vehicle axles arranged one behind the other in the longitudinal direction of the vehicle, also simply referred to as axles.
  • the respective vehicle axle has at least or exactly two vehicle wheels, which are also simply referred to as wheels.
  • the respective vehicle wheels of the respective vehicle axle are arranged on opposite sides in the transverse direction of the motor vehicle.
  • the vehicle wheels are ground contact elements by means of which the motor vehicle can be or is supported downwards on a ground in the vertical direction of the motor vehicle.
  • the motor vehicle has at least one drive motor by means of which the vehicle wheels of at least or exactly one of the vehicle axles can be driven via the transmission device 10, whereby the motor vehicle as a whole can be driven.
  • the drive motor can be an internal combustion engine or an electric machine, so that the motor vehicle is designed, for example, as a hybrid vehicle or as an electric vehicle, in particular as a battery-electric vehicle (BEV).
  • BEV battery-electric vehicle
  • the vehicle wheels that can be driven via the transmission device 10 are also referred to as drive wheels. When the wheels or the vehicle wheels are mentioned below, this means the drive wheels of the motor vehicle, unless otherwise stated.
  • the transmission device 10 has a spur differential 12, which is also referred to as a spur differential gear.
  • the spur differential 12 is a differential gear, also simply referred to as a differential, which is designed as a spur differential gear.
  • the spur differential 12 is designed as a planetary differential.
  • the spur differential 12 has a first sun gear 14, which is also referred to as a first sun.
  • the first sun gear 14 is designed as a first output of the spur differential 12.
  • the first sun gear 14 is designed as a first spur gear.
  • the sun gear 14 is a first gear which is designed as a spur gear.
  • the first sun gear 14 has a first pitch circle diameter.
  • the spur differential 12 also has a second sun gear 16, which is designed as a second output of the spur differential 12.
  • the second sun gear 16 is designed as a second spur gear.
  • the second sun gear 16 is a second gear which is designed as a spur gear. It can be seen particularly well from Fig. 1 and 2 that the sun gears 14 and 16 are arranged coaxially to one another.
  • the transmission device 10 has a housing 18, which is shown particularly schematically in Fig. 1, with the spur gear differential 12 being at least partially arranged in the housing 18.
  • the sun gears 14 and 16 are rotatable relative to the housing 18 about a sun gear axis of rotation common to the sun gears 14 and 16.
  • the sun gear axis of rotation 20 is also simply referred to as the axis of rotation, with the axis of rotation running in the axial direction of the transmission device 10 and thus of the spur gear differential 12, in particular coinciding with the axial direction of the transmission device 10 and thus of the spur gear differential 12.
  • the axial direction of the transmission device 10 coincides with the axial direction of the spur gear differential 12, the radial direction of which coincides with the radial direction of the transmission device 10.
  • the second sun gear 16 is designed as a second output of the spur gear differential 12.
  • the spur gear differential 12 can provide output torques via its outputs, i.e. via the sun gears 4 and 16, by means of which the drive wheels can be driven.
  • the respective output torque provided or available by the respective sun gear 14, 16 results from a drive torque which can be introduced or is introduced into the spur gear differential 12.
  • the drive torque can be provided by the drive motor or the
  • Drive torque results from a further torque which can be provided by the drive motor.
  • the drive torque can be divided and distributed between the vehicle wheels, in particular in half, by means of the spur gear differential 12.
  • a first shaft designed as a first side shaft 22 extends from the first sun gear 14 and a second shaft designed as a second side shaft 22 extends from the sun gear 16.
  • Side shaft 24 is drivable, wherein a first of the drive wheels is drivable by the side shaft 22 and a second of the drive wheels is drivable by the side shaft 24.
  • the first sun gear 14 is provided, in particular permanently, in rotation with the first side shaft 22, and alternatively or additionally the second sun gear 16 is, in particular permanently, in rotation with the second side shaft 24.
  • the second sun gear 16 has a second pitch circle diameter that is different from the first pitch circle diameter, wherein in this case the second pitch circle diameter is smaller than the first pitch circle diameter.
  • the second sun gear 16 is also referred to as the second sun, small sun or smaller sun, wherein the sun gear 14 is also referred to as the first sun, larger sun or large sun.
  • the spur gear differential 12 further comprises a planetary gear set 26, by means of which the sun gears 14 and 16 are coupled to one another in such a way that the sun gears 14 and 26 can rotate in opposite directions, in particular about the axis of rotation relative to the housing 18.
  • the planetary gear set 26 comprises a planet carrier 28, which is also referred to as a web and is arranged coaxially to the sun gears 14 and 16 in this case.
  • the planet carrier 28 can be rotated about the axis of rotation (sun gear axis of rotation 20) relative to the housing 18.
  • the planetary gear set 26 further comprises a first differential planet gear 30.
  • the planetary gear set 26 comprises at least one further or several further first differential planet gears, wherein the following and previous statements regarding the first differential planet gear 30 can also be readily applied to the respective further first differential planet gear and vice versa.
  • the first differential planetary gear 30 engages with the first sun gear 14, and thus meshes with the first sun gear 14 or is in engagement with the first sun gear 14.
  • the first differential planetary gear 30 is held on the planet carrier 28 so as to be rotatable about a first planetary axis of rotation 32 relative to the planet carrier 28.
  • the first differential planetary gear 30 has a third pitch circle diameter.
  • the first differential planetary gear 30 is assigned a first bolt 34, which is also referred to as the first planetary bolt.
  • the first differential planetary gear 30 is arranged, in particular mounted, on the bolt 34 so as to be rotatable about the first planetary axis of rotation 32 relative to the bolt 34 and relative to the planet carrier 28, wherein, for example, the bolt 34 is in turn fastened, in particular in a rotationally fixed manner, to the planet carrier 28.
  • the planetary gear set 26 also has at least one second differential planetary gear 36.
  • the planetary gear set 26 it is conceivable for the planetary gear set 26 to have at least one further or several further second differential planetary gears, wherein the previous and following statements regarding the second differential planetary gear 36 can also be easily applied to the further second differential planetary gear and vice versa.
  • the second differential planetary gear 36 engages with the second sun gear 16, which is shown in Fig.
  • the second differential planetary gear 36 meshes with the sun gear 16 or the second differential planetary gear 36 is in engagement with the second sun gear 16.
  • the dashed arrow 38 therefore means “meshes with”.
  • the second differential planetary gear 36 is held on the planet carrier 28 so as to be rotatable about a second planetary axis of rotation 40 relative to the planet carrier 28. From Fig. 2 it can be seen that the second planetary axis of rotation 40 runs parallel to the first planetary axis of rotation 32 and is spaced from the planetary axis of rotation 32.
  • the planetary axes of rotation 32 and 40 run parallel to the axis of rotation (sun gear axis of rotation 20), and the planetary axes of rotation 32 and 40 are each spaced from the axis of rotation.
  • the second differential planetary gear 36 is assigned a second bolt 42, which is also referred to as a second planetary bolt.
  • the second differential planetary gear 36 is arranged, in particular mounted, on the second bolt 42 so as to be rotatable about the second planetary axis of rotation 40 relative to the bolt 42 and relative to the planet carrier 28, wherein, for example, the second bolt 42 is in turn fastened, in particular in a rotationally fixed manner, to the planet carrier 28.
  • the planetary gear set 26 also has at least one coupling planetary gear 44.
  • the planetary gear set 26, in particular for each first differential planetary gear has a respective coupling planetary gear such as the coupling planetary gear 44.
  • the first differential planetary gear 30, the second differential planetary gear 36 and the coupling planetary gear 44 are designed as spur gears, thus as gears which are designed as spur gears.
  • the coupling planetary gear 44 is arranged coaxially to the first differential planetary gear 30 and, in particular permanently, is connected in a rotationally fixed manner to the first differential planetary gear 30.
  • the coupling planetary gear 44 engages the second differential planetary gear 36, whereby the differential planetary gears 30 and 36 are coupled to one another via the coupling planetary gear 44, in particular in a torque-transmitting manner.
  • the coupling planetary gear 44 has a fourth pitch circle diameter that is different from the third pitch circle diameter of the first differential planetary gear 30.
  • the first differential planetary gear 30 and the coupling planetary gear 44 associated with it form a differential stage planetary gear 46, which also referred to as a differential stage planet.
  • the planetary gear set 26 thus has the differential stage planetary gear 46.
  • the planetary gear set 26 has at least one further or several further differential stage planetary gears, wherein the previous and following statements on the differential stage planetary gear 46 can also be easily transferred to the respective further differential stage planetary gear and vice versa.
  • the differential stage planetary gear 46 is held on the planet carrier 28 so as to be rotatable about the first planetary axis of rotation 32 relative to the planet carrier 28.
  • the differential stage planetary gear 46 is arranged, in particular mounted, on the bolt 34 so as to be rotatable about the first planetary axis of rotation 32 relative to the bolt 34 and relative to the planet carrier 28, so that the coupling planetary gear 44 is also arranged, in particular mounted, on the bolt 34 so as to be rotatable about the first planetary axis of rotation 32 relative to the bolt 34 and relative to the planet carrier 28.
  • the first differential planetary gear 30 is a first stage planet of the differential stage planetary gear 46 or is also referred to as the first stage planet of the differential stage planetary gear 46.
  • the coupling planetary gear 44 is a second stage planet of the differential stage planetary gear 46, or the coupling planetary gear 44 is also referred to as the second stage planet of the differential stage planetary gear 46.
  • the fourth pitch circle diameter of the coupling planetary gear 44 is smaller than the third pitch circle diameter of the first differential stage planetary gear 46, so that the coupling planetary gear 44 is also referred to as a small stage planet or smaller stage planet or small planet, and so that the first differential planetary gear 30 is also referred to as a large stage planet or larger stage planet or large planet.
  • the first differential planetary gear 30 has a first toothing having a first number of teeth and a first toothing module, which engages in the first sun gear 14 and has first teeth with a respective first tooth height.
  • the coupling planetary gear 44 has, for example, a second toothing having a second number of teeth and a second toothing module, which engages in the second differential planetary gear 36 and has second teeth with a respective second tooth height. It is also preferably provided that the first number of teeth and the second number of teeth are the same, and that the first gear module and the second gear module differ from one another, so that the respective first relationship and the respective second relationship differ from one another.
  • Fig. 4 shows a schematic front view of a first embodiment of the differential stage planetary gear 46.
  • the first toothing of the first differential planetary gear 30 is designated 48, the first teeth of which are designated 50.
  • the second toothing of the coupling planetary gear 44 is designated 52 in Fig. 4, the second teeth of which are designated 54.
  • the first toothing 48 also has first gaps 56, which are also referred to as first tooth gaps.
  • first tooth gaps 56 In the circumferential direction of the toothing 48 and thus of the differential planetary gear 30 running around the planetary axis of rotation 32, a respective one of the gaps 56 is arranged between each two directly adjacent teeth 50.
  • the toothing 52 has second gaps 58, which are also referred to as second tooth gaps.
  • one of the second gaps 58 is arranged between two immediately adjacent teeth 54.
  • the respective gap 56 is also referred to as the first tooth gap
  • the respective gap 58 is also referred to as the second tooth gap.
  • the toothings 48 and 52 are rotationally oriented from one another when viewed around the planetary axis of rotation 32 in such a way that the respective first gaps 56 are aligned with the respective second gaps 58 in the axial direction of the differential stage planetary gear 46 and thus along the first planetary axis of rotation 32.
  • the first differential planetary gear 30 and the coupling planetary gear 44 are designed separately from one another and are connected to one another.
  • the first differential planetary gear 30 and the coupling planetary gear 44 are directly adjacent to one another, in particular abutting one another, in the axial direction of the differential stage planetary gear 46 and thus viewed along the first planetary axis of rotation 32, i.e. immediately adjacent to one another, so that, for example, the first differential planetary gear 30 and the coupling planetary gear 44 are in direct contact with one another in the axial direction of the differential stage planetary gear 46.
  • Fig. 3 shows a second embodiment of the transmission device 10 in a schematic and sectional side view.
  • the first differential planetary gear 30 and the associated coupling planetary gear 44 are also designed separately from one another and are, in particular permanently, connected to one another in a rotationally fixed manner.
  • an intermediate region 60 is arranged between the first differential planetary gear 30 and the associated coupling planetary gear 44, which intermediate region 60 can also be referred to as a transition region or can be designed as a transition region.
  • the first differential planetary gear 30, in particular its toothing 48 has a first width running in the axial direction of the differential stage planetary gear 46, over which, for example, the toothing 48 engages the sun gear 14.
  • the coupling planetary gear 44 in particular its toothing 52, has a second width running in the axial direction of the differential stage planetary gear 46, in particular a second toothing width, over which, for example, the toothing 52 engages the differential planetary gear 36.
  • the first width is also referred to, for example, as b1
  • the second width is also referred to, for example, as b2.
  • the intermediate region 60 has a third width running in the axial direction of the differential stage planetary gear 46, which is also designated b3.
  • Fig. 5 shows a schematic front view of a second embodiment of the differential stage planetary gear 46.
  • the toothings 48 and 52 are rotationally oriented relative to one another in the circumferential direction of the differential stage planetary gear 46 running around the first planetary axis of rotation 32 in such a way that the first gaps 56 of the first toothing 48 of the first differential planetary gear 30, viewed in the axial direction of the differential stage planetary gear 46, are aligned with the second teeth 54 of the second toothing 52 of the coupling planetary gear 44, and that the first teeth 50 of the first toothing 48 of the first differential planetary gear 30, viewed in the axial direction of the differential stage planetary gear 46, are aligned with the second gaps 58 of the second toothing 52 of the coupling planetary gear 44.
  • the toothings 48 and 52 are not aligned, but are offset or rotated by an offset angle V in the circumferential direction of the differential stage planetary gear 46 running around the first planetary axis of rotation 32, so that, for example, at least respective Partial regions of the teeth 50 and the gaps 58 and at least respective partial regions of the gaps 56 and the teeth 54 are arranged at the same height or in the same rotational position when viewed around the circumferential direction of the differential stage planetary gear 46.
  • the third width b3 of the intermediate region 60 is smaller than the first width b1 of the first stepped planet and smaller than the second width b2 of the second stepped planet. It is conceivable that the first width and the second width are the same or the first width and the second width can differ from one another.
  • the first sun gear 14 has a third number of teeth and a third toothing module, third toothing which engages in the first differential planet gear 30, in particular in its first toothing 48, and has third teeth with a respective third tooth height.
  • the second sun gear 16 has, for example, a fourth toothing having a fourth number of teeth and a fourth toothing module, which engages in the second differential planet gear 36, in particular in its fifth toothing, and has fourth teeth with a respective fourth tooth height.
  • the third number of teeth and the fourth number of teeth differ from one another, wherein preferably the third toothing module and the fourth toothing module are the same, so that preferably the respective third tooth height and the respective fourth tooth height are the same. It is therefore preferably provided that all toothings of the spur differential 12 are straight-toothed.
  • Fig. 6 and 7 show a third embodiment of the transmission device 10 in a schematic front view and in a schematic and sectional side view, respectively.
  • the transmission device 10 has a planetary gear 62 provided in addition to the spur gear differential 12, which is explained in more detail below.
  • the planetary gear 62 has at least one stepped planetary gear 64 provided in addition to the differential stage planetary gear 46 or in addition to the differential stage planetary gears 46, which is held on the planetary carrier 28 so as to be rotatable about the second planetary axis of rotation 40 relative to the planet carrier 28.
  • the stepped planetary gear 64 is arranged on, in particular on, the second bolt 42 so as to be rotatable about the planetary axis of rotation 40 relative to the bolt 42 and relative to the planet carrier 28. in particular mounted.
  • the stepped planetary gear 64 is arranged coaxially to the second differential planetary gear 36.
  • the second differential planetary gear 36 and the stepped planetary gear 64 are rotatable relative to one another about the second planetary axis of rotation 40.
  • the planetary gear 62 can have at least one further or several further stepped planetary gears, wherein the previous and following statements on the stepped planetary gear 64 can be readily transferred to the respective further stepped planetary gear and vice versa.
  • a respective stepped planetary gear 64 is provided for each second differential planetary gear 36.
  • the stepped planetary gear 64 has a first planetary gear 66 and a second planetary gear 68, wherein the planetary gears 66 and 68 are connected to one another in a rotationally fixed manner, in particular permanently.
  • the planetary gears 66 and 68 are spur gears.
  • the planetary gears 66 and 68 are gears which are designed as spur gears.
  • the planetary gears 66 and 68 are also straight-toothed.
  • the planetary gear 66 is also referred to as the third stepped planet
  • the planetary gear 68 is also referred to as the fourth stepped planet.
  • the planetary gears 66 and 68 are different sizes, thus have different pitch circle diameters and/or different pitch circle diameters, in this case such that the planetary gear 66 has a fifth pitch circle diameter and the planetary gear 68 has a sixth pitch circle diameter which is smaller than the fifth pitch circle diameter. Therefore, the planetary gear 66 is also called the large planetary gear or larger planetary gear, and the planetary gear 68 is also called the small planetary gear or smaller planetary gear.
  • the planetary gear 62 also has a third sun gear 70, which is also referred to as a drive sun gear or drive sun, which is provided in addition to the first sun gear 14 and in addition to the second sun gear 16.
  • the third sun gear 70 is preferably also a spur gear and preferably has straight teeth. It can be seen that the large planet gear, in this case the planet gear 66, engages with the third sun gear 70. In other words, the large planet gear is in engagement with the third sun gear 70.
  • the planetary gear 62 also has a ring gear 72, which in the third embodiment is connected to the housing 18 in a rotationally fixed manner, in particular permanently. In an alternative embodiment, it would be conceivable for a switching element to be provided which can be switched between a coupled state and a decoupling state.
  • the ring gear 72 In the coupled state, for example, the ring gear 72 is connected to the housing 18 in a rotationally fixed manner by means of the switching element.
  • the switching element releases the ring gear 72 for rotations about the axis of rotation (sun gear rotation axis 20) relative to the housing 18, so that the ring gear 72 can rotate about the axis of rotation relative to the housing 18 in the uncoupled state.
  • the planetary gear 62 is thus arranged coaxially to the spur gear differential 12.
  • the sun gear 70 is arranged coaxially to the sun gears 14 and 16 and can therefore rotate about the sun gear rotation axis 20 relative to the housing 18.
  • the planet carrier 28 is a planet carrier common to the spur gear differential 12 and the planetary gear 62, on which the stepped planet gear 64 is also held so as to be rotatable about the second planetary rotation axis 40. It can be seen that the small planet gear, in this case the planet gear 68, is in engagement with the ring gear 72.
  • the sun gear 70 can be driven by the drive motor, so that the aforementioned drive torque can be provided, for example, via the planetary gear 62 and can be introduced into the spur gear differential 12 via the planetary gear 62 in order to thereby drive the planet carrier 28 and thus the spur gear differential 12.
  • the planet carrier 28 is preferably designed as a drive of the spur gear differential 12, via whose drive the aforementioned drive torque of the spur gear differential 12 can be introduced.
  • a dashed arrow 74 means “meshes with”, so that the dashed arrow 74 illustrates that the sun gear 70 meshes with the large planet gear (planet gear 66), and is therefore in engagement with the large planet gear.
  • the second differential planetary gear 36 is connected to the ring gear 72 and to the planetary gear 68 meshing with the ring gear 72 in a direction that runs in the axial direction of the second differential planetary gear 36 and thus runs parallel to the second planetary axis of rotation 40 or coincides with the second planetary axis of rotation 40, illustrated in Fig.
  • the first pitch circle diameter of the first sun gear 14 is larger than the second pitch circle diameter of the second sun gear 16.
  • the second sun gear 16 adjoins the sun gear 14 in an arrangement direction that runs in the axial direction of the sun gears 14 and 16 and thus runs parallel to the sun gear axis of rotation 20 or coincides with the sun gear axis of rotation 20, illustrated in Fig. 3 by an arrow 78, wherein in the present case the arrangement direction illustrated by the arrow 78 corresponds to the direction illustrated by the arrow 76.
  • the first sun gear 14 adjoins the third sun gear 70 in the arrangement direction (arrow 78), whereby the first sun gear 14 is arranged between the second sun gear 16 and the third sun gear 70 in the axial direction of the sun gears 14, 16 and 70 and thus along the sun gear rotation axis 20.
  • planet carrier walls 80 and 82 of the planet carrier 28, to whose planet carrier walls 80 and 82 the bolts 34 and 42 are fastened, in particular in a rotationally fixed manner, are located exclusively on the outside in the axial direction of the planetary gear 62 and the spur gear differential 12 and thus along the sun gear rotation axis 20, thus adjoining on both sides the ring gear 72, the stepped planet gear 64, the second differential planet gear 36, the differential stepped planet gear 46 and the sun gears 14, 16 and 70 and are thus arranged outside both the planetary gear 62 and the spur gear differential 12.
  • Fig. 8 and 9 show a fourth embodiment of the transmission device 10 in a schematic front view and in a schematic and sectional side view, respectively.
  • the small planetary gear (planetary gear 68) engages with the ring gear 72
  • the large planetary gear (planetary gear 66) engages with the third sun gear 70.
  • the large planetary gear (planetary gear 66) is arranged between the second differential planetary gear 36 and the small planetary gear (planetary gear 68), so that the planetary gear 66 in the axial direction of the stepped planetary gear 64 and the second differential planetary gear 36 is arranged between the second differential planetary gear 36 and the ring gear 72.
  • Fig. 3 shows a third embodiment of the differential stage planetary gear 46.
  • the differential planetary gear 30 and the associated coupling planetary gear 44 are formed separately from one another and are connected to one another in a rotationally fixed manner.
  • the coupling planetary gear 44 has a projection 84, which in the present case is formed as a collar of the coupling planetary gear 44 or by a collar of the coupling planetary gear 44.
  • the differential planetary gear 30 is arranged on the projection 84 and, in particular permanently, is connected to the projection 84 in a rotationally fixed manner, as a result of which the differential planetary gear 30 is, in particular permanently, connected to the coupling planetary gear 44 in a rotationally fixed manner.
  • the differential planetary gear 30 has a hub 36 in which the projection 84 is arranged.
  • the differential planetary gear 30 is connected via its hub 86, in particular permanently, in a rotationally fixed manner to the projection 84 and thus to the coupling planetary gear 44.
  • Fig. 11 shows a fourth embodiment of the differential stage planetary gear 46.
  • the first differential planetary gear 30 and the associated coupling planetary gear 44 are formed integrally with one another and are thereby connected to one another in a rotationally fixed manner, in particular permanently.
  • an area is designated B.
  • a radial outer contour 88 of the differential stage planetary gear 46 in the transition area (intermediate area 60) does not fall below a first tip circle diameter k1 of the second toothing 52, but rather increases from the first tip circle diameter k1 to a second tip circle diameter k2 of the first toothing 48, in particular at least substantially continuously.
  • machining, in particular production, of the toothing 52 and/or the toothing 48 takes place, in particular by means of a toothing tool, so that area B is, for example, a tool run-out area.
  • Fig. 12 shows a fifth embodiment of the differential stage planetary gear 46. From Fig. 12 it can be seen that in the fifth embodiment the intermediate region 60 (transition region) is free of teeth.
  • the spur gear differential 12 comprises the planet carrier 28, which is driven or drivable in any way, and the two differently sized sun gears 14 and 16, which simultaneously form the two outputs, also referred to as outputs. represent outputs of the spur gear differential 12.
  • the spur gear differential 12 also comprises the differential stage planetary gear 46 or preferably a group of identical differential stage planetary gears 46, wherein the group each comprises at least or more than two identical differential stage planetary gears 46.
  • the differential stage planetary gears 46 are preferably arranged evenly distributed in the circumferential direction of the spur gear differential 12 running around the sun gear axis of rotation 20, in particular over a respective circumference of the respective sun gear 14, 16.
  • the spur gear differential 12 also comprises the second differential planetary gear 36 or preferably a group of identical differential planetary gears 36, wherein the plurality of differential planetary gears 36 are preferably arranged evenly distributed in the circumferential direction of the spur gear differential 12 running around the sun gear axis of rotation 20.
  • a respective second differential planetary gear 36 is provided for each differential stage planetary gear 46.
  • the differential stage planetary gears 46 and the second differential planetary gears 36 are rotatably mounted on, in particular on, their respective associated bolts 34 and 42. For example, rolling and/or sliding bearings can be used for this.
  • the bolts 34 and 42 are attached to, in particular in, the planet carrier 28, in particular in a rotationally fixed manner.
  • the planet carrier 28 can be designed in one or more parts, thus in one piece or in several parts.
  • the planet carrier 28 is mounted directly or indirectly, in particular rotatably, for example relative to the one or more part housing 18, which is designed, for example, as a gear housing or as a drive housing.
  • a direct bearing between the planet carrier 28 and the housing takes place via at least or exactly two bearings designed, for example, as sliding bearings or rolling bearings, in particular such that the planet carrier 28 is rotatably mounted on the housing 18 via the bearings mentioned, in particular such that the planet carrier 28 can rotate about the axis of rotation relative to the housing 18.
  • the second differential planetary gear 36 meshes with the second, smaller sun gear 16 and with the coupling planetary gear 44, which is smaller than the first differential planetary gear 30, in particular directly in each case, and preferably otherwise with no other, further gear.
  • the first differential planetary gear 30 meshes, for example, exclusively with the first, larger sun gear 14.
  • WS 1 designates the first pitch circle diameter of the first sun gear 14, WS2 the second pitch circle diameter of the second sun gear 16, WSP1 the third pitch circle diameter of the first differential planetary gear 30 and WSP2 the fourth pitch circle diameter of the coupling planetary gear 44.
  • the first pitch circle diameter is larger than the second pitch circle diameter
  • the third pitch circle diameter is larger than the fourth pitch circle diameter.
  • All of the gear teeth of the spur gears can be straight or helical. Straight teeth are preferred. If, as shown in Fig. 4, the gear teeth 48 and 52 are oriented rotationally to one another in such a way that the teeth 50 are exactly aligned with the teeth 54, so that gap 56 is exactly aligned with gap 58 and tooth 50 is exactly aligned with tooth 54, a tool outlet for a gear cutting tool for producing the smaller gear teeth 52 can, for example, protrude into the gaps of the larger gear teeth 48 to a certain extent, without removing material in the area of the larger gear teeth 48. 90 designates a collar by means of which a particularly wide bearing base of the stepped planetary gear 64 can be formed.
  • the unusable intermediate region 60 between the gears 48 and 50 in the axial direction of the differential stage planetary gear 46 can be kept small or short.
  • the rotationally fixed connection between the differential planetary gear 30 and the associated coupling planetary gear 44 can be implemented via a press fit, via a spline, a weld seam, a combination of these connections or in another way.
  • One advantage here is that the differential planetary gear 30 and the associated coupling planetary gear 44 can be designed axially directly adjacent, i.e. without the intermediate region 60, which makes it possible to have a particularly short axial design.
  • the intermediate region 60 with the width B3 is between the differential planetary gear 30 and the coupling planetary gear 44, thus between the Gearings 48 and 52 are provided.
  • the intermediate region 60 there is, for example, the tool run-out of the gear cutting tool for producing the gearing 52 of the coupling planetary gear 44.
  • the gear cutting tool also simply referred to as a tool, even runs, for example, into the area of the gearing 48 of the differential planetary gear 30, but only into the gaps 56 of the gearing 48, so that the gearing 48 is not damaged, machined or otherwise impaired by the gear cutting tool by means of which the gearing 52 is produced.
  • the teeth 54 of the gearing 52 grow, so to speak, from the second pitch circle diameter or from the tip circle diameter k1 to the first pitch circle diameter or to the tip circle diameter k2.
  • the radial outer contour 88 of the differential planetary gear 46 therefore does not fall below the tip diameter k1 of the coupling planetary gear 44, which is smaller than the first differential planetary gear 30, in the intermediate region 60.
  • the difference between the first pitch circle diameter of the differential planetary gear 30 and the second pitch circle diameter of the coupling planetary gear 44 is chosen to be as small as possible, since the width b3 of the intermediate region 60 can be kept small as a result.
  • the differential stage planetary gear 46 can be designed as a single piece or in one piece, which means that costs can be kept particularly low.
  • the width b3 which represents a distance between the differential planetary gear 30 and the coupling planetary gear 44 in the axial direction of the differential stage planetary gear 46, can be kept small.
  • the intermediate region 60 with the width b3 exists between the two toothings 48 and 52 or between the differential planetary gear 30 and the associated coupling planetary gear 44 in the axial direction of the differential stage planetary gear 46, wherein in the fifth embodiment shown in Fig. 12, within the intermediate region 60, the outer diameter of the differential stage planetary gear 46 is significantly smaller than the smaller tip circle diameter k1 of the teeth 54 compared to the tip circle diameter k2 of the teeth 50 or the toothing 48. or the gearing 52.
  • the outer diameter is designated by a in Fig. 12.
  • the outer diameter a can even be the same size or smaller than a root circle diameter of the gearing 52 in this intermediate region 60.
  • the gear cutting tool for producing the gearing 52 does not penetrate into the region or into the gaps 56 of the gearing 48.
  • This rotational alignment or rotation of the gears 48 and 52 can at least be freely selected, but should be the same size for all differential stage planetary gears 46 so that the spur gear differential 12 can be easily assembled.
  • the gears 52 and 48 should not necessarily have the same number of teeth.
  • the disadvantage of this can be a large width b3 between the gears 48 and 52, but this can be considered acceptable.
  • the resulting advantages can be:
  • the number of teeth in the gears 48 and 52 are identical, whereby, for example, as is provided in the first embodiment shown in Fig. 4, the teeth 50 and 54 of the two gears 48 and 52 are aligned in the axial direction of the differential stage planetary gear 46.
  • the gears 48 and 52 viewed in the circumferential direction of the differential stage planetary gear 46, are arranged rotated relative to one another in contrast to the mutually aligned alignment.
  • V offset angle a outside diameter k1 first tip circle diameter k2 second tip circle diameter

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Abstract

L'invention concerne un dispositif de boîte de vitesses (10) pour un véhicule à moteur, ledit dispositif de boîte de vitesses comprenant un différentiel à engrenage cylindrique à denture droite (12) qui présente un premier pignon planétaire (14) qui est réalisé sous la forme d'une première sortie du différentiel à engrenage cylindrique à denture droite (12) et en tant que premier engrenage cylindrique à denture droite et qui présente un premier diamètre primitif. Le différentiel à engrenage cylindrique à denture droite (12) comprend : un second pignon planétaire (16) qui est disposé de manière coaxiale par rapport au premier pignon planétaire (14) et qui est conçu en tant que seconde sortie du différentiel à engrenage cylindrique à denture droite (12) et en tant que second engrenage cylindrique à denture droite et comprend un second diamètre primitif qui diffère du premier diamètre primitif. Le différentiel à engrenage cylindrique à denture droite (12) comprend au moins un train planétaire (26), au moyen duquel les pignons planétaires (14, 16) sont accouplés les uns aux autres de telle sorte que les pignons planétaires (14, 16) peuvent tourner dans des directions opposées, le train planétaire (26) comprenant un porte-satellites (28). Le train planétaire (26) comprend un premier pignon planétaire différentiel (30) qui s'engage dans le premier pignon planétaire (14), comprend un troisième diamètre primitif, et est maintenu sur le porte-satellites (28) de façon à pouvoir tourner par rapport au porte-satellites (28) autour d'un premier axe de rotation de satellite (32).
PCT/EP2023/080012 2022-10-31 2023-10-26 Différentiel à engrenage cylindrique à denture droite pour véhicule automobile WO2024094546A1 (fr)

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DE102022004088.3A DE102022004088A1 (de) 2022-10-31 2022-10-31 Getriebevorrichtung für ein Kraftfahrzeug sowie Kraftfahrzeug, insbesondere Kraftwagen

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WO2014019744A1 (fr) * 2012-07-31 2014-02-06 Schaeffler Technologies AG & Co. KG Différentiel à pignons droits
DE102014203522A1 (de) 2014-02-27 2015-08-27 Schaeffler Technologies AG & Co. KG Stirnraddifferentialgetriebe mit lastabhängig variierendem Überbrückungsmoment
CN105909757A (zh) * 2016-07-08 2016-08-31 天津天海同步科技有限公司 紧凑型差速器
WO2016135703A1 (fr) * 2015-02-27 2016-09-01 E-Aam Driveline Systems Ab Module d'entraînement comportant un mécanisme de différentiel compact
DE102018128836B3 (de) 2018-11-16 2019-10-02 Schaeffler Technologies AG & Co. KG Getriebevorrichtung für ein Kraftfahrzeug
DE102015214035B4 (de) 2015-07-24 2019-10-02 Schaeffler Technologies AG & Co. KG Elektronische Antriebseinheit für ein Kraftfahrzeug
US20210364075A1 (en) * 2020-05-22 2021-11-25 Leonidas Kyros Kontopoulos Variable torque differential

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DE811650C (de) 1948-12-28 1951-08-23 Arthur Gaunitz Stirnrad-Differentialgetriebe fuer Kraftfahrzeuge
DE102004015278A1 (de) 2004-03-29 2005-10-20 Josef Gail Differentialgetriebe
JP4981694B2 (ja) 2008-01-08 2012-07-25 株式会社ユニバンス 動力伝達装置
US20170175868A1 (en) 2015-12-16 2017-06-22 Atieva, Inc. Parallel Axis Epicyclic Gear Differential
DE102019203655A1 (de) 2019-03-19 2020-09-24 Zf Friedrichshafen Ag Stirnraddifferentialgetriebe für ein Fahrzeug

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* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2014019744A1 (fr) * 2012-07-31 2014-02-06 Schaeffler Technologies AG & Co. KG Différentiel à pignons droits
DE102014203522A1 (de) 2014-02-27 2015-08-27 Schaeffler Technologies AG & Co. KG Stirnraddifferentialgetriebe mit lastabhängig variierendem Überbrückungsmoment
WO2016135703A1 (fr) * 2015-02-27 2016-09-01 E-Aam Driveline Systems Ab Module d'entraînement comportant un mécanisme de différentiel compact
DE102015214035B4 (de) 2015-07-24 2019-10-02 Schaeffler Technologies AG & Co. KG Elektronische Antriebseinheit für ein Kraftfahrzeug
CN105909757A (zh) * 2016-07-08 2016-08-31 天津天海同步科技有限公司 紧凑型差速器
DE102018128836B3 (de) 2018-11-16 2019-10-02 Schaeffler Technologies AG & Co. KG Getriebevorrichtung für ein Kraftfahrzeug
US20210364075A1 (en) * 2020-05-22 2021-11-25 Leonidas Kyros Kontopoulos Variable torque differential

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