Differential transmission for vehicle

Abstract

A differential transmission for a vehicle is provided. The differential transmission (3) for a vehicle (1) includes a first output shaft (5), a second output shaft (6), a first planetary gear set (10), a second planetary gear set (20), and a fixed member (31). The first planetary gear set (10) includes a first sun gear (11), a first carrier (12), first planetary gears (13), and a first ring gear (14). The second planetary gear set (20) includes a second sun gear (21), a second carrier (22), second planetary gears (23), and a second ring gear (24). The first planet carrier (12) is connected to the first output shaft (5) by an anti-torque connection (30). The second ring gear (24) is connected to the second output shaft (6). The first ring gear (14) is rotationally fixed to the second sun gear (21). The second planet carrier (22) is supported at the fixed member (31). The first planet carrier (12) is rotatably supported at the fixed part (31) by a support (40). The support (40) of the first planet carrier (12) is arranged opposite the anti-torque connection (30) in the axial direction with respect to the first planet gear (13).

Description

Technical Field

[0001] The invention relates to a differential transmission for a vehicle. The invention also relates to a drive unit with a differential transmission and to a vehicle with a drive unit. Background Art

[0002] Differential transmissions are commonly used in vehicles. Differential transmissions are used so that drive wheels driven by the same motor can have different rotation speeds. This is necessary, for example, when turning. The drive wheels on the inside of the curve cover a shorter path than the drive wheels on the outside of the curve. Therefore, the drive wheels on the inside of the curve must rotate slower than the drive wheels on the outside of the curve.

[0003] The object of the present invention is to provide an improved differential transmission which has an extended service life, can be produced more cost-effectively and requires less installation space.

[0004] This object is achieved by a differential transmission having the features of claim 1 . Summary of the invention

[0005] A differential transmission for a vehicle comprises a first output shaft, a second output shaft, a first planetary gear set, a second planetary gear set and a fixed component. The first output shaft and the second output shaft may extend out of the fixed component in an axial direction. In this case, the axial direction may be determined by the rotation axis of the first output shaft. The first output shaft and the second output shaft may be coaxial with each other. The vehicle may be, for example, a commercial vehicle such as a truck, a construction machine or an agricultural machine or a bus.

[0006] The first planetary gear set includes a first sun gear, a first planet carrier, a first planet gear and a first ring gear. The first planetary gear set may include a plurality of planet gears, preferably three planet gears. The first planetary gear set may be formed as a positive planetary gear set or a negative planetary gear set. The first sun gear is engaged with the first planet gear, and the first planet gear is engaged with the first ring gear. The engagement between the two gears is achieved by overlapping the gears in the axial direction and spacing the axes of rotation of the gears in the radial direction, so that at least one tooth of one gear contacts the teeth of the second gear. The first sun gear, the first planet carrier and the first ring gear may be arranged coaxially with each other. The first sun gear may be used to drive the first planetary gear set.

[0007] The first planet carrier can be used as output and is connected to the first output shaft via a torsion-proof connection. The torsion-proof connection can be arranged adjacent to the second output shaft in the region of the end of the first output shaft located in the fixed component. The first output shaft can be arranged coaxially with the first sun gear.

[0008] If two elements are connected to each other, they are coupled to each other directly or indirectly so that a movement of one element causes a reaction of the other element. For example, the connection can be provided by a form-fitting or friction-fitting connection. The connection can correspond to the meshing of corresponding teeth of the two elements. In this case, further elements, such as one or more spur gear stages, can be provided between the elements. For example, the connection can be torsion-proof.

[0009] The torsion-proof connection of two elements is understood to mean a connection in which the two elements are rigidly coupled to one another in all expected states of the transmission so that they have essentially the same rotational speed. In this case, the elements can exist as separate components which are torsionally coupled to one another or connected in an integral manner. The torsion-proof connection can be configured as a spline shaft connection or a toothed shaft connection. In this case, a fixing element, such as a fixing ring, a retaining ring or a spiral ring, can be provided to limit the relative movement in the axial direction. The torsion-proof connection can be configured as a press connection or as a threaded connection via a flange of the first planet carrier and the first output shaft.

[0010] The first planet carrier is rotatably supported at the fixed part via a support. The support of the first planet carrier is arranged opposite to the torsion-proof connection in the axial direction relative to the first planet gear. The axial direction can be the axial direction of the planet bridge at the first planet carrier on which the first planet gear is rotatably supported. The support of the first planet carrier can be designed as a needle roller sleeve without an inner ring. The bushing can be present in the needle roller sleeve. If the first planet carrier is produced at least in sections from hardened steel, the bushing can be omitted.

[0011] As a result, the first planet carrier can be constructed thinner and the service life of the differential transmission can be extended. In this case, it is not necessary to guide oil between the first output shaft and the second output shaft. As a result, the second output shaft is not weakened and can be constructed with thin walls, which leads to a lower weight. In addition, corresponding sealing elements can be omitted, which leads to cost advantages, installation space advantages and weight advantages. It is not necessary to directly supply oil to the support of the second output shaft via the fixed component, because fewer support parts require oil in total.

[0012] The second planetary gear set includes a second sun gear, a second planet carrier, a second planet gear and a second ring gear. The second planetary gear set may include a plurality of planet gears, preferably three planet gears. The second planetary gear set may be formed as a positive planetary gear set or a negative planetary gear set. The second sun gear is engaged with the second planet gear, and the second planet gear is engaged with the second ring gear. The second sun gear, the second planet carrier and the second ring gear may be arranged coaxially with each other and coaxially with the first sun gear, the first planet carrier and the first ring gear. The second ring gear is connected to the second output shaft in a torsionally fixed manner. The connection of the second ring gear to the second output shaft may be constructed as a press connection, or by a threaded connection in the axial direction of the second planet carrier to the second ring gear, or by a shaft-hub connection.

[0013] The first ring gear is connected to the second sun gear in a rotationally fixed manner.The first ring gear can be connected to the second sun gear in a rotationally fixed manner, for example, by a dog connection, a toothed shaft connection or by a threaded connection.

[0014] The second planet carrier is supported at the fixed component. The support of the second planet carrier at the fixed component can be constructed by a press connection, material bonding or threaded connection of the second planet carrier to the fixed component in the axial direction. Alternatively, the second planet carrier can be fixed to the fixed component via a switching element. The torsion-proof connection between the two elements can be selectively established or released via a switching element (e.g., a clutch). The second planet carrier may include a second planet bridge, and the second planet gear is rotatably supported at the second planet bridge. The second planet bridge can be supported at the fixed component. A cylindrical protrusion of the fixed component can form the second planet bridge.

[0015] The fixed component may be a transmission housing. The transmission housing may completely surround the first planetary gear set and the second planetary gear set. The transmission housing may include a recess to enable a mechanical connection from the outside of the transmission housing to the first sun gear. In addition, the transmission housing may include a recess to enable the first output shaft and the second output shaft to extend to the outside of the transmission housing.

[0016] In an embodiment, the support of the first planet carrier can be supported at the cylindrical outer periphery of a section of the fixed component. For example, the cylindrical outer periphery can be arranged at a cylindrical protrusion protruding from the fixed component in the axial direction. An intermediate element can also be provided, which provides a cylindrical outer periphery and is supported at the fixed component. The outer periphery of the support of the first planet carrier is arranged at the cylindrical inner periphery of a section of the first planet carrier. An intermediate element can also be provided, which provides a cylindrical inner periphery and is supported at the first planet carrier.

[0017] In an embodiment, the support of the first planet carrier can be supported at the cylindrical inner periphery of a section of the fixed component. For example, the cylindrical inner periphery can be arranged in a hole or a recess in the fixed component in the axial direction. An intermediate component can also be provided, which provides the cylindrical inner periphery and is supported at the fixed component. The inner periphery of the support of the first planet carrier is arranged at the cylindrical outer periphery of a section of the first planet carrier. An intermediate component can also be provided, which provides the cylindrical outer periphery and is supported at the first planet carrier.

[0018] In an embodiment, the first output shaft may be rotatably supported at the second output shaft by a support. The support of the first output shaft may be arranged opposite to the support of the first planetary carrier in the axial direction relative to the first planetary gear. The first output shaft may extend in sections within the second output shaft. The outer periphery of a section of the first output shaft and the inner periphery of a section of the second output shaft may form a gap. The support of the first output shaft may be arranged in the gap. The support of the first output shaft may include a floating bearing. For example, a needle bearing or a sliding bearing may form a floating bearing of the first output shaft. Therefore, the support of the first planetary carrier may be improved, and the service life of the differential transmission may be extended.

[0019] In an embodiment, the support of the first output shaft may be arranged between the first planet carrier and the second output shaft. In other words, the first output shaft may be indirectly supported by the support of the first output shaft. The outer periphery of a section of the first planet carrier and the inner periphery of a section of the second output shaft may form a gap. The support of the first output shaft may be arranged in the gap. The first output shaft may be supported at the first planet carrier, for example, by a torsion-proof connection. The first output shaft is then supported at the second output shaft via the first planet carrier by the support of the first output shaft.

[0020] The first output shaft may be rotatably supported by a support member that is arranged on one side of the support member of the first planet carrier in the axial direction relative to the first planetary gear. For example, the support member of the first output shaft may rotatably support the first output shaft at a fixed component.

[0021] In an embodiment, the second planetary gear set may be arranged to be offset in the axial direction relative to the first planetary gear set. The second planetary gear set may be arranged completely outside the first planetary gear set in the axial direction. The first planetary gear set may overlap with the first output shaft in the axial direction. The second planetary gear set may overlap with the second output shaft in the axial direction. The second planetary gear set may be offset in the axial direction relative to the second output shaft.

[0022] In an embodiment, the second sun gear may be arranged in the radial direction inside the first ring gear. The diameter of the second sun gear may be greater than the diameter of the first ring gear. Thus, a compact design of the differential transmission is possible in the radial direction.

[0023] In an embodiment, the differential transmission may include a sun ring gear that forms a first ring gear at an inner periphery and a second sun gear at an outer periphery. The first planetary gear set may overlap with the second planetary gear set in an axial direction. All gear set elements may be arranged in the same plane in an axial direction. All gear set elements may be aligned with each other in an axial direction so that corresponding teeth engage with each other. The first planetary gear set and the second planetary gear set may overlap with the first output shaft in an axial direction.

[0024] The sun ring gear can be constructed in one piece. In an alternative embodiment, the sun ring gear can be constructed in multiple parts. In this case, the sun ring gear includes a first ring gear, a second sun gear and a coupling element. The first ring gear can then be connected to the inner periphery of the coupling element in a torsion-proof manner. The second sun gear can then be connected to the outer periphery of the coupling element in a torsion-proof manner.

[0025] The sun ring gear may be constructed in an annular manner. The first ring gear may be arranged radially within the second sun gear, and the first ring gear may overlap with the second sun gear in the axial direction. The first ring gear and the second sun gear may overlap so that the gear with a smaller extension in the axial direction is arranged within the other gear. For example, the second sun gear may be wider than the first ring gear in the axial direction. Then, the first ring gear may be arranged in the axial direction within the second sun gear so that the first ring gear does not protrude from the second sun gear in the axial direction.

[0026] In an embodiment, the differential transmission may include an input element, which may be connected to the first sun gear in a torsion-proof manner and which may be rotatably supported at a fixed component by a support. The torsion-proof connection between the input element and the first sun gear may be constructed as a shaft-hub connection, a press connection or a threaded connection via flanges of the sun gear and the input element.

[0027] The support of the first planet carrier can overlap with the support of the input element in the axial direction. In particular, this embodiment can be used in combination with an arrangement of a support of a section of the first planet carrier that is located outside the support of the input element in the radial direction. Furthermore, this embodiment can be used in particular in combination with a support of the support of the first planet carrier at the cylindrical outer circumference of a section of the stationary component. For example, the support of the input element can be arranged completely within the support of the first planet carrier in the axial direction. In this case, a very compact differential transmission design in the axial direction is possible.

[0028] In an embodiment, the support of the first planet carrier can be arranged adjacent to the support of the input element in the axial direction. In particular, this embodiment can be used in combination with the support of the support of the first planet carrier at the cylindrical inner circumference of a section of the fixed component. This enables a simpler oil supply to the support of the first planet carrier. In this embodiment, the diameter of the cylindrical inner circumference of a section of the fixed component can be selected to be small. Advantageously, a small support diameter leads to low friction losses. As a result, the efficiency of the differential transmission can be increased.

[0029] Furthermore, a bushing of hardened steel can be arranged at the cylindrical outer circumference of a section of the first planet carrier. The first planet carrier can then be produced, for example, from aluminum. Alternatively, a section of the first planet carrier can serve as a running surface for a support of the first planet carrier. The planet carrier can, for example, be produced at least partially from hardened steel. A separate bushing of hardened steel serving as a running surface for a rolling element of a support of the first planet carrier can then be omitted at the cylindrical outer circumference of a section of the first planet carrier. This reduces the number of components of the differential transmission and enables a simple construction.

[0030] The cylindrical recess in the fixed part for the bearing seat where the outer ring of the support of the input element is mounted can be used to form the bearing seat where the outer ring of the support of the first planet carrier is mounted. In other words, both bearing seats can be produced in the fixed part by one machining step. This reduces production costs. The circumference of the bearing seat for supporting the input shaft can be larger than the circumference of the bearing seat for supporting the first planet carrier.

[0031] The first sun gear may be configured to be hollow. For example, the first sun gear may be configured to be annular. In this case, the first output shaft may extend through the first sun gear and be coaxial with the first sun gear. Therefore, a compact design of the differential transmission is possible.

[0032] The input element can be configured as a hollow shaft, wherein the first output shaft can extend through the input element. The first sun gear, the input element and the first output shaft can be arranged coaxially. Thus, a compact design of the differential transmission can be achieved.

[0033] The input element and the first sun gear may be formed integrally. In other words, the input element may form the first sun gear. Therefore, the number of components of the differential transmission may be reduced, and a compact design of the differential transmission may be achieved.

[0034] The second output shaft can be arranged coaxially with the first output shaft and opposite to the first output shaft in the axial direction relative to the fixed component. The first output shaft and the second output shaft can each extend to a drive wheel, a wheel hub or a joint shaft of the vehicle. Therefore, a compact design of the differential transmission is possible and the number of components of the differential transmission can be reduced. The torque introduced into the first sun gear can be transmitted to the first output shaft and the second output shaft.

[0035] The first output shaft and the second output shaft may each be rotatably supported at the fixed component by a support. The supports of the first output shaft and the second output shaft may be arranged coaxially with each other. The second output shaft may include a first support and a second support. The first support may be a floating bearing. The second support may be a fixed bearing. The first support of the second output shaft may be arranged outside the support of the first planetary carrier in a radial direction. The first support of the second output shaft may overlap with the support of the first planetary carrier in a radial direction. The first support of the second output shaft and the support of the first planetary carrier may be constructed identically. The second support of the second output shaft may be arranged in the support of the first planetary carrier in a radial direction.

[0036] In an embodiment, a fixing element for axially fixing the support of the first planet carrier can be arranged between the support of the first planet carrier and the support of the input element. The fixing element can be formed by a fixing ring or a retaining ring. This embodiment can be used in particular in combination with a support of the first planet carrier, which is arranged adjacent to the support of the input element. A shoulder can be provided for positioning the support of the first planet carrier in the axial direction. The shoulder can be arranged opposite the fixing element relative to the support of the first planet carrier. As a result, the support of the first planet carrier is easy to assemble.

[0037] In one aspect, the drive unit comprises a motor and a differential transmission according to the aforementioned embodiment. The motor is coupled to the differential transmission to drive the first sun gear.

[0038] In one aspect, a vehicle comprises a drive unit according to the aforementioned embodiment and a drive wheel. The drive unit is installed in the vehicle so as to drive the drive wheel. BRIEF DESCRIPTION OF THE DRAWINGS

[0039] Figure 1 A top view of a vehicle according to an embodiment is shown.

[0040] Figure 2 A cross-sectional view of a differential transmission for a vehicle according to an embodiment is shown.

[0041] Figure 3 A cross-sectional view of a differential transmission for a vehicle according to an embodiment is shown.

[0042] Figure 4A cross-sectional view of a differential transmission for a vehicle is shown according to an alternative embodiment.

[0043] Figure 5 A cross-sectional view of a differential transmission for a vehicle is shown according to an alternative embodiment.

[0044] Figure 6 A cross-sectional view of a differential transmission for a vehicle according to an embodiment is shown.

[0045] Figure 7 A cross-sectional view of a differential transmission for a vehicle is shown according to an alternative embodiment.

[0046] Figure 8 A detailed view of a differential transmission for a vehicle according to an alternative embodiment is shown in cross-section. DETAILED DESCRIPTION

[0047] Figure 1 A top view of a vehicle 1 according to an embodiment is shown. The vehicle 1 comprises a drive unit 2 having a motor 73, a differential transmission 3 having a first output shaft 5 and a second output shaft 6, a drive wheel 70, a first axle 71 and a second axle 72. In the present embodiment, the motor 73 is an electric motor. In an alternative embodiment, the motor 73 is an internal combustion engine. The motor 73 is connected to the differential transmission 3 so that the motor 73 can drive the first output shaft 5 and the second output shaft 6 through the differential transmission 3 and divide the driving power thereof.

[0048] The first output shaft 5 and the second output shaft 6 extend from the differential transmission 3 in opposite directions parallel to the first axle 71 toward the drive wheels 70. The first output shaft 5 extends through the transmission 3 and the motor 73. In the present case, the first axle 71 is a driven rear axle of the vehicle 1. In an alternative embodiment, the first axle 71 may be a driven front axle of the vehicle 1. The first output shaft 5 and the second output shaft 6 are connected to the drive wheels 70 of the vehicle 1 so that the first output shaft 5 and the second output shaft 6 can each drive one of the drive wheels 70.

[0049] One of the drive wheels 70 transmits the driving power of the motor 73 to the ground, the drive wheel 70 rests on the ground and generates the driving movement of the vehicle 1. The steering wheel 74 of the vehicle 1 is rotatably arranged at the second axle 72, which is the front axle in this case. In an alternative embodiment, the second axle 72 can be the rear axle of the vehicle 1.

[0050] In another embodiment, a joint and a hub may be arranged between the respective drive wheel 70 and the first and second output shafts 5 , 6 in order to compensate for possible misalignments of the first and second output shafts 5 , 6 .

[0051] Figure 2A cross-sectional view of a differential transmission 3 for a vehicle 1 according to an embodiment is shown. Figure 2 : is a half-section showing the upper part of the differential transmission 3. The differential transmission 3 includes a fixed component 31, an input element 4, a first output shaft 5 and a second output shaft 6. The first output shaft 5 and the second output shaft 6 extend out of the fixed component 31 in opposite directions. The differential transmission 3 also includes a first planetary gear set 10, which has a first sun gear 11, a first planet carrier 12, a plurality of first planetary gears 13 and a first ring gear 14. The first planetary gears 13 are each rotatably supported by a first planetary bridge. The first planet carrier 12 is supported in the fixed component 31 by a support 40. The first sun gear 11 is engaged with the first planetary gear 13. The first planetary gear 13 is engaged with the first ring gear 14. The differential transmission 3 also includes a second planetary gear set 20, which has a second sun gear 21, a second planet carrier 22, a plurality of second planetary gears 23 and a second ring gear 24. The second planetary gears 23 are each rotatably supported by a second planetary bridge. The second sun gear 21 is engaged with the second planetary gear 23. The second planetary gear 23 is engaged with the second ring gear 24. The first sun gear 11, the first planetary gears 13 and the first ring gear 14 overlap in the axial direction. In addition, the second sun gear 21, the second planetary gears 23 and the second ring gear 24 overlap in the axial direction. The first planetary gear set 10 is arranged offset in the axial direction relative to the second planetary gear set 20. The first planetary gear set 10 overlaps with the first output shaft 5 and the input element 4 in the axial direction. The second planetary gear set 20 overlaps with the second output shaft 6 in the axial direction. In an alternative embodiment, the second planetary gear set 20 partially overlaps with the second output shaft 6 in the axial direction. In an alternative embodiment, the second planetary gear set is offset in the axial direction relative to the second output shaft 6.

[0052] The support member 40 of the first planet carrier 12 is described in more detail below.

[0053] The support 40 of the first planet carrier 12 is arranged in the axial direction opposite to the first planet gears 13 of the first planetary gear set 10 and the torsion-proof connection 30 of the first planet carrier 12 and the first output shaft 5. Therefore, the first planet carrier 12 is supported on both sides in the axial direction relative to the first planet gears 13. Therefore, the radial force from one of the first planet gears 13 can be distributed to the support 40 and the torsion-proof connection 30 of the first planet carrier 12. This results in a more uniform force distribution in the first planet carrier 12 and a precise positioning of the first planet gears 13 at the first planet carrier 12.

[0054] The support 40 of the first planet carrier 12 is in this case constructed as a needle roller sleeve without an inner ring. The support 40 of the first planet carrier 12 also includes a bushing 44, which is a hardened steel sleeve in this case. The bushing 44 is arranged radially inside the needle roller sleeve. Therefore, the needle rollers of the needle roller sleeve can roll at the bushing 44. The bushing 44 is positioned so that it protrudes beyond the needle roller sleeve in the axial direction. The width of the bushing 44 in the axial direction is greater than the width of the needle roller sleeve. If the fixed part is made of hardened steel at least in some sections and hardened at least in some sections, the bushing 44 of the support 40 of the first planet carrier 12 can be omitted.

[0055] Further details of the embodiments are described below.

[0056] The differential transmission 3 further includes an input element 4 . The input element 4 is rotatably supported on the fixed component 31 via a support 43 .

[0057] The support member 40 of the first planet carrier 12 overlaps the support member 43 of the input element 4 in the axial direction. In this case, the support member 40 of the first planet carrier 12 is arranged outside the support member 43 of the input element 4 in the radial direction. Thereby, a compact installation space of the differential transmission 3 in the axial direction can be achieved.

[0058] The input element 4 is configured as a hollow shaft. The input element 4 can rotate about its central axis. The input element 4 is connected to the rotor shaft of the motor 73 in a rotationally fixed manner and is driven together with the rotor shaft of the motor 73. Figure 2 The first sun gear 11 is configured to be hollow and is integrated with the input element 4. The first output shaft 5 extends through the first sun gear 11 and the input element 4 and is coaxial with the first sun gear 11.

[0059] The first ring gear 14 is rotationally fixedly connected to the second sun gear 21 by a claw connection (e.g. crown teeth). The first ring gear 14 and the second sun gear 21 are positioned relative to each other in the axial direction by a fixing element 56, in the present case a retaining ring. In an alternative embodiment, the first ring gear 14 is rotationally fixedly connected to the second sun gear 21 by a toothed shaft connection or by a threaded connection. The second sun gear 21 is arranged in the first ring gear 14 in the radial direction. The second planet carrier 22 is rotationally fixedly supported at the fixed component 31 by the second planet carrier 22 being fastened to the fixed component 31 in the axial direction. The second ring gear 24 is rotationally fixedly connected to the second output shaft 6. The first output shaft 5 and the second output shaft 6 are coaxially constructed with respect to each other and are rotatably supported in the fixed component 31.

[0060] In another embodiment including all the features of the previous embodiment, the fixed component 31 is a two-part transmission housing. Figure 2Detail of the first part of the two-part transmission housing is shown on the left side of the differential transmission 3. Figure 2 Detail of the second part of the two-part transmission housing is shown on the right side of the differential transmission 3. The two parts of the two-part transmission housing are circumferentially connected to each other by a threaded connection. Figure 2 The threaded connection is not shown.

[0061] In another embodiment including all the features of the previous embodiment, the support 40 of the first planet carrier 12 forms a floating bearing. In the present case, the support 43 of the input element 4 is a grooved ball bearing and forms a fixed bearing. The first output shaft 5 is rotatably supported in the fixed part 31 by a support, not shown. The support of the first output shaft 5, in the present case a grooved ball bearing, is configured as a fixed bearing.

[0062] The second output shaft 6 is rotatably supported at the fixed part 31 by a first support 41 and a second support 42. The first support 41 of the second output shaft 6 (in this case a needle bearing) is a floating bearing. The second support 42 of the second output shaft 6 (in this case a grooved ball bearing) is a fixed bearing. In an alternative embodiment, the first support 41 is configured as a fixed bearing and the second support 42 is configured as a floating bearing.

[0063] In another embodiment including all the features of the aforementioned embodiment, the width of the first sun gear 11 in the axial direction is greater than the width of the first planetary gears 13. Further, the width of the sun ring gear 32 in the axial direction is respectively greater than the widths of the first planetary gears 13 and the second planetary gears 23. In addition, in order to position the sun ring gear 32 in the axial direction relative to the first planetary gears 13, in this case, fixing elements 56, 57 and thrust washers are provided at the inner periphery of the sun ring gear 32 on both sides of the first planetary gears 13.

[0064] In another embodiment including all the features of the previous embodiment, the outer ring of the needle roller sleeve of the support 40 of the first planet carrier 12 is positioned in the axial direction by the shoulder of the first planet carrier 12 and the fixing element 50 (in this case a retaining ring). The bushing 44 is positioned in the axial direction by the shoulder of the fixing part 31 and the fixing element 51 (in this case a fixing ring).

[0065] The outer ring of the first support 41 of the second output shaft is positioned in the axial direction by a shoulder in the fixed part 31 and by a fixing element 53, in this case a snap ring. The outer ring of the second support 42 is positioned in the axial direction by a shoulder in the fixed part 31 and a fixing element 58, in this case a snap ring. The inner ring of the second support 42 is positioned in the axial direction by a shoulder in the second output shaft 6 and a fixing element 54, in this case a snap ring.

[0066] The width of the second ring gear 24 is greater than the width of the second planetary gears 23. For the rotationally fixed connection of the second ring gear 24 to the second output shaft 6, in the present case, the second ring gear 24 and the second output shaft 6 each comprise teeth of a shaft-hub connection. Furthermore, the rotationally fixed connection comprises a fixing element 55, in the present case a snap ring, for relative positioning in the axial direction.

[0067] In another embodiment including all the features of the previous embodiment, the torsion-proof connection 30 of the first planet carrier 12 and the first output shaft 5 comprises a fixing element 52, in this case a snap ring, for axial relative positioning. The torsion-proof connection 30 is in this case configured as a toothed shaft connection. In an alternative embodiment, the torsion-proof connection 30 is formed by a threaded connection.

[0068] In another embodiment including all the features of the previous embodiment, the input element 4 in this embodiment is formed integrally with the rotor shaft and is rotatably supported at the fixed part 31 via a rotor support. In an alternative embodiment, the input element 4 includes teeth for a shaft-hub connection for a torsionally fixed connection of the input element 4 to the rotor shaft.

[0069] Figure 3 1 shows a cross-sectional view of a differential transmission 3 for a vehicle 1 according to an embodiment. Figure 2 The embodiment described differs in that the first output shaft 5 is rotatably supported at the second output shaft 6 via a support 45. The support 45 of the first output shaft 5 comprises a needle bearing and is configured as a floating bearing. The outer ring of the support 45 is positioned in the axial direction by a shoulder in the second output shaft 6 and a fixing element 59, in this case a snap ring. In an alternative embodiment, the support 45 of the first output shaft 5 comprises a sliding bearing. In an alternative embodiment, the support 45 of the first output shaft 5 is arranged between the first planet carrier 12 and the second output shaft 6. In this case, the first output shaft 5 is indirectly supported at the second output shaft 6 via the support 45 of the first output shaft 5.

[0070] Figure 4 A cross-sectional view of a differential transmission 3 for a vehicle 1 according to an alternative embodiment is shown. Figure 3 The embodiment described is different in that the first planetary gear set 10 overlaps the second planetary gear set 20 in the axial direction. The teeth of the first planetary gear set 10 and the second planetary gear set 20 are aligned with each other in the axial direction so that the corresponding teeth engage with each other. In the present case, the differential transmission 3 includes a sun ring gear 32 which is formed in one piece and which forms the first ring gear 14 at the inner periphery and the second sun gear 21 at the outer periphery.

[0071] Figure 5 A cross-sectional view of a differential transmission 3 for a vehicle 1 according to an alternative embodiment is shown. Figure 2 The embodiment described differs in that the support 40 of the first planet carrier 12 is supported at the cylindrical inner periphery of a section of the fixed part 31. The support 40 of the first planet carrier 12 is arranged adjacent to the support 43 of the input element 4 in the axial direction. The support 40 of the first planet carrier 12 is arranged in the radial direction within the support 43 of the input element 4. In an alternative embodiment, the support 40 of the first planet carrier 12 protrudes beyond the support 43 of the input element 4 in the radial direction. In the present case, the bushing 44 of the support 40 of the first planet carrier 12 can be omitted, because the first planet carrier 12 is made of hardened steel at least in some sections. In an alternative embodiment, the first planet carrier 12 is made of aluminum. The bushing 44 is then arranged at the outer periphery of a section of the first planet carrier 12.

[0072] In another embodiment, the outer ring of the support 40 of the first planet carrier 12 is positioned in the axial direction by a shoulder of the fixing part 31 and a fixing ring 50 (a snap ring in this case). In this case, the shoulder is arranged between the bearing 43 of the input element 4 and the bearing 40 of the first planet carrier 12.

[0073] Figure 6 1 shows a cross-sectional view of a differential transmission 3 for a vehicle 1 according to an embodiment. Figure 5 The embodiment described differs in that the first output shaft 5 is rotatably supported at the second output shaft 6 via a support 45. The support 45 of the first output shaft 5 comprises a needle bearing and is not configured as a floating bearing. In an alternative embodiment, the support 45 of the first output shaft 5 comprises a sliding bearing.

[0074] Figure 7 A cross-sectional view of a differential transmission 3 for a vehicle 1 according to an alternative embodiment is shown. Figure 6 The embodiment described is different in that the first planetary gear set 10 overlaps the second planetary gear set 20 in the axial direction. The teeth of the first planetary gear set 10 and the second planetary gear set 20 are aligned with each other in the axial direction so that the corresponding teeth engage with each other. In the present case, the differential transmission 3 includes a sun ring gear 32 which is formed in one piece and which forms the first ring gear 14 at the inner periphery and the second sun gear 21 at the outer periphery.

[0075] Figure 8 A detailed view of a differential transmission 3 for a vehicle 1 according to an alternative embodiment is shown in cross section. Figures 5 to 7The embodiment described differs in that the shoulders of the fixing ring 50 and the support 40 are interchanged. The fixing element 50 is arranged between the support 40 of the first planet carrier 12 and the support 43 of the input element 4. The outer diameter of the needle bearing of the support 40 of the first planet carrier 12 is smaller than the outer diameter of the grooved ball bearing of the support 43 of the input element 4.

[0076] Reference numerals

[0077] 1 Vehicle

[0078] 2. Drive unit

[0079] 3-speed differential transmission

[0080] 4 Input elements

[0081] 51st output shaft

[0082] 6 Second output shaft

[0083] 10.First planetary gear set

[0084] 11First sun gear of the first planetary gear set

[0085] 12First planet carrier of the first planetary gear set

[0086] 13 First planetary gear of the first planetary gear set

[0087] 14First ring gear of the first planetary gear set

[0088] 20 Second planetary gear set

[0089] 21 The second sun gear of the second planetary gear set

[0090] 22 Second planet carrier of the second planetary gear set

[0091] 23 The second planetary gear of the second planetary gear set

[0092] 24 Second ring gear of the second planetary gear set

[0093] 30 Anti-torsion connection

[0094] 31Fixed parts

[0095] 32 Sun ring gear

[0096] 40 Supporting member of the first planet carrier

[0097] 41 First support member of the second output shaft

[0098] 42 Second support member of the second output shaft

[0099] 43 Input element support

[0100] 44 Bushing

[0101] 45 Support member of the first output shaft

[0102] 50, 51, 52, 53, 54, 55, 56, 57, 58, 59 fixing elements

[0103] 70 driving wheel

[0104] 71 First Axle

[0105] 72 Second axle

[0106] 73 Motor

[0107] 74 Steering wheel

Claims

1. A differential transmission (3) for a vehicle (1), the differential transmission (3) comprising a first output shaft (5), a second output shaft (6), a first planetary gear set (10), a second planetary gear set (20) and a fixed component (31), wherein; The first planetary gear set (10) comprises a first sun gear (11), a first planet carrier (12), a first planetary gear (13) and a first ring gear (14), wherein: The first sun gear (11) is engaged with the first planetary gear (13), and the first planetary gear (13) is engaged with the first ring gear (14), The second planetary gear set (20) comprises a second sun gear (21), a second planet carrier (22), a second planetary gear (23) and a second ring gear (24), wherein the second sun gear (21) is engaged with the second planetary gear (23), and the second planetary gear (23) is engaged with the second ring gear (24). The first planet carrier (12) is connected to the first output shaft (5) via a torsion-resistant connection portion (30); The second ring gear (24) is connected to the second output shaft (6) in a rotationally fixed manner; The first ring gear (14) is connected to the second sun gear (21) in a rotationally fixed manner; The second planet carrier (22) is supported on the fixed component (31), The first planet carrier (12) is rotatably supported on the fixed component (31) via a support member (40), and The support element (40) of the first planet carrier (12) is arranged opposite to the rotationally fixed connection (30) in the axial direction relative to the first planetary gear (13).

2. The differential transmission (3) according to claim 1, characterized in that: The support element (40) of the first planet carrier (12) is supported on the cylindrical outer circumference of a section of the fixed component (31).

3. The differential transmission (3) according to claim 1, characterized in that: The support element (40) of the first planet carrier (12) is supported on the cylindrical inner circumference of a section of the fixed component (31).

4. The differential transmission (3) according to one of the preceding claims, characterized in that The first output shaft (5) is rotatably supported on the second output shaft (6) via a support member (45); wherein The support member (45) of the first output shaft (5) is arranged opposite to the support member (40) of the first planet carrier (12) in the axial direction relative to the first planetary gear (13).

5. The differential transmission (3) according to claim 4, characterized in that: The support member (45) of the first output shaft (5) is arranged between the first planet carrier (12) and the second output shaft (6).

6. The differential transmission (3) according to one of the preceding claims, characterized in that The second planetary gear set (20) is arranged to be offset in the axial direction relative to the first planetary gear set (10).

7. The differential transmission (3) according to claim 6, characterized in that: The second sun gear (21) is arranged inside the first ring gear (14) in a radial direction.

8. The differential transmission (3) according to one of claims 1 to 5, characterized in that A sun ring gear (32) is provided, wherein the first ring gear (14) is formed at the inner periphery and the second sun gear (21) is formed at the outer periphery. The first planetary gear set (10) and the second planetary gear set (20) overlap in the axial direction.

9. The differential transmission (3) according to one of the preceding claims, characterized in that An input element (4) is connected to the first sun gear (11) in a rotationally fixed manner and is rotatably supported on the fixed component (31) via a support (43).

10. The differential transmission (3) according to claim 9, characterized in that: The support element (40) of the first planet carrier (12) is arranged adjacent to the support element (43) of the input element (4) in the axial direction.

11. The differential transmission (3) according to claim 10, characterized in that: A fixing element (50) is used to axially fix the support member (40) of the first planet carrier (12), and the fixing element (50) is arranged between the support member (40) of the first planet carrier (12) and the support member (43) of the input element (4).

12. A drive unit (2) having a motor (73) and a differential transmission (3) according to one of the preceding claims, wherein The motor (73) is connected to the differential transmission (3) to drive the first sun gear (11).

13. A vehicle (1) having a drive unit (2) according to claim 12 and a drive wheel (70), wherein The drive unit (2) is installed in the vehicle (1) to drive the drive wheel (70).

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