Electronic drive unit

Abstract

Electronic drive unit (10), comprising: a shell casing (18) defining a hollow interior (20) extending along a primary axis (A1); a hollow shaft (28) which is arranged in the hollow interior (20) of the shell housing (18) and extends along the primary axis (A1); an electric motor (30) which is arranged in the hollow interior (20) of the shell housing (18) and radially surrounds a section of the hollow shaft (28); wherein the electric motor (30) is functionally connected to the hollow shaft (28) such that the hollow shaft (28) rotates about the primary axis (A1) in response to operation of the electric motor (30); at least one gear set (50, 60) which is arranged at a distance from the electric motor (30) along the primary axis (A1); wherein at least one gear set (50, 60) is in functional engagement with the hollow shaft (28) and is designed for rotation about the primary axis (A1); at least one output shaft (38, 40) which is arranged at least partially in the hollow interior (20) of the casing (18) and extends along the primary axis (A1); wherein the at least one output shaft (38, 40) is rotatably connected to the at least one gear set (50, 60) and is designed for rotation about the primary axis (A1); wherein at least one gear set (50, 60) is designed to rotate at least one output shaft (38, 40) about the primary axis (A1) at a rotational speed which is less than the rotational speed of the hollow shaft (28); wherein at least one gear set (50, 60) is at least one planetary gear set and wherein each of which comprises at least one planetary gear set: a ring gear (48A, 48B) which is arranged in the hollow interior (20) of the shell housing (18) and surrounds the primary axle (A1); a sun gear (46, 64) that radially surrounds and engages with the hollow shaft (28), such that the sun gear (46, 64) rotates about the primary axis (A1) in response to a rotation of the hollow shaft (28) about the primary axis (A1); at least one planetary wave (51) extending along a secondary axis (A2, A3) in a spaced and parallel relationship to the primary axis (A1); a planet carrier (52, 62) that radially surrounds the primary axis (A1) and is designed to rotate about it; wherein the planet carrier (52, 62) functionally connects each of the at least one planetary wave (51) and the at least one output wave (38, 40); at least one planet (54) which rotatably surrounds at least one planetary wave (51); wherein at least one planet (54) is in intermeshing engagement with each of the sun wheel (46, 64) and the ring wheel (48A, 48B); wherein the at least one planet (54) rotates about the respective secondary axis (A2, A3) in response to a rotation of the sun wheel (46, 64) about the primary axis (A1), such that the planetary support arrangement (55, 65) rotates about the primary axis (A1) due to the meshing engagement between the at least one planet (54) and the ring wheel (48A, 48B); and wherein the at least one planet (54) comprises: at least one inner planet (56) which is rotatable around at least one planetary shaft (51) about the secondary axis (A2, A3); and at least one outer planet (58) that radially surrounds and engages with a section of the inner planet (56); where at least one outer planet (58) is in combing engagement with the sun wheel (46, 64); where at least one inner planet (56) is in meshing engagement with the ring gear (48A, 48B).

Description

TECHNICAL AREA

[0001] The present invention relates to an electronic drive unit designed to drive at least one wheel of a vehicle. BACKGROUND OF THE INVENTION

[0002] A typical four-wheel-drive vehicle's drivetrain includes an engine, transmission, transfer case, front and rear drive shafts, and front and rear differentials. The transfer case is functionally connected to the transmission to direct power to the front and / or rear wheels. The front drive shaft functionally connects the transfer case to the front differential, and the rear drive shaft functionally connects the transfer case to the rear differential. The front differential drives the front wheels, and the rear differential drives the rear wheels. During certain driving conditions, the transfer case is engaged to direct power to only one of the rear wheels. In other driving conditions, i.e., in four-wheel drive mode, the transfer case is engaged to direct power to both the front and rear wheels.

[0003] From DE 603 ​​18 807 T2, an integrated drive motor unit is known, which is integrally constructed from a motor, a torque converter, and a reduction differential unit arranged in series, and a frame section. The reduction differential unit is connected to an output shaft of the motor and distributes the motor's torque to a pair of shafts, one of which passes through the torque converter. The frame section forms part of the motor and part of the reduction differential unit and has a section that surrounds the shaft passing through the torque converter. The torque converter is located outside the frame section.

[0004] From US Patent 5,718,302 A, a hydraulic circuit for the drivetrain of an electric car is known, comprising a motor, a torque transmission device for transmitting the motor's output torque to drive wheels, an oil pump for supplying oil from an oil reservoir, a drive device for rotating the oil pump, and an outlet circuit for receiving the oil discharged by the oil pump. A lubrication circuit is connected to the outlet circuit via a first restrictor to the torque transmission device. A cooling circuit is connected to the outlet circuit via a second restrictor and directs the oil flow to the motor.

[0005] The object of the present invention is to create an electronic drive unit that optimizes the propulsion of a vehicle as much as possible. This object is achieved by the subject matter of the independent patent claim. SUMMARY OF THE INVENTION

[0006] An electronic drive unit (EDU) comprises a casing that defines a hollow interior and extends along a primary axis. A hollow shaft is arranged within the hollow interior of the casing and extends along the primary axis. An electric motor is arranged within the hollow interior of the casing and radially surrounds a portion of the hollow shaft. The electric motor is functionally connected to the hollow shaft such that the hollow shaft rotates about the primary axis in response to operation of the electric motor. At least one gear set is arranged at a distance from the electric motor along the primary axis. The gear set is functionally meshed with the hollow shaft and is configured for rotation about the primary axis. At least one output shaft is arranged, at least partially, within the hollow interior of the casing and extends along the primary axis.The output shaft is rotatably connected to the gear set and designed for rotation about the primary axis. The gear set is designed to convert a rotation of the hollow shaft into a rotation of at least one output shaft about the primary axis at a rotational speed that is lower than the rotational speed of the hollow shaft.

[0007] The at least one gear set is at least one planetary gear set. This includes a ring gear located in the hollow interior of the casing and surrounding the primary shaft. A sun gear radially surrounds the hollow shaft and meshes with it, such that the sun gear rotates about the primary axis in response to a rotation of the hollow shaft. The at least one planetary gear set further includes at least one planetary shaft extending along a secondary axis spaced and parallel to the primary axis, and a planet carrier radially surrounding the primary axis and configured to rotate about it. The planet carrier functionally connects each of the at least one planetary shaft and the at least one output shaft.The at least one planetary gear set further comprises at least one planet rotatably surrounding the at least one planetary shaft and meshing with each of the sun gear and the ring gear. The at least one planet rotates about its respective secondary axis in response to a rotation of the sun gear about its primary axis, such that the planet carrier assembly rotates about its primary axis due to the meshing between the at least one planet and the ring gear.

[0008] The at least one planet comprises at least one inner planet, which is rotatable around the secondary axis via at least one planetary shaft, and at least one outer planet, which radially surrounds a section of the inner planet and meshes with it. The at least one outer planet meshes with the sun gear. The at least one inner planet meshes with the ring gear.

[0009] In another embodiment, an EDU comprises a casing and an electric motor. The casing defines a hollow interior. The electric motor comprises a stator and a rotor. The stator is arranged radially about a primary axis within the hollow interior of the casing. The rotor is radially surrounded by the stator within the hollow interior of the casing and is configured to rotate about the primary axis relative to the stator. A motor housing extends about the primary axis and surrounds the stator about the primary axis. A cooling cavity is defined between the motor housing and the casing and is configured such that a coolant flows through the cooling cavity to cool the electric motor. At least one seal is arranged between the casing and the motor housing. The casing defines at least one outlet that is open towards the at least one seal.The outlet is designed to allow any coolant that leaks at at least one seal to flow through it and out of the casing.

[0010] In yet another embodiment, an EDU comprises a shell housing that defines a hollow interior extending along a primary axis. A hollow shaft is arranged within the hollow interior of the shell housing and extends along the primary axis. An electric motor is arranged within the hollow interior of the shell housing and radially surrounds a section of the hollow shaft. The electric motor is functionally connected to the hollow shaft such that the hollow shaft rotates about the primary axis in response to operation of the electric motor. At least one gear set engages functionally with the hollow shaft and is configured for rotation about the primary axis. The gear set includes a planet carrier. A first output shaft and a second output shaft each extend along the primary axis in opposite directions.A differential assembly is rotatably arranged about the primary axis between the first output shaft and the second output shaft. The differential assembly is rotatably engaged with the planet carrier of the at least one gear set such that the differential assembly rotatably connects each of the at least one gear set and the output shafts. The gear set is configured to rotate the first output shaft and the second output shaft about the primary axis at a rotational speed lower than the rotational speed of the hollow shaft.

[0011] Therefore, the transfer case, front and rear differentials, and front or rear driveshaft can be replaced by the EDU. Replacing these components with the EDU saves cost, weight, and complexity. Additionally, the EDU can equalize rotational speed and / or torque between each of the rear wheels without using these components. Eliminating these components can improve fuel economy through weight reduction and by minimizing the losses associated with rotating these components to propel the vehicle. The EDU can also be used for regenerative braking.

[0012] The above features and advantages, and further features and advantages of the present invention, will become readily apparent from the following detailed description of the best embodiments of the invention when taken in conjunction with the accompanying drawings. BRIEF DESCRIPTION OF THE DRAWINGS

[0013] Now, with reference to the figures, which are exemplary embodiments and in which identical reference numerals are numbered the same, it is: Fig. 1 a schematic top view of a vehicle with a machine connecting a pair of front wheels and an electric drive unit (EDU) connecting a pair of rear wheels; Fig. 2 a schematic cross-sectional view from the side of an embodiment of the EDU of Fig. 1; Fig. 3 a schematic cross-sectional view from the side of another embodiment of the EDU of Fig. 1, which includes a sun gear pump for providing lubrication; Fig. 3A a cross-sectional view from the side, taken along line 3A-3A from Fig. 3, which shows the sun gear pump for providing lubrication; Fig. 4 a schematic cross-sectional view from the side of another embodiment of the EDU of Fig. 1, which includes a pump driven from the inlet for providing lubrication; Fig. 5 a schematic cross-sectional view from the side of another embodiment of the EDU of Fig. 1, which has an axis-displaced pump for providing lubrication; Fig. 6 a schematic cross-sectional view from the side of another embodiment of the EDU of Fig. 1; Fig. 7 a schematic cross-sectional view from the side of another embodiment of the EDU of Fig. 1, which includes a pump driven by an input for providing lubrication; Fig. 8 a schematic cross-sectional view from the side of another embodiment of the EDU of Fig. 1, which includes an axially offset pump for providing lubrication; and Fig. 9 a schematic cross-sectional view from the side of another embodiment of the EDU of Fig. 1, which has an axis-displaced pump to provide lubrication. DESCRIPTION OF PREFERRED EXECUTION FORMS

[0014] Referring to the drawings, in which the same reference numerals refer to the same components, shows Fig. 1. An electronic drive unit 10 (EDU). The EDU 10 can be used in conjunction with a machine 16 of a vehicle 15, such that the machine 16 drives the front wheels 12 of the vehicle 15 and the EDU 10 drives the rear wheels 14 of the vehicle 15. It should be noted that other embodiments of the EDU 10 can be used within the vehicle 15, as is known to those skilled in the art.

[0015] With reference to the Fig. 2 - 9 EDU 10 comprises a casing 18 that defines a hollow interior 20 extending along a primary axis A1. The casing 18 can include a jacket 22 and a jacket cover 24. The jacket cover 24 is detachably attached to the jacket 22 by means of fasteners 26 and the like. However, it should be noted that other embodiments of the casing 18 can also be used, as is known to those skilled in the art.

[0016] A hollow shaft 28 is arranged in the hollow interior 20 of the shell housing 18 and extends along the primary axis A1. An electric motor 30 is arranged in the hollow interior 20 of the shell housing 18 and radially surrounds a section of the hollow shaft 28. More precisely, the electric motor 30 can be arranged in the shell cover 24 of the shell housing 18. However, it should be noted that the electric motor 30 is not limited to being housed in the shell cover 24 of the shell housing 18. The electric motor 30 is functionally connected to the hollow shaft 28 such that the hollow shaft 28 rotates about the primary axis A1 in response to operation of the electric motor 30. More precisely, the electric motor 30 comprises a rotor 32 and a stator 34, which radially surrounds the rotor 32 about the primary axis A1. The rotor 32 surrounds a section of the hollow shaft 28 about the primary axis A1. The rotor 32 and the section of the hollow shaft 28 are rotatably engaged with each other, i.e.via a splined mesh and the like. The stator 34 is fixed to ground on the outer casing 18. When the rotor 32 rotates about the primary axis A1 relative to the stator 34, the rotor 32 causes the hollow shaft 28 to rotate about the primary axis A1.

[0017] Again with reference to Fig. 1. The EDU 10 can be functionally connected to a controller 36 in the vehicle 15. The controller 36 controls the operation of the electric motor 30 in the EDU 10 to selectively rotate the hollow shaft 28, i.e., via a rotation of the rotor 32, around the primary axis A1 and to drive one or more of the rear wheels 14 of the vehicle 15.

[0018] With reference to the Fig. 2 - 9, at least one output shaft 38, 40 is arranged at least partially within the hollow interior 20 of the shell housing 18 and extends along the primary axis A1. Each of the output shafts 38, 40 is configured to rotate about the primary axis A1. The output shaft 38, 40 can be a first output shaft 38 and a second output shaft 40, each extending along the primary axis A1 in opposite directions. Each output shaft 38, 40 is arranged at least partially within the hollow interior 20 of the shell housing 18. With reference to Fig. 1. The output shafts 38, 40 are designed for connection with an axle 44, which in turn is functionally connected to a respective rear wheel 14. Again with reference to the Fig. In section 2-9, the hollow shaft 28 defines a passage 42 that extends through it along the primary axis A1. The first output shaft 38 extends through the passage 42, so that the hollow shaft 28 surrounds the first output shaft 38.

[0019] With reference to the in the Fig. In embodiments 2-5, a first gear set 50 is arranged axially spaced along the primary axis A1 relative to the electric motor 30. The first gear set 50 is a planetary gear set with stepped planets, which is described in more detail below. The first gear set 50 comprises a sun gear 46, a ring gear 48A, and a first planet carrier assembly 55. Each planet carrier assembly 55 comprises a first planet carrier 52, several planets 54, and several bearings (not shown).

[0020] The sun gear 46 rotatably surrounds the hollow shaft 28. The sun gear 46 is rotatably engaged with the hollow shaft 28, for example, via a splined connection or the like, so that rotation of the hollow shaft 28 about the primary axis A1 causes the sun gear 46 to also rotate about the primary axis A1 together with the hollow shaft 28. The sun gear 46 is axially spaced from the electric motor 30 along the primary axis A1. The ring gear 48A is arranged in the hollow interior 20 of the outer casing 18 and is attached to the outer casing 18. The ring gear 48A is splined with the outer casing 18 and radially surrounds the primary axis A1.

[0021] The first planet carrier assembly 55 is arranged axially spaced along the primary axis A1 relative to the electric motor 30. The first planet carrier assembly 55 radially surrounds the primary axis A1 and the sun gear 46. The first planet carrier assembly 55 is in meshing engagement with the sun gear 46 and the ring gear 48A. As a result of the meshing engagement between the planet carrier assembly 55 and the ring gear 48A and the sun gear 46, the planets 54 are configured to rotate a respective secondary axis A2 relative to the ring gear 48A and the sun gear 46, which causes the first planet carrier assembly 55 to rotate about the primary axis A1.

[0022] The first gear set 50 can only be a planetary gear set 50, as is the case in the Fig. Figures 2-5 show that any number of gear sets 50 can be arranged at a distance from any other along the primary axis A1, such as a first and a second gear set 50, 60, as shown in the figures. Fig. The embodiments shown in Figures 6-9. In these embodiments, each gear set 50, 60 comprises a respective first and second planet carrier arrangement 55, 65. The gear sets 50, 60 in the Fig. 6 - 9 are functionally attached to one or more of the output shafts 38, 40 such that each gear set 50, 60 is designed to convert a rotation of the hollow shaft 28 about the primary axis A1 into a rotation of each of the output shafts 38, 40 about the primary axis A1 at a rotational speed that is less than the rotational speed of the hollow shaft 28, i.e. to provide a reduction in transmission or a gear reduction.

[0023] With reference to the Fig. 2 - 9 Each planetary carrier arrangement 55, 65 comprises several planetary shafts 51 extending along a corresponding secondary axis A2. The secondary axes A2 are radially spaced and parallel to the primary axis A1. As explained in more detail below, the planetary carrier arrangements 55, 65 of the Fig. 6-9 also tertiary axes A3, which are radially spaced and parallel to the primary axis A1. Each planet carrier assembly 55, 65 comprises respective first and second planet carriers 52, 62, which radially surround the primary axis A1 and are designed to rotate about it. A planet 54 surrounds the respective planet shaft 51 radially around the secondary axis A2 such that each of the planets 54 is rotatable about the respective planet shaft 51 when the respective planet carrier assembly 55, 65 rotates about the primary axis A1 relative to the sun gear 46 and the ring gear 48A.

[0024] Again with reference to the points in the Fig. In the embodiments shown in Figures 2-5, the planet 54 can be a stepped planet comprising an inner planet 56 and an outer planet 58. The outer planet 58 surrounds the inner planet 56 radially around the secondary axis A2 such that the outer planet 58 extends radially from the inner planet 56, thus providing a stepped planet 54. However, it should be noted that this configuration of the inner and outer planets 58 is not necessary to provide a stepped planet 54, as other configurations known to those skilled in the art can also be used. The inner planet 56 and the outer planet 58 each extend radially away from the secondary axis A2. The outer planet 58 meshes with the sun gear 46. Likewise, the inner planet 56 meshes with the ring gear 48A.The inner and outer planets 58 rotate together around the planetary shaft 51 and the secondary axis A2 relative to the sun gear 46 and the ring gear 48A in response to a rotation of the sun gear 46 around the primary axis A1. This means that when the inner planet 56 rotates around the secondary axis A2 and meshes with the ring gear 48A, the entire planet carrier assembly 55 rotates around the primary axis A1 relative to the sun gear 46 and the ring gear 48A.

[0025] The alternatives in the Fig. The embodiments shown in Figures 6-9 comprise the first gear set 50 and the second gear set 60. In this embodiment, the second gear set 60 is axially spaced from the first gear set 50 along the primary axis A1. In this embodiment, the sun gear 46 surrounding the hollow shaft 28 is a first sun gear 46. The second gear set 60 comprises the second sun gear 64, a ring gear 48B, and the second planet carrier assembly 65. The second planet carrier assembly 65 comprises the second planet carrier 62, several planets 54, and bearings (not shown). A second sun gear 64 of the second gear set 60 extends from the first planet carrier 52 of the first gear set 50. This means that the second sun gear 64 rotates about the primary axis A1 together with the first planet carrier 52. Then, a rotation of the first planet carrier 52 around the first axis A1 drives the second planet carrier arrangement 65.The second planet carrier assembly 65 radially surrounds the primary axis A1 at an axial distance from the first gear set 50. As mentioned above, the first planet carrier 52 of the first planet carrier assembly 55 is rotatably engaged with the second sun gear 64 of the second gear set 60. Likewise, the second planet carrier 62 of the second planet carrier assembly 65 of the second gear set 60 is rotatably functionally connected to at least one of the output shafts 38, 40.

[0026] The planets 54 of each planetary carrier arrangement 55, 65 in the Fig. 6 - 9 are in meshing engagement with the respective ring gear 48A, 48B and sun gear 46, 64. The planets 54 of the first planet carrier arrangement 50 are rotatable about the respective secondary axis A2 relative to the first sun gear 46 and the respective ring gear 48A. When the hollow shaft 28 and the first sun gear 46 rotate together around the primary axis A1 in response to a rotation of the rotor 32, the planets 54 of the first planet carrier assembly 50 therefore rotate around their respective secondary axis A2 relative to the first sun gear 46 via the meshing engagement between the planets 54 of the first planet carrier assembly 55 and the first sun gear 46. Due to the meshing between the planets 54 of the first planet carrier assembly 55 and the respective sun gear 46 and the ring gear 48A, the first planet carrier assembly 55 rotates equally around the primary axis A1 relative to the respective sun gear 46 and ring gear 48B.As discussed above, the first planet carrier assembly 55 is connected to the second sun gear 64 such that when the first planet carrier 52 of the first planet carrier assembly 55 rotates about the primary axis A1, the second sun gear 64 also rotates about the primary axis A1. When the second sun gear 64 rotates about the primary axis A1 with the first planet carrier assembly 55, the planets 54 of the second planet carrier assembly 65 rotate about their respective tertiary axes A3 relative to the second sun gear 64 and the respective ring gear 48B via a meshing engagement between the planets 54 of the second planet carrier assembly 65 and the second sun gear 64. The tertiary axes A3 each extend radially spaced and parallel to the primary axis A1.When the second planet carrier assembly 65 rotates about the primary axis A1, the second planet carrier 62 also rotates about the primary axis A1, causing at least one of the output shafts 38, 40 to also rotate about the primary axis A1. The planets 54 of each planet carrier assembly 55, 65, the ring gears 48A, 48B, and the sun gears 46, 64 are dimensioned and designed such that a desired reduction in gear ratio is provided, so that the rotational speed of the output shafts 38, 40 is lower than the rotational speed of the hollow shaft 28.

[0027] With reference to the Fig. 2 - 9 A differential assembly 66 is rotatably arranged about the primary axis A1 between the first output shaft 38 and the second output shaft 40. The differential assembly 66 functionally connects the first sun gear 46 or the second sun gear 64 of the respective gear set 50, 60 and each of the output shafts 38, 40. Therefore, the differential assembly 66 and each of the output shafts 38, 40 rotate together about the primary axis A1 in response to the hollow shaft 28 rotating about the primary axis A1. The differential assembly 66 includes a gear housing 68. With reference to the Fig. 2 - 5 the first planet carrier 52 extends from the gear housing 68. With reference to the Fig. The second planet carrier 62 extends from the gear housing 68 at points 6-9. The gear housing 68 rotatably supports each of the output shafts 38, 40 along the primary axis A1. Several differential gears 70 are arranged in the gear housing 68 in meshing relation with each of the output shafts 38, 40. The differential gears 70 are of a type known to those skilled in the art, such that the first output shaft 38 is allowed to rotate relative to the second output shaft 40 when a torque difference exists between the output shafts 38, 40. With reference to the Fig. Figures 1-3 and 4-9 are two differential gears 70 arranged on the primary axis A1, with splined connections to the two output shafts 38, 40 to drive the output shafts 38, 40. Although four differential gears 70 are shown in the figures, there could actually be six differential gears 70, i.e., two differential gears on one axis (not shown) perpendicular to the primary axis A1.

[0028] The operation of the electric motor 30 in the casing 18 can generate heat. Referring to the Fig. In the embodiment 2-9, a cooling jacket 72 can be provided to dissipate heat from the electric motor 30, surrounding the electric motor 30. The cooling jacket 72 comprises a motor housing 74, which is arranged between the electric motor 30 and the jacket cover 24. The motor housing 74 extends around the primary axis A1 and surrounds the electric motor 30. A cooling cavity 76 is defined between the motor housing 74 and the jacket cover 24 of the jacket housing 18 and is configured such that a coolant flows through the cooling cavity 76 to dissipate heat and cool the motor housing 74. The coolant can be water. However, it should be noted that the coolant can also be any other fluid known to those skilled in the art for dissipating heat. The cooling cavity 76 can be wound around the outer circumference of the motor housing 74. In the embodiments shown, the cooling cavity 76 has a helical shape.However, it can be stated that the shape of the cooling cavity 76 can be any suitable shape for dissipating heat from the electric motor 30. The jacket housing 18 can also include a port 78 that opens to the cooling cavity 76. More precisely, at least two ports 78 that are open to the cooling cavity 76. Each port 78 is in fluid communication with the cooling cavity 76 such that the ports 78 can supply coolant to and / or remove it from the cooling cavity 76. At least one seal 80 can be arranged between the motor housing 74 and the jacket housing 18. The seal 80 is designed to prevent coolant from leaking out of the cooling cavity 76 to the electric motor 30. To further prevent coolant from leaking to the electric motor 30, the jacket 22 can also define at least one outlet 82 that is open to the seal 80.The outlet 82 is designed to allow any coolant passing over the seal 80 to flow through the jacket housing 18 and out, i.e. away from the electric motor 30.

[0029] With reference to the Fig. 3-5 and 7-9, the EDU 10 can comprise a sump 84 and at least one pump 86 to provide lubrication for the gear set(s) 50, 60, the differential assembly 66, the output shafts 38, 40, the hollow shaft 28, etc. The sump 84 is arranged in the shell housing 18 and is configured to hold a volume of fluid. The fluid can be oil. However, it should be noted that any other fluid known to those skilled in the art can also be used. The pump 86 is in fluid communication with the sump 84 and is configured to draw a quantity of the fluid from the sump 84 and supply the quantity of the fluid to the gear set(s) 50, 60, the differential assembly 66, the output shafts 38, 40, and / or the hollow shaft 28. In an embodiment described in the Fig. 3, Fig. 4 and Fig. As shown in Figure 7, the pump 86 is arranged on the primary axis A1 and designed to rotate about it. The pump 86 can be a sun gear pump 88, as shown in the Fig. 3 and Fig. Figure 3A shows, for example, an internal gear pump comprising an inner ring 90 and an outer ring 92. The inner ring 90 extends around the primary axis A1 and is rotatable about the primary axis A1 relative to the casing 18. The outer ring 92 surrounds the inner ring 90 around the primary axis A1 and is rotatable about the primary axis A1. The outer ring 92 can be in meshing engagement with at least one of the planetary carrier assemblies 55, 65, e.g., the planet 54, such that the operation of the planetary carrier assembly 55, 65 rotates the inner ring 90 and the outer ring 92 about the primary axis A1. The inner ring 90 is held off-center from the primary axis A1 by a feature on the casing 18. The outer ring 92 is held at the center of the primary axis A1 by another feature on the casing 18.Oil enters the suction side of the sun gear pump 88 at its underside and is pressurized when the two rings 90, 92 of the pump rotate together. At the top of the sun gear pump 88, the oil reaches its maximum pressure and is discharged to lubricate at least one of the gear set(s) 50, 60, the differential assembly 66, the output shaft(s) 38, 40, and / or the hollow shaft 28. More precisely, the outer ring 92 meshes with each of the inner planets 56. Although there are only two inner planets 56 in . Fig. As shown in Figure 3, it can be observed that typically several inner planets 56 surround the outer ring 92, such as three or four inner planets 56. Therefore, when the inner planet 56 rotates around its respective secondary axis A2, the planets 56 surrounding the outer ring 92 rotate around its primary axis A1. Referring to the Fig. 4 and Fig. 7. The pump 86 can be an input-driven pump 88A. The input-driven pump 88A comprises the inner ring 90 and the outer ring 92. The inner ring 90 engages in a splined mesh with the hollow shaft 28. Rotation of the hollow shaft 28 rotates the inner ring 90 to draw the fluid from the sump 84 and thus lubricate the gear set(s) 50, 60, the differential assembly 66, the outer shaft(s) 38, 40 and / or the hollow shaft 28.

[0030] In another embodiment, which is in the Fig. 5, Fig. 8 and Fig. As shown in Figure 9, the pump 86 is arranged on a lubrication axis A4 in a radially spaced and generally parallel relationship to the primary axis A1. In this embodiment, the pump 86 is configured to draw a quantity of fluid from the sump 84 and supply that quantity of fluid to the gear set(s) 50, 60. The pump 86 can be an offset pump or a positive displacement pump unit 96, such as an internal gear pump. This type of pump 86 comprises an inner rotor 98 and an outer rotor 100 extending around the lubrication axis A4. The inner rotor 98 has several teeth (not shown), and the outer rotor 100 has one more tooth (not shown) than the inner rotor 98. The inner rotor 98 is arranged off-center, and both rotors rotate. During part of the rotation cycle of the arrangement, an area between the inner rotor 98 and the outer rotor 100 increases, creating a negative pressure between them.This negative pressure creates a suction effect, and thus this part of the cycle takes place where the inlet is located. Subsequently, the area between the rotors decreases, causing compression. During this compression period, fluid can be pumped or compressed. However, it should be noted that the pump 86 is not limited to being a positive displacement pump unit 96, as any other pump 86 known to experts can also be used.

[0031] With reference to the Fig.2 - 5 The lubrication for the differential assembly 66, the gear set(s) 50, 60, the output shafts 38, 40 and / or the hollow shaft 28 can also be provided by rotating the differential assembly 66 about the primary axis A1. In this embodiment, the differential assembly 66 can also include a centrifugal plate 102 that substantially surrounds the gear housing 68 of the differential assembly 66. The centrifugal plate 102 can be configured to rotate about the primary axis A1 together with the differential assembly 66. The centrifugal plate 102 is designed to capture or collect a lubricant from the interior of the hollow interior 20 of the shell housing 18 and to direct the lubricant into the gear set(s) 50, 60, the first output shaft 38, the second output shaft 40, the hollow shaft 28 and / or the differential assembly 66.

[0032] Although the best embodiments of the invention have been described in detail, those skilled in the field relating to this invention will recognize various alternative designs and embodiments for the practical implementation of the invention within the scope of protection of the attached claims.

Claims

[1] Electronic drive unit (10), comprising: a shell casing (18) defining a hollow interior (20) extending along a primary axis (A1); a hollow shaft (28) which is arranged in the hollow interior (20) of the shell housing (18) and extends along the primary axis (A1); an electric motor (30) which is arranged in the hollow interior (20) of the shell housing (18) and radially surrounds a section of the hollow shaft (28); wherein the electric motor (30) is functionally connected to the hollow shaft (28) such that the hollow shaft (28) rotates about the primary axis (A1) in response to operation of the electric motor (30); at least one gear set (50, 60) which is arranged at a distance from the electric motor (30) along the primary axis (A1); wherein at least one gear set (50, 60) is in functional engagement with the hollow shaft (28) and is designed for rotation about the primary axis (A1); at least one output shaft (38, 40) which is arranged at least partially in the hollow interior (20) of the casing (18) and extends along the primary axis (A1); wherein the at least one output shaft (38, 40) is rotatably connected to the at least one gear set (50, 60) and is designed for rotation about the primary axis (A1); wherein at least one gear set (50, 60) is designed to rotate at least one output shaft (38, 40) about the primary axis (A1) at a rotational speed which is less than the rotational speed of the hollow shaft (28); wherein at least one gear set (50, 60) is at least one planetary gear set and wherein each of which comprises at least one planetary gear set: a ring gear (48A, 48B) which is arranged in the hollow interior (20) of the shell housing (18) and surrounds the primary axle (A1); a sun gear (46, 64) that radially surrounds and engages with the hollow shaft (28), such that the sun gear (46, 64) rotates about the primary axis (A1) in response to a rotation of the hollow shaft (28) about the primary axis (A1); at least one planetary wave (51) extending along a secondary axis (A2, A3) in a spaced and parallel relationship to the primary axis (A1); a planet carrier (52, 62) that radially surrounds the primary axis (A1) and is designed to rotate about it; wherein the planet carrier (52, 62) functionally connects each of the at least one planetary wave (51) and the at least one output wave (38, 40); at least one planet (54) which rotatably surrounds at least one planetary wave (51); wherein at least one planet (54) is in intermeshing engagement with each of the sun wheel (46, 64) and the ring wheel (48A, 48B); wherein the at least one planet (54) rotates about the respective secondary axis (A2, A3) in response to a rotation of the sun wheel (46, 64) about the primary axis (A1), such that the planetary support arrangement (55, 65) rotates about the primary axis (A1) due to the meshing engagement between the at least one planet (54) and the ring wheel (48A, 48B); and wherein the at least one planet (54) comprises: at least one inner planet (56) which is rotatable around at least one planetary shaft (51) about the secondary axis (A2, A3); and at least one outer planet (58) that radially surrounds and engages with a section of the inner planet (56); where at least one outer planet (58) is in combing engagement with the sun wheel (46, 64); where at least one inner planet (56) is in meshing engagement with the ring gear (48A, 48B). [2] Electronic drive unit (10) according to claim 1, further comprising: a sump (84) designed to hold a volume of fluid; at least one pump (86) in fluid connection with the sump (84); wherein the at least one pump (86) is designed to draw off a quantity of fluid from the sump (84) and to supply the quantity of fluid to the at least one gear set (50, 60). [3] Electronic drive unit (10) according to claim 2, wherein the at least one pump (86) is arranged on the primary axis (A1) and is designed to rotate about it. [4] Electronic drive unit (10) according to claim 3, comprising at least one pump (86): an inner ring (90) extending around the primary axis (A1); an outer ring (92) that surrounds the inner ring (90) around the primary axis (A1); wherein the outer ring (92) is centered around the primary axis (A1); wherein the inner ring (90) is off-center from the primary axis (A1); wherein the inner ring (90) and the outer ring (92) are rotatable together about the primary axis (A1); wherein the outer ring (92) is in meshing engagement with the at least one inner planet (56), such that a rotation of the at least one inner planet (56) rotates the at least one pump (86) to draw a quantity of fluid from the sump (84) into the at least one pump (86) in order to pressurize and discharge the quantity of fluid from the at least one pump (86) and thus supply the quantity of fluid to the at least one gear set (50, 60), the at least one output shaft (38, 40) and / or the hollow shaft (28). [5] Electronic drive unit (10) according to claim 2, wherein the at least one pump (86) is arranged and configured on a lubrication shaft (A4) in a spaced-apart and generally parallel relationship to the primary shaft (A1) to draw off an amount of fluid from the sump (84) and supply the amount of fluid to the at least one gear set (50, 60). [6] Electronic drive unit (10) according to claim 1, wherein the planetary gear set is a first planetary gear set and a second planetary gear set axially spaced from the first planetary gear set along the primary axis (A1); wherein the planet carrier (52, 62) of the first planetary gear set is rotatably engaged with the sun gear (46, 64) of the second planetary gear set. [7] Electronic drive unit (10) according to claim 1, wherein the at least one output shaft (38, 40) is a first output shaft (38) and a second output shaft (40) which each extend along the primary axis (A1) in opposite directions; wherein the first output shaft (38) and the second output shaft (40) are rotatably connected to the at least one gear set (50, 60) and are designed to rotate about the primary axis (A1); wherein at least one gear set (50, 60) is designed to convert a rotation of the hollow shaft (28) into a rotation of the first output shaft (38) and the second output shaft (40) about the primary axis (A1).

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