Electric drive module with shifting system; electric drive train

Abstract

The invention relates to an electric drive module (1) for a motor vehicle, having an electric machine (2), a planetary transmission (5) which can be operated via two different transmission stages (3, 4), wherein a sun gear (7) which serves as an input (6) of the planetary transmission (5) is connected in a torque-transmitting manner to a rotor shaft (8) of the electric machine (2), and having a shifting system (9) for shifting between the two transmission stages (3, 4), wherein the shifting system (9) is configured in such a way that, in order to adjust the transmission stage (3, 4), it axially displaces a planetary carrier (10) of the planetary transmission (5) between at least two different positions and thus changes a torque transmission path. The invention also relates to an electric drive train (26) for a motor vehicle, comprising an electric drive module (1) according to one of the preceding claims and a transmission (54) connected downstream of the drive module (1).

Description

[0001] Electric drive module with switching system; Electric drive train

[0002] The invention relates to an electric drive module for a motor vehicle, preferably a truck, with an electric machine and a switchable planetary gear unit that can be operated via two different gear ratios.

[0003] The use of a multi-gear drivetrain is particularly relevant for electric commercial vehicles. In especially heavy-duty truck e-axles, a total of two motors are used per axle. Currently, it is generally possible to implement the drivetrain without a clutch, as the electric motors are able to release torque during gear changes. With currently used...

[0004] However, with transmissions / transmission structures, the problem is that no torque can be transmitted during the shifting process, so that in this state the vehicle is not driven.

[0005] The object of the present invention is to provide an electric drive module which ensures a simplified switching system while continuing load transmission.

[0006] This is achieved in the present electric drive module by connecting a sun gear, serving as the input to the planetary gear, to a rotor shaft of the electric machine in a torque-transmitting manner, and by designing an output of the planetary gear as a ring gear. A switching system is used to change between the two gear ratios. This switching system is designed to axially displace a planet carrier of the planetary gear between at least two different positions, thereby altering / switching a torque transmission path. The axial displacement allows for two axial directions of movement: a first and a second direction. The switching system enables a space-saving design, as the planet carrier is axially displaceable.Overall, with the present embodiment, the switching system of the transmission stages has been relocated to the electric machine. Advantageous embodiments are claimed in the dependent claims and are explained in more detail below.

[0007] It is advantageous if the switching system is designed and the planet carrier is mounted in such a way that, in a first gear stage, in its first position, the planet carrier is held against a support area fixed to the housing during operation (e.g., the housing of the electric machine and / or a gearbox). Preferably, the planet carrier and the housing-fixed support area together form a positive-locking connection. For this purpose, the planet carrier can have a positive-locking contour and the support area a positive-locking counter-contour. This allows the planet carrier to be preferably held rotationally fixed in the first gear stage. A first torque transmission path can then run from the rotating sun gear to the planet gears meshing with and rotating with the sun gear, and subsequently to the ring gear meshing with the rotating planet gears.The first gear ratio of this first gear stage can thus be derived from the quotient of the number of teeth on the sun gear and the number of teeth on the ring gear. The first gear ratio is preferably less than one.

[0008] Furthermore, the switching system can be designed and the planet carrier mounted in such a way that, in a second transmission stage, its second position, the planet carrier is rotationally fixed to the sun gear by means of an internal toothing. Preferably, the planet carrier is designed as a hollow body. An internal toothing can be formed on the inside of an axial section. This results in a particularly space-saving variant. A second torque transmission path can be transferred directly from the sun gear to the ring gear via the planet gears. Due to the rotationally fixed connection between the sun gear and the planet carrier, the planet gears are locked. A second transmission ratio of this second transmission stage thus results from the locked planetary gear set. The first transmission ratio is preferably one.

[0009] It is advantageous if the switching system is designed and the planet carrier is oriented such that the planet carrier is in a free position in a third position. In this position, the planet carrier can be decoupled from the support area and the sun gear. The electric motor is thus decoupled from the planetary gear set. Preferably, the third position is formed axially between the first and second positions.

[0010] The first direction of movement describes an axial displacement from the first position to the second position, and the second direction of movement describes an axial displacement from the second position to the first position.

[0011] Preferably, the two transmission stages transmit torque in the same direction. Furthermore, the electric drive module can have a third and fourth transmission stage, which are implemented by reversing the direction of rotation of the first and second transmission stages, respectively. This allows the first and second transmission stages to be used for one direction of rotation of a forward gear, and the third and fourth transmission stages to be used for one direction of rotation of two reverse gears. The direction of rotation can be reversed between the first and third transmission stages, as well as between the second and fourth transmission stages. Thus, the electric drive module can switch between a total of four transmission stages or four gears.

[0012] It is advantageous if the switching system comprises a first switching element and a second switching element linked to the first via a sliding mechanism, whereby the sliding mechanism can be actuated by means of a brake to force the various positions. Actuating with the brake allows a relative circumferential rotation from the first switching element to the second, resulting in an axial displacement of the first switching element relative to the second. Due to the braking action, the rotational speed of the second switching element is lower than that of the first. In other words, the rotational rate of the second switching element is reduced, and the second switching element can rotate more slowly. Furthermore, the switching system allows switching between the three positions described above.Preferably, the displacement mechanism is designed such that the first switching element can move in both directions of rotation (comparable to a switching drum). Preferably, the first switching element is connected to the planet carrier so that the previously described displacement of the planet carrier is possible.

[0013] It is advantageous if the brake is a magnetic brake. The magnetic brake can generate a braking torque designed to decelerate the second switching element. Preferably, the second switching element comprises a material that reacts to a magnetic field, so that the second switching element can be magnetically actuated.

[0014] It is advantageous for the shifting mechanism to have a ramp system with rollers formed on the first and second switching elements. The previously described rotation relative to each other can be achieved using the ramp system with the rollers, preferably balls. This is a particularly space-saving solution.

[0015] It is advantageous if the ramp system has ramp contours on both the first and second switching elements, which extend at least partially circumferentially. Preferably, the first switching element has a continuous, circumferentially extending, sectionally rising and sectionally falling first ramp contour. Particularly preferably, the first ramp contour is formed in a radially inner region of the first switching element. Preferably, the second switching element has a second ramp contour extending sectionally circumferentially, rising and falling. Particularly preferably, the second ramp contour is formed in a radially outer region. The second switching element can have a plurality, preferably three, of second ramp contours formed circumferentially (section by section).

[0016] Furthermore, the switching system can include a holding mechanism for maintaining at least one position of the first switching element relative to the second switching element. The holding mechanism is designed to allow the first switching element to be held in a holding position relative to the second switching element, even without a braking torque. Preferably, a plurality of holding positions, in particular two holding positions, can be implemented using the holding mechanism. A first holding position describes the second position described above. A second holding position describes the third position described above. In other words, the position in the second position can be held without a braking torque.

[0017] It is advantageous if the first switching element and the second switching element have retaining contours. Preferably, the retaining contours are axially extending recesses. Particularly preferably, the retaining contours on the first switching element are formed in the ramp contour and / or the retaining contours on the second switching element are arranged circumferentially between the second ramp contours.

[0018] It is advantageous if the number of rolling devices is three.

[0019] Preferably, the first switching element is connected to the ring gear (non-rotatably) and / or is coupled axially to the planet carrier. With axial coupling to the planet carrier, the first switching element can provide axial displacement of the planet carrier in both directions of movement. Preferably, the switching element can be coupled to the planet carrier by means of a bearing. This allows for rotational decoupling. The energy for adjusting the first switching element relative to the second switching element can be converted via the connection between the first switching element and the ring gear.

[0020] It is advantageous if the first switching element is pre-tensioned in at least one of its two positions by means of a spring mechanism. Due to the different rotational rates / velocities of the first and second switching elements relative to each other, the rotation of the first switching element relative to the second creates a pre-tension on the spring mechanism. This pre-tension allows the first switching element to be moved axially in the second direction of movement when the magnetic brake is deactivated, i.e., without the application of braking torque. Preferably, the spring mechanism comprises at least one, and preferably three, springs, in particular leaf springs. The previously described connection between the ring gear and the first switching element is preferably achieved by means of these springs.

[0021] Preferably, the first and second switching elements are designed in a ring shape and arranged coaxially to each other. The first switching element can be designed as an outer ring and the second switching element as an inner ring. This results in a space-saving design of the switching system.

[0022] In one embodiment, a synchronization device may be provided which generates a synchronization torque for adjusting the rotational speed of the planet gears (relative to the sun gear). The synchronization device may include a spring, preferably a pre-tensioned one, in particular a ring spring. A pre-tensioned spring has the advantage that its amplitude (tension stroke) is smaller compared to a non-pre-tensioned spring. Another advantage is that a high torque is available for synchronization as soon as the planet carrier is freely rotatable. Preferably, the spring is positioned axially between the ring gear and the planet gears mounted on the planet carrier, and the spring is designed to generate a synchronization torque for adjusting the rotational speed of the planets (relative to the sun gear). The second position described above is reached more quickly with the aid of the synchronization torque.The axial displacement of the planet carrier allows the spring to be supported by the ring gear and the planet gears. This allows the planet carrier to be braked against the ring gear, and the planet gears on the planet carrier can also be braked. This allows the rotational speed of the planet carrier to be adjusted to the rotational speed of the sun gear. This promotes the meshing of the internal teeth of the planet carrier with the sun gear.

[0023] The invention also relates to an electric drivetrain for a motor vehicle, preferably a truck, comprising a previously described electric drive module and a transmission downstream of the drive module. It is advantageous if two previously described drive modules are arranged upstream of the transmission in the drivetrain. Preferably, the two electric drive modules engage a common gear in the electric drivetrain. This offers the advantage that the respective electric motors of the two electric drive modules can have different gear ratios. This results in higher efficiency. Furthermore, the different gear ratios allow the electric drive modules to be switched at different times. This, in turn, enables load replenishment during the period when the gear ratio change is being applied to the other electric drive module.Furthermore, each motor can be decoupled separately from the electric drivetrain.

[0024] In other words, the invention relates to an electric drive module with a simple two-speed transmission system for a motor vehicle, preferably a truck. The drive module comprises an electric motor and a planetary gear set, wherein the input of the planetary gear set is via a sun gear and the output is via a ring gear. A planet carrier is axially displaceable for the transmission.

[0025] In the first position, the planet carrier can be engaged with a housing. In this position, the gear ratio is less than one. In the second position, the planet carrier can be disengaged from the housing. No torque is transmitted. In the third position, the planet carrier can be engaged with the sun gear. The gear ratio is one.

[0026] It is advantageous if the axial displacement of the planet carrier can be achieved via a ramp system / ramp between a first component / switching element and a second component / switching element. Preferably, the first component is rotationally fixed to the ring gear by means of leaf springs and / or axially coupled to the planet carrier. The second component can be braked using a magnetic brake. In other words, the second component can be braked. This braking action allows for adjustment of the ramp system. It is advantageous if the ramp system has pockets. Preferably, balls can be arranged in these pockets. The first component is axially displaced by the balls in the pockets. The leaf springs allow the first component to be pushed back in the absence of a locking mechanism or magnetic brake.

[0027] Several advantageous embodiments of the invention are explained in more detail below with reference to a drawing with figures.

[0028] They show:

[0029] Fig. 1 shows an electric drive module according to the invention in a first embodiment,

[0030] Fig. 2 shows the electrical drive module according to the invention as shown in Fig. 1 and a first switching element and second switching element in a first rotational position,

[0031] Fig. 3 shows the electrical drive module according to the invention as shown in Fig. 1 and the first switching element and the second switching element in a second rotational position,

[0032] Fig. 4 shows the electrical drive module according to the invention as shown in Fig. 1 and the first switching element and the second switching element in a third rotational position,

[0033] Fig. 5 shows the electrical drive module according to the invention as shown in Fig. 1 and the first switching element and the second switching element in a fourth rotational position,

[0034] Fig. 6 shows an electric drive module according to the invention in a second embodiment, Fig. 7 shows the electric drive module according to the invention according to Fig. 6 and the first switching element and second switching element in the first rotational position,

[0035] Fig. 8 shows the electrical drive module according to the invention as shown in Fig. 6 and the first switching element and the second switching element in the second rotational position.

[0036] Fig. 9 shows the electrical drive module according to the invention as shown in Fig. 6 and the first switching element and the second switching element in the third rotational position.

[0037] Fig. 10 shows the electrical drive module according to the invention as shown in Fig. 6 and the first switching element and the second switching element in the fourth rotational position,

[0038] Fig. 11 shows the electrical drive module according to the invention as shown in Fig. 6 and the first switching element and the second switching element in a fifth rotational position,

[0039] Fig. 12 shows a front view of the planetary gear with the different gear ratio stages,

[0040] Fig. 13 shows an electric drive train with an electric drive module in various embodiments.

[0041] The figures are purely schematic and serve solely to illustrate the invention. Identical elements are identified by the same reference numerals. Features of the individual embodiments are interchangeable and can be used alternatively or cumulatively.

[0042] Fig. 1 shows an electric drive module 1 according to the invention for a motor vehicle, preferably a truck, comprising an electric motor 2 and a switchable planetary gear 5 operable via two different gear ratios 3 and 4. A sun gear 7, serving as the input 6 of the planetary gear 5, is connected to a rotor shaft 8 of the electric motor 2 in a torque-transmitting manner and is connected to a switching system 9 for switching between the two gear ratios 3 and 4. The switching system 9 is designed such that, to adjust the gear ratio 3 and 4, it axially displaces a planet carrier 10 of the planetary gear 5 between two different positions, thereby changing a torque transmission path. An output 11 of the planetary gear 5 is designed as a ring gear 12.

[0043] Fig. 1 shows the inventive electric drive module 1 in a first embodiment in a first position in a sectional view.

[0044] The basic structure of the electric drive module 1 is explained with reference to Fig. 1. Various rotational positions of the switching system 9 are shown with reference to Figs. 2 to 5. Some components and parts are only recognizable in these rotational positions. Please refer to Figs. 2 to 5 for further details.

[0045] For clarity, an axial direction 13, a radial direction 14, and a circumferential direction 15 are defined. The axial direction 13 extends in the direction of a central axis 16, which is also an axis of rotation of the rotor shaft 8 of the electric machine 2. The radial direction 14 is perpendicular to the axial direction 13. The circumferential direction 15 extends in a direction of rotation about the central axis 16 of the rotor shaft 8.

[0046] In the first embodiment shown in Fig. 1, the electric drive module 1 is depicted in a first position. A first transmission stage 3 is shown in engagement. In this case, the sun gear 7 is axially connected to the rotor shaft 8 at its end, in a region far from the housing (of a housing 27a of the electric machine 2), transmitting torque. The sun gear 7 is axially secured on both sides by means of a retaining ring 17, 18. The planet carrier 10 is a hollow body and has a section with internal teeth 45 at its axial end. An axial projection in the form of a hollow sleeve 19 is formed / shaped on the rotor shaft at the beginning of the rotor shaft 8, in a region near the housing (of the housing 27a of the electric machine 2). The planet carrier 10 is positioned radially to the sleeve 19 and extends at least in the axial direction 13 along a section of the rotor shaft 8.A first bearing 67 is arranged radially between the planet carrier 10 and the sleeve 19.

[0047] At its initial axial end, the planet carrier is held against a housing-fixed support area 28. A positive locking connection 29 is formed between the sleeve 19 and the planet carrier 10.

[0048] Planet gears 20 are rotatably arranged axially at the ends of the planet carrier 10. The planet gears 20 mesh with the sun gear 7. Two planet gears 20 are visible in the sectional view shown. The planetary gear set 5 has a plurality of planet gears 20 spaced uniformly apart from each other in the circumferential direction 15. In the present embodiment, there are three planet gears 20 (see Fig. 12). The planet gears 20 mesh with the ring gear 12. Thus, the torque path runs via the sun gear 7 to the planet gears 20, which transmit the torque to the ring gear 12.

[0049] The ring gear 12 is axially torque-resistant at its end to a flange 21 of a hollow shaft 22 by means of axial fasteners, in this case a plurality of screws 23 spaced apart from each other in the circumferential direction 15. The hollow shaft 22 is arranged axially at the end of the rotor shaft 8. An external toothing 25 is formed on a flange-free outer surface 24 of the hollow shaft 22, which is prepared to be connected to further components of an electric drive train 26 via a further transmission stage to transmit torque.

[0050] The switching system 9 is arranged in the axial direction 13 between the ring gear 12 and the housing 27a. The switching system 9 comprises a first switching element 30 and a second switching element 31, as well as a brake 32, in this case designed as a magnetic brake. The first switching element 30 is formed in the form of an outer ring, and the second switching element 31 is formed in the form of an inner ring. On the side of the ring gear 12 facing away from the flange 21, the first switching element 30 is connected to the ring gear 12 by means of a spring mechanism in a frictional and torque-locking manner. The first switching element 30 has tabs 33 on its radial outer side, each with axial through holes 34. The first switching element 30 is connected to the ring gear 12 by means of screws 64 via a leaf spring 36 per tab 33 using rivets 35 (see Figs. 2a and 2b).

[0051] The two switching elements 30, 31 are coupled to each other via a sliding mechanism and a holding mechanism. For the sliding mechanism, the first switching element 30 and the second switching element 31 each have a ramp system 37, which is formed by ramp contours 39, 40 in the first switching element 30 and the second switching element 31, respectively, and includes rolling elements 41. The first switching element 30 has a radially internal, ascending and descending first ramp contour 39 extending in the circumferential direction 15 and formed in the axial direction 13. The second switching element 31 has segmentally extending second ramp contours 40 extending in the circumferential direction 15. The first switching element 30 and the second switching element 31 are positioned coaxially to each other. The second switching element 31 is positioned in the inner, radially free area of ​​the first switching element 30.

[0052] In the ramp contours 39, 40, rolling elements, in this case in the form of spheres, are arranged. A total of three rolling elements 41 are present in the circumferential direction 15, positioned relative to each other at 120° intervals. The first switching element 30 is rotationally fixed to the ring gear 12.

[0053] The switching system 9 also features the holding mechanism. The holding mechanism is implemented by holding contours 42, 43 provided in the first switching element 30 and second switching element 31, and by rolling elements 41 that can be positioned in these holding contours 42, 43. The holding contours 42, 43 are each axial indentations in the first switching element 30 and second switching element 31, so that the relative position of the first switching element 30 to the second switching element 31 can be maintained by means of the rolling elements 41. The holding contours 42, 43 are also designed in the form of a ramp. First holding contours 42 are formed in the first ramp contour 39. Second holding contours 43 are formed in the circumferential direction 15 between the second ramp contours 40.The brake 32 is positioned radially spaced from the planet carrier 10 and axially at the initial end, such that the first switching element 30 and the second switching element 31 are arranged in the axial direction 13 between the ring gear 12 and the brake 32. A braking torque can be generated by means of the brake 32, which enables a relative rotation in the circumferential direction 15 of the first switching element 30 to the second switching element 31.

[0054] In the axial direction 13, a second bearing 68 is positioned between the first switching element 30 and the planet carrier 10. The second bearing 68 allows the planet carrier 10 to be rotatably decoupled from the ramp system 37.

[0055] Figures 2a to 5a show the switching system 9 in operation and illustrate the various individual positions for switching from the first transmission stage 3 to the second transmission stage 4. Figures 2b to 5b simultaneously show the rotation of the first switching element 30 and the second switching element 31 relative to each other. A total of three (main) positions—a first position, a second position, and a third position—can be represented, corresponding to the two transmission stages 3 and 4, and a (torque-free) position.

[0056] In Figures 2a and 2b, the rotation of the first switching element 30 to the second switching element 31 is 30° in a first rotational position. A braking torque is generated by means of the brake 32, which slows the rotation of the second switching element 31. The first switching element 30 and the second switching element 31 rotate at different speeds. Due to the rotation, the rolling elements 41 roll circumferentially 15 along the ramp contours 39, 40 and cause an axial displacement of the first switching element 30 relative to the second switching element 31. Since the first switching element 30 is coupled to the planet carrier 10 in the axial direction 13, the planet carrier 10 is displaced in the axial direction 13 according to a first direction of movement 44 and is no longer held against the support area 28. Once the planet carrier 10 is detached from the support area 28, the electric machine 2 is decoupled and no more torque transmission takes place.The planet carrier 10 rotates freely. The planetary gear 5 is in its third position. In Figures 3a and 3b, the rotation from the first switching element 30 to the second switching element 31 is 63° in a second rotational position. After the planet carrier 10 is released from the support area 28 and moves axially, its internal teeth 45 engage the sun gear 7. Due to the greater axial displacement compared to Figure 2a, the rotational speed of the planet carrier 10 is adjusted to the rotational speed of the sun gear 7. As soon as the rotational speeds match, the planet carrier 10 engages the sun gear 7. The planet carrier 10 is thus directly connected to the sun gear 7 for torque transmission. The axial displacement in the first direction of movement 44 tensions the leaf springs 36. The leaf springs 36 can, provided there is no longer a braking torque, ensure that the displacement mechanism is reset.

[0057] In Figures 4a and 4b, the rotation from the first switching element 30 to the second switching element 31 is 120° in a third rotation position. In this rotation position, the rolling elements 41 are positioned in the retaining contours 42, 43 of the first switching element 30 and the second switching element 31. This position can be held without braking torque. To release the rolling elements 41 from the retaining contours 42, 43, an increased braking torque is preferred. In this second position, the second transmission stage 4, and thus the second position, is reached, and the torque of the electric machine 2 is transmitted via the second transmission stage 4.

[0058] In Figures 5a and 5b, the rotation from the first switching element 30 to the second switching element 31 is 240° in a fourth rotation position. Due to the design of the ramp contours 39, 40, the first switching element 30 has moved back in a second direction of movement 52, and the planetary gear 5 is again in the first position. The first switching element 30 has rotated in the same direction.

[0059] Figure 6 shows a second embodiment of the electric drive module 1. The operation of the switching system 9 corresponds to that of the first embodiment according to Figures 2 to 5. In the present embodiment, the arrangement of the planetary gear 5, the switching system 9, and the hollow shaft 22 is rotated by 180°, so that the first direction of movement 44 in the axial direction 13 extends towards the housing 27a of the electric machine 2, and the second direction of movement 52 extends in the axially opposite direction. The support area 28 is formed on a housing 27b (of the planetary gear 5). In the present embodiment, the sleeve 19 is fixedly held to the housing 27b by means of a screw connection.

[0060] In the present embodiment, the electric drive module 1 has a synchronization device 46. For this purpose, a spring 47 is arranged axially between the hollow shaft 22 and the planet gears 20. The spring 47 is arranged axially 13 on a second hollow shaft 48. The second hollow shaft 48 has a flange 49 against which the spring 47 rests with one axial side. On a second axial side of the spring 48, it is held and pre-tensioned by a retaining ring 50.

[0061] Figures 7a to 11a show the switching system 9 for the second embodiment of the electric drive module 1 in operation, and illustrate the various individual positions for switching from the first transmission stage 3 to the second transmission stage 4, with the electric drive module 1 and the switching elements 30, 31 shown in their different rotational positions. Figures 7b to 11b simultaneously show the rotation of the first switching element 30 and the second switching element 31 relative to each other.

[0062] For the movement sequence of the switching system 9, refer to Figs. 2a to 5a. The operation of the synchronizing device 46 is explained below.

[0063] In Figures 7a and 7b, the rotation from the first switching element 30 to the second switching element 31 is 30° in the first rotational position. The axial displacement in the first direction of movement 44 also axially displaces the spring 47. In this position, the spring 47 remains held by the retaining ring 50.

[0064] In Figures 8a and 8b, the rotation from the first switching element to the second switching element is 31° in a fifth rotation position. In this position, the spring 47 is supported on one side by an inner end face 51 of the hollow shaft 22 and on the other side by the planet gears 20, more precisely by the flange 49 of the second hollow shaft 49. From this position, a synchronization torque is generated, which assists in adjusting the speed of the planet carrier 10 to the speed of the sun gear 7. Furthermore, the synchronization torque enables the planet gears 20 to be braked. This allows for a faster shift into the second gear stage 4, so that the planet carrier 10, with its internal teeth 45, can engage with the sun gear 7.

[0065] Figures 12a to 12d illustrate the various gear ratios achievable with the planetary gear set 5. The planetary gear set 5 is shown in a front view. Figure 12a depicts the first gear, a first forward gear. In this gear, the rotor shaft 8 rotates with torque, and thus the sun gear 7 also rotates counterclockwise, as shown. The planet carrier 10 is held against the support area 28, as described previously. This prevents the planet carrier 10 from rotating. The planet gears 20, which mesh with the sun gear 7, rotate clockwise on a web of the planet carrier 10. The ring gear 12, which meshes with the planet gears 20, also rotates clockwise. This is a first torque transmission path and the first gear ratio stage 3.

[0066] Fig. 12b shows the second gear, a second forward gear. In this embodiment, the planet carrier 10 is connected to the sun gear 7 via the internal teeth 45 (see Fig. 4a) to transmit torque. The torque is transmitted via the sun gear 7 directly to the planet carrier, which then transmits the torque via the planet gears 20 to the ring gear 12. The rotor shaft 8 rotates clockwise, causing the planet gears 20, which mesh with the sun gear 7, to transmit the torque directly to the ring gear 12. The ring gear 12 also rotates clockwise. This constitutes a second torque transmission path and the second gear ratio 4.

[0067] Fig. 12c now shows the first reverse gear. Here, the rotor shaft 8 rotates in the opposite direction shown in Fig. 12a. Thus, the sun gear 7, the planet gears 20, and the ring gear 12 also change their direction of rotation. This is a third gear ratio 65. Fig. 12d now shows the second reverse gear. Here, the rotor shaft 8 rotates in the opposite direction shown in Fig. 12b. Thus, the sun gear 7 and the ring gear 12 also change their direction of rotation. This is a fourth gear ratio 66.

[0068] Fig. 13a shows the electric drive train 26 with the electric drive module 1 of the first embodiment.

[0069] The electric drive train 26 has, in the direction of the first torque transmission path after the electric drive module 1, an intermediate shaft 53 with a gear stage 54, a further (second) planetary gear set 55, and three synchronizer units 56, 57, 58. The torque is transmitted via the external teeth 25 of the first hollow shaft 22, through the gear stage 54, to a freely rotatable gear 59 on the intermediate shaft 53. The torque can be transmitted via a total of two synchronizer units 56, 57. With the aid of a first synchronizer unit 56, the gear 59 can be directly connected to the intermediate shaft 53 for torque transmission. With the aid of a second synchronizer unit 57, the torque can be transmitted to the further planetary gear set 55. With the aid of a third synchronizer unit 58, the torque transmitted via the further planetary gear set 55 can be transmitted to the intermediate shaft 53.In this process, a planet carrier 60 of the planetary gear 55 can be connected to the intermediate shaft 53.

[0070] The electric drive module 1 is arranged twice in the electric drive train 26. Both electric drive modules are engaged with the gear 59 of the gear stage 54.

[0071] The intermediate shaft 53 engages with a differential gear 61 to transmit torque, which then transmits the torque to a driven gear 62, 63 respectively.

[0072] Figure 13b shows the electric drive train 26 with the electric drive module 1 in the second embodiment. The previously described configurations of the electric drive train 26 also apply here. List of reference symbols: electric drive module, electric machine, first gear stage, second gear stage, planetary gear input, sun gear, rotor shaft, switching system, planet carrier, output, ring gear, axial direction, radial direction, circumferential direction, center axis, retaining ring, retaining ring, sleeve, planet gear, flange, hollow shaft, screw, outer side, external teeth, electric drive train: a) housing, b) housing, support area, positive locking connection, first switching element, second switching element, brake

[0073] tab

[0074] Through hole

[0075] rivet

[0076] leaf spring

[0077] Ramp system

[0078] Holding mechanism first ramp contour second ramp contour

[0079] Rollers first holding contour second holding contour first direction of movement

[0080] internal teeth

[0081] Synchronization device

[0082] Feather

[0083] Hollow shaft

[0084] flange

[0085] retaining ring

[0086] Front side, second direction of movement

[0087] Intermediate wave

[0088] gear stage

[0089] Planetary gear set, first synchronization unit, second synchronization unit, third synchronization unit

[0090] gear

[0091] Planetary carrier

[0092] Differential gear first output gear second output gear

[0093] screw third gear stage fourth gear stage first bearing second bearing

Claims

Patent claims 1. Electric drive module (1) for a motor vehicle comprising an electric machine (2), a planetary gear (5) operable via two different gear ratio stages (3, 4), wherein a sun gear (7) serving as input (6) of the planetary gear (5) is connected to a rotor shaft (8) of the electric machine (2) in a torque-transmitting manner, and a switching system (9) for switching between the two gear ratio stages (3, 4), wherein the switching system (9) is designed such that, in order to adjust the gear ratio stage (3, 4), it axially displaces a planet carrier (10) of the planetary gear (5) between at least two different positions and thereby changes a torque transmission path.

2. Electric drive module (1 ) according to claim 1 , characterized in that the switching system (9) is designed and the planet carrier (10) is received in such a way that the planet carrier (10) is held in a first position in a first transmission stage (3) on a support area (28) which is fixed to the housing during operation.

3. Electric drive module (1 ) according to claim 1 or 2, characterized in that the switching system (9) is designed and the planet carrier (10) is received in such a way that the planet carrier (10) is rotationally fixed to the sun gear (7) in a second position in a second transmission stage (4).

4. Electric drive module (1) according to one of claims 1 to 3, characterized in that the switching system (9) is designed and the planet carrier (10) is aligned such that the planet carrier (10) is in a free position in a third position.

5. Electric drive module (1 ) according to one of claims 1 to 4, characterized in that the switching system (9) has a first switching element (30) and a second switching element (31 ) linked to the first switching element (30) via a sliding mechanism, wherein the sliding mechanism can be actuated by means of a brake (32).

6. Electric drive module (1 ) according to claim 5, characterized in that the displacement mechanism has a ramp system (37) with roller means (41 ) formed on the first switching element (30) and second switching element (31 ).

7. Electric drive module (1 ) according to claim 5 or 6, characterized in that the first switching element (30) is pre-tensioned in at least one of the two positions by means of a spring mechanism.

8. Electric drive module (1 ) according to one of claims 1 to 7, characterized in that a synchronization device (46) is provided which generates a synchronization torque for adjusting the speed of the planet gears (20).

9. Electric powertrain (26) for a motor vehicle comprising an electric drive module (1 ) according to one of the preceding claims and a transmission (54) downstream of the drive module (1 ).

10. Electric drive train (26) according to claim 9, characterized in that two drive modules (1 ) according to one of claims 1 to 7 are connected upstream of the transmission (54).

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