Planetary gears and motor vehicle

Abstract

The invention relates to a planetary gear (1) and a motor vehicle comprising the planetary gear (1), wherein the planetary gear (1) comprises: - a sun gear (2) with a left-hand toothed first sun gear part (2a) and a right-hand toothed second sun gear part (2b), - a ring gear (3) with a left-hand toothed first ring gear part (3a) and a right-hand toothed second ring gear part (3b), - comprising a planet gear (4) which is mounted on a planet gear carrier (6) of the planetary gear (1) by means of a planet gear bolt (5) and which meshes with both the sun gear (2) and the ring gear (3): - a right-hand toothed first planet gear part (4a) and a left-hand toothed second planet gear part (4b) manufactured separately from the first planet gear part (4a), - a centering sleeve (7) by means of which the planet gear parts (4a, 4b) are mounted axially and rotatably to each other.

Description

[0001] The present invention relates to a planetary gear and a motor vehicle comprising the planetary gear.

[0002] To achieve exceptionally smooth running and low noise levels in motor vehicles, especially passenger cars, spur gears in conventional transmissions are often helical. However, this results in high radial and axial forces during operation, necessitating particularly rigid and stable bearings for the spur gears. This leads to a weight disadvantage, as the bearings are material-intensive and heavy due to the high stiffness requirements. Furthermore, the heavy and rigid bearings result in particularly high friction losses within the conventional transmission. Additionally, the automotive sector, in particular, requires the ability to transmit high power and torque using a highly compact transmission.

[0003] DE 10 2011 085 119 B3 discloses a spur gear differential whose planet carrier is formed from two sheet metal components connected to each other in a housing-like manner. The planet carrier, i.e., the sheet metal components, and a drive spur gear are connected to each other via connecting screws, the drive gear being able to have helical teeth. DE 1 963 831 B discloses a planetary gear with a two-part central gear, the halves of which are formed separately from each other. The central gear halves are connected to a gear housing or a slow-running shaft via coupling teeth and a toothed coupling sleeve connection for load equalization. The coupling sleeve connection is formed in one piece as a coupling sleeve with two teeth, and the adjacent coupling teeth of the central gear halves engage together in one of the two teeth of the coupling sleeve and are axially secured.Furthermore, DE 10 2016 115 011 A1 shows a planetary gear set with a double helical planetary gear, which is composed of two gear pieces.

[0004] The object of the present invention is to create a solution that is as simple and cost-effective as possible in order to transmit a particularly high amount of power or torque as efficiently as possible by means of a radially compact gearbox.

[0005] This problem is solved by the subject matter of the independent claims. Further possible embodiments of the invention are disclosed in the dependent claims, the description, and the figures. Features, advantages, and possible embodiments set forth in the description for one of the subject matter of the independent claims are to be regarded, at least analogously, across categories and embodiments as features, advantages, and possible embodiments of the respective subject matter of the other independent claims, as well as of any possible combination of the subject matter of the independent claims, optionally in conjunction with one or more of the dependent claims.

[0006] According to the invention, a planetary gear system for a motor vehicle is proposed. Furthermore, the invention proposes a motor vehicle that incorporates one or more such planetary gear systems, for example, to provide a transmission ratio between a rotor shaft of an electric drive motor of the motor vehicle and a wheel drive shaft of the motor vehicle. This means that the planetary gear system, in its intended installation position, forms an integral part of the motor vehicle. Therefore, the motor vehicle is, in particular, a purely electric or hybrid-electric vehicle. However, the use of the planetary gear system is not limited to the technical field of motor vehicles.

[0007] The planetary gear set comprises a sun gear, a ring gear, and a planet gear. The sun gear has a left-handed first part and a right-handed second part, while the ring gear has a left-handed first part and a right-handed second part. The first and second parts of the sun gear and the first and second parts of the ring gear can be manufactured separately or integrally. In any case, the sun gear and ring gear parts are arranged along a common longitudinal center axis, resulting in double helical teeth on both the sun gear and the ring gear due to their opposing tooth orientations. The first and second parts of the sun gear and the first and second parts of the ring gear can be rotatably or non-rotatably mounted relative to each other with respect to their respective longitudinal center axis.The planet gear is mounted on a planet carrier of the planetary gear set by means of a planet gear bolt and meshes with both the sun gear and the ring gear. The planet gear has a first planet gear section with right-handed teeth and a second planet gear section with left-handed teeth, manufactured separately from the first planet gear section. The planet gear sections are arranged along a longitudinal center axis of the planet gear, so that a double helical tooth profile is formed on the planet gear that corresponds to the double helical teeth of the sun gear and the double helical teeth of the ring gear. The planet gear sections are mounted axially and rotatably relative to each other by means of a centering sleeve of the planet gear.

[0008] By meshing the two counter-rotating helical planetary gear sections with the sun gear(s) and the ring gear(s), the planetary gear can transmit twice the torque for a given ratio between the axial length of the sun gear and the base circle diameter, and for a given ratio between the sun gear and ring gear diameters – i.e., for a given gear ratio. This allows the planetary gear to be radially very compact while still being capable of transmitting a particularly high power or torque. Thanks to the double helical gearing, axial forces occurring in the gear meshes during operation of the planetary gear cancel each other out, resulting in very low stress on the sun gear shaft bearing and, if applicable, the drive shaft bearing, leading to advantageously low bearing friction losses.The multi-part design of the planetary gear allows for the independent manufacturing of the first planetary gear ring and the second planetary gear ring of the second planetary gear ring. This permits larger tolerances for the double helical gearing of the planetary gear. Because the planetary gear parts are rotatable relative to each other on the centering sleeve, these tolerances can be efficiently compensated for. This makes the double helical planetary gear, and consequently the planetary gearbox, particularly easy to manufacture. Furthermore, the relative rotatability of the planetary gear parts allows for the compensation of any assembly-related and / or design-related rotational errors in the ring gear and sun gear.

[0009] In a further possible embodiment, the centering sleeve and one of the planet gear parts are materially bonded together. The centering sleeve can therefore be materially bonded either to the first, right-handed planet gear part or to the second, left-handed planet gear part. For example, the corresponding planet gear part and the centering sleeve can be welded or bonded together. Furthermore, it is conceivable that the corresponding planet gear part and the centering sleeve are manufactured in one piece, particularly by thermoforming. This reduces the number of individual parts that need to be handled during assembly of the planetary gear, further simplifying its production.

[0010] According to a possible further development, the centering sleeve is axially penetrated between the planetary gear components – specifically, axially in the center – by a radial centering sleeve opening. In particular, the centering sleeve has two or more centering sleeve openings along its circumference. Due to these centering sleeve openings, the centering sleeve is made particularly lightweight. Furthermore, the respective centering sleeve opening can be precisely positioned to balance the centering sleeve. Additionally, since each centering sleeve opening is fluid-permeable, it can be used as a passage for a coolant and / or lubricant, such as oil.When oil is introduced into an internal area of ​​the centering sleeve, centrifugal force forces it radially outward during operation of the planetary gear system, towards an inner circumferential surface of the centering sleeve. From there, it passes through the radial opening(s) of the centering sleeve and reaches a toothed ring of the planet gear. This allows for particularly efficient lubrication of the meshing between the planet gear and the ring gear during operation of the planetary gear system. The coolant and / or lubricant, or the oil, is introduced into the interior of the centering sleeve, for example, via the planet gear pin, as described in more detail below.

[0011] According to another possible embodiment, the planet gear has a spacer device by means of which the planet gear parts are axially spaced from one another via a planet gear gap. The spacer device comprises the centering sleeve, which is axially long enough to space the planet gear parts from one another via the planet gear gap. Alternatively or additionally, the spacer device comprises a spacer collar arranged between the planet gear parts, which is axially as long as the planet gear gap. For example, the spacer collar can be attached to the first or the second planet gear part, with the other planet gear part abutting the spacer collar at its end face. It is also conceivable that the spacer collar comprises a first spacer collar portion arranged on the first planet gear part and a second spacer collar portion arranged on the second planet gear part, which abut each other axially at their end faces.The spacer collar can be interrupted once or more along the circumferential direction of the planet gear or planet gear parts, particularly in the area of ​​the centering sleeve opening(s). This ensures that the two planet gear parts do not touch each other axially, i.e., at their end faces, but are spaced apart, thus preventing the teeth from rubbing against each other during operation of the planetary gear.

[0012] The two planet gear sections are rotatably mounted on the planet gear pin by means of a rolling bearing, where, for example, a needle bearing, a deep groove ball bearing, etc., is suitable as a rolling bearing. In this case, a thrust washer is used to absorb axial loads. In another possible embodiment, the first planet gear section is mounted on the planet gear pin by means of a first tapered roller bearing, whereas the second planet gear section is mounted on the same planet gear pin by means of a second tapered roller bearing. The tapered roller bearings are arranged, in particular, in an X-arrangement. Instead of the tapered roller bearings, bearings of other designs can be used, for example, angular contact ball bearings, tapered roller bearings, etc. The tapered roller bearings support the planet gear sections axially and radially on the planet gear pin, which is why a thrust washer is not required in the planetary gear according to the invention.The elimination of thrust washers results in less friction during the operation of the planetary gear than with thrust washers, which is particularly evident in lower drag losses.

[0013] According to a possible further development, the planetary gear set is designed so that the planet gear pin and the planet carrier are fixed to each other in a rotationally fixed manner. This prevents the planet gear pin from rotating in its bearing hub on the planet carrier during operation, which again leads to less friction within the planetary gear set. Furthermore, the planet gear pin's fixed position within the planet carrier makes it particularly efficient for supplying oil to the planet gear bearings and for the gear meshing between the planet gear and the ring gear, as will be described in more detail below.To prevent the planetary gear bolt from rotating relative to the planet carrier, the collar of the planetary gear bolt can, for example, be non-circular, with the planet carrier's flange having a shape corresponding to the planetary gear bolt collar, so that the planetary gear bolt inserted into the planet carrier is securely seated against rotation. Alternatively or additionally, a locking pin is provided that engages radially in the planetary gear bolt on one side and in the planet carrier, specifically in its flanged seat, on the other. The locking pin prevents not only rotation of the planetary gear bolt but also axial displacement of the planetary gear bolt relative to the planet carrier.

[0014] In another possible embodiment, the planetary gear bolt has a central axial blind opening and one or more radial oil openings. Each radial oil opening completely penetrates a wall of the planetary gear bolt, opening radially into the blind hole on one side and radially onto an outer circumferential surface of the planetary gear bolt on the other. In particular, the radial oil openings are arranged axially between the planetary gear components. This embodiment of the planetary gear further includes an oil supply device whose oil outlet is directed towards the axial blind opening of the planetary gear bolt. During operation of the planetary gear, oil is introduced into the axial blind opening of the planetary gear bolt, from where it passes through the radial oil opening and is conveyed into the interior of the centering sleeve.In particular, the oil reaches the tapered roller bearings of the planetary gear, thus lubricating them very efficiently. As described above, the oil then passes through the centering sleeve opening(s) to the meshing teeth between the ring gear and the planetary gear. Furthermore, the rotating planetary gear forces the oil, due to centrifugal force, through the centering sleeve opening(s) to the meshing teeth between the sun gear and the planetary gear. For example, the oil outlet of the oil supply device is an oil nozzle, through which the oil is injected directly into the axial slot opening. Alternatively or additionally, the oil supply device can have a radial oil channel formed in a drive shaft connected to the sun gear, branching off from an axial oil supply channel of the drive shaft. In this case, the oil supply device also includes an oil guide device (for example, an oil guide plate, an oil guide tray, an oil guide channel, etc.).), which is attached to the planet carrier or is formed as part of the planet carrier. During operation of the planetary gear, the oil is thus driven from the radial oil channel of the rotating drive shaft into the oil guide and from there conveyed into the axial slot of the planet gear pin. Regardless of whether the drive shaft has the radial oil channel for the oil guide or not, the drive shaft can have a sun gear oil channel located in the area of ​​the sun gear, which branches off from the oil supply channel of the drive shaft. The sun gear oil channel opens axially, in particular, between the sun gear components on an outer circumferential surface of the drive shaft, so that oil can be supplied to the gear mesh between the sun gear and the planet gear with particular efficiency.

[0015] In connection with the rotationally fixed connection between the planet gear pin and the planet carrier, in conjunction with the oil supply device, another possible embodiment provides that only a portion of the planet gear pin wall projecting radially outwards in the axial section of the planetary gear is penetrated by the radial oil opening. This eliminates unnecessary radial openings, such as bores, in the planet gear pin, thus preventing unnecessary weakening of the planet gear pin. Nevertheless, a reliable oil supply to the tapered roller bearings and into the interior of the centering sleeve is ensured, since the radial oil opening is located precisely in the portion of the planet gear pin wall to which the oil is driven by centrifugal force on the inside, i.e., in the axial recess opening.

[0016] According to another possible embodiment, the sun gear of the planetary gear is designed according to one of the following options: i. One of the sun gear components and the drive shaft of the planetary gear set are manufactured separately and connected to each other in a rotationally fixed manner by means of a sun gear spline. The corresponding sun gear component is clamped against a support collar on the drive shaft, for example, by means of a flange nut screwed onto the drive shaft, and thus axially fixed on / to the drive shaft. The other sun gear component and the drive shaft are joined together by a material bond, for example, formed in one piece or welded, bonded, etc. ii. Both sun gear parts are manufactured separately from each other and separately from the drive shaft and are connected to the drive shaft in a rotationally fixed manner by means of a sun gear spline. The two sun gear parts can be clamped against a support collar on the drive shaft by means of a flanged nut and thus axially fixed on / to the drive shaft. Alternatively, the two sun gear parts can be individually clamped against their respective support collars by means of a flanged nut, or both parts can be clamped against the same support collar. iii. Both sun gear parts and the drive shaft of the planetary gear are materially bonded to each other, i.e. formed in one piece with the drive shaft or first manufactured separately or in one piece together and then bonded, welded, etc. to the drive shaft.

[0017] In options i. and ii., the assembly of the planetary gear is further simplified, and in option iii., the drive shaft and the sun gear or sun gear parts are connected to each other in a particularly stable manner, which benefits a particularly efficient power or torque transmission.

[0018] In another possible embodiment, the sun gear parts are rotated relative to each other such that each end face of a tooth of the first sun gear part lies axially opposite a corresponding tooth gap of the second sun gear part. This arrangement is called a tooth-on-gap arrangement. The ring gear parts are arranged with a corresponding rotation relative to each other so that the planet gear parts can maintain their axial alignment along the longitudinal center axis of the planet gear, with the planet gear parts being rotated relative to each other corresponding to the rotational phase offset of the sun and ring gear parts. This rotational phase offset results in a particularly homogeneous stiffness profile of the respective gear teeth, leading to a particularly low excitation behavior of the planetary gear components involved. This results in a particularly advantageous vibration and...The acoustic behavior of the planetary gear is optimized. As a result, a user of a vehicle equipped with a planetary gear is provided with particularly high NVH quality (noise, vibration, harshness). In this context, the outer splines of the sun gear's toothing, located on the drive shaft, can be arranged rotated relative to each other to achieve the desired rotational phase offset.

[0019] To further improve NVH quality, a possible further development involves connecting the ring gear and the ring gear carrier of the planetary gear unit in a rotationally fixed manner. The planetary gear unit housing has a mounting element that is rotationally fixed to the ring gear carrier but axially and / or radially movable. The ring gear carrier can be made of plastic. A particularly simple way to create this rotationally fixed but axially and / or radially movable connection between the ring gear(s) and the ring gear carrier is a radially movable ring gear carrier splined connection. This means that a splined hub portion of the ring gear carrier splined connection is located on the ring gear carrier, while a splined shaft portion of the ring gear carrier splined connection, engaging with the splined hub portion, is located on the mounting element.When the planet gear rolls on the internal teeth of the ring gear, the ring gear is reversibly stretched radially outwards at the tooth engagement between the planet and ring gears. This causes the ring gear, and consequently the ring gear carrier, to deviate from a perfect circular shape during operation of the planetary gear set. This is known as ovalization. The ring gear carrier splined shaft compensates for this ovalization by moving the splines of the splined hub radially outwards, following the tooth engagement between the planet and ring gears. The splines of the splined shaft and splined hub sections are designed with a radial spline height such that the spline flanks can slide against each other, but only to the extent necessary to maintain engagement at the point of circumferential ovalization of the ring gear carrier. This ensures reliable power and torque transmission while simultaneously compensating for the ovalization.This advantageously prevents vibrations that occur due to the circumferential ovalization during the operation of the planetary gear from being transmitted to the housing.

[0020] In a possible further development, the ring gear of the planetary gear is designed according to one of the following options: i. One of the ring gear parts and the ring gear carrier are manufactured separately and connected to each other in a rotationally fixed manner by means of a ring gear spline. In contrast, the other ring gear part and the ring gear carrier are joined by a material bond, for example, manufactured in one piece or welded, bonded, etc. The ring gear part manufactured separately from the ring gear carrier can, for example, be axially secured by means of a clamping ring located in a clamping ring groove of the ring gear carrier, with the corresponding ring gear part positioned between the clamping ring and the other ring gear part. Axial securing by means of an externally threaded ring screwed into an internal thread of the ring gear carrier is also conceivable. ii. Both ring gear parts are manufactured separately from each other and separately from the ring gear carrier and are connected to the ring gear carrier in a rotationally fixed manner by means of a ring gear spline. The ring gear parts can be axially secured in the ring gear carrier between two clamping or external threaded rings. If a rotational phase offset is provided, the internal splines of the ring gear spline arranged on the ring gear carrier can be arranged rotated relative to each other. iii. Both ring gear parts and the ring gear carrier are materially bonded to each other, i.e. formed in one piece with the ring gear carrier or first manufactured separately or in one piece together and then bonded, welded, etc. to the ring gear carrier.

[0021] In options i. and ii., the assembly of the planetary gear is further simplified, and in option iii., the ring gear carrier and the ring gear or ring gear parts are connected to each other in a particularly stable manner, which benefits particularly efficient power and torque transmission.

[0022] Further features of the invention may become apparent from the claims, the figures, and the description of the figures. The features and combinations of features mentioned above in the description, as well as the features and combinations of features shown below in the description of the figures and / or in the figures themselves, can be used not only in the combinations specified, but also in other combinations or on their own, without departing from the scope of the invention.

[0023] The drawing shows in: Fig. 1. A view (i.e., an axial section) of a planetary gear set cut along an axial section plane spanned by a radius and a main axis of the gear set. Fig. 2 a perspective and partial view of a planetary gear part of a planetary gear of the planetary gear and Fig. 3 a schematic view of a rotational phase offset of two sun gear parts of a sun gear of the planetary gear.

[0024] The following is a joint description of a planetary gear 1 and a motor vehicle (not shown) incorporating the planetary gear 1. In the figures, identical and functionally equivalent elements are designated with the same reference numeral.

[0025] Fig. Figure 1 shows the planetary gear set 1 in an axial section view. The planetary gear set 1 comprises, as gear wheels 2, 3, 4, a sun gear 2, a ring gear 3, and a planet gear 4. The sun gear 2 has a left-handed first sun gear section 2a and a right-handed second sun gear section 2b, while the ring gear 3 has a left-handed first ring gear section 3a and a right-handed second ring gear section 3b. The planet gear 4 is mounted on a planet carrier 6 of the planetary gear set 1 by means of a planet gear pin 5 and meshes with both the sun gear 2 and the ring gear 3. The planet gear 4 has a right-handed first planet gear section 4a and a left-handed second planet gear section 4b, which is manufactured separately from the first planet gear section 4a. By means of a centering sleeve 7 of the planet gear 4, the planet gear parts 4a, 4b are axially and rotatably mounted to each other.

[0026] In the present example, a drive shaft 8 of the planetary gear 1 and the first sun gear part 2a are formed integrally, whereas the second sun gear part 2b and the drive shaft 8 are connected to each other in a rotationally fixed manner by means of a sun gear spline 9. The second sun gear part 2b is axially secured to the drive shaft 8 by means of a flange nut 10. Other embodiments of the sun gear 2 or the drive shaft 8 are conceivable; for example, sun gear parts 2a, 2b and the drive shaft 8 of the planetary gear 1 can be connected to each other in a rotationally fixed manner by means of the sun gear spline 9, or both sun gear parts 2a, 2b and the drive shaft 8 can be joined to each other by a material bond, for example, formed integrally.

[0027] In this example, the planetary gear 1 has a ring gear carrier 11 in which the ring gear parts 3a, 3b are mounted in a rotationally fixed manner by means of a ring gear spline 12. The ring gear parts 3a, 3b are axially secured between two clamping rings 13, which are arranged in respective clamping ring grooves 14. Other embodiments of the ring gear 3 and the ring gear carrier 11 are equally conceivable; for example, one of the ring gear parts 3a, 3b and the ring gear carrier 11 can be rotationally fixed to each other by means of the ring gear spline 12, while the other ring gear part 3a, 3b and the ring gear carrier 11 are bonded together by a material connection. Furthermore, both ring gear parts 3a, 3b and the ring gear carrier 11 can be bonded together by a material connection.

[0028] In this example, the planet gear parts 4a, 4b and the centering sleeve 7 are manufactured separately. Alternatively, one of the planet gear parts 4a, 4b and the centering sleeve could be bonded together, for example, manufactured in one piece. In any case, both planet gear parts 4a, 4b sit on the centering sleeve 7 in such a way that the planet gear parts 4a, 4b are rotatable relative to each other. The centering sleeve 7 has a radial centering sleeve opening 15 – in this case, several centering sleeve openings 15 – wherein each centering sleeve opening 15 completely penetrates a wall of the centering sleeve 7 radially. Fig. Figure 1 shows that the centering sleeve openings 15 are located along a circumferential direction of the centering sleeve 7 and axially centered between the planet gear parts 4a, 4b. In particular, the centering sleeve openings 15 are equidistant from each other along the circumferential direction of the centering sleeve 7.

[0029] The planet gear parts 4a, 4b abut a respective planet gear shoulder 16 (see Fig. 2, which shows a perspective and partial view of the first planet gear part 4a), directly abuts the centering sleeve 7 at a respective axial centering sleeve end face 17, thereby keeping the planet gear parts 4a, 4b axially separated from each other by means of the centering sleeve 7, so that a planet gear gap 18 is formed between the planet gear parts 4a, 4b. In this way, the centering sleeve 7 acts as a first spacer element of a spacer device 19 of the planet gear 4. According to the example described here, the spacer device 19 also has a spacer collar 20, which is arranged between the planet gear parts 4a, 4b. In this case, the spacer collar 20 has a first spacer collar portion 20a arranged on the first planet gear part 4a and a second spacer collar portion 20b arranged on the second planet gear part 4b, which abut each other axially at their end faces.The spacer collar 20 is also interrupted several times along the circumferential direction of the planet gear parts 4a, 4b, here in each case in the area of ​​the centering sleeve openings 15.

[0030] The planetary gear 1 also has a bearing for the planet gear 4, which in this example is formed by a first tapered roller bearing 21 and a second tapered roller bearing 22. As in Fig. As can be seen in Figure 1, the first planet gear part 4a is supported by the first tapered roller bearing 21, whereas the second planet gear part 4b is supported by the second tapered roller bearing 22. The tapered roller bearings 21 and 22 are arranged in an X configuration. Furthermore, it is evident from Fig. Figure 1 shows that the planet gear bolt 5 and the planet gear carrier 6 are fixed to one another in a rotationally fixed manner. For this purpose, a locking pin 23 is provided in the present example, which engages on one side in the planet gear bolt 5 and on the other side in the planet gear carrier 6, thus preventing rotation of the planet gear bolt 5 and axial displacement of the planet gear bolt 5 relative to the planet gear carrier 6. Furthermore, according to the present example, the planet gear bolt 5 has an axial blind hole 24, which is referred to here as the axial blind opening 24. In addition, the planet gear bolt 5 has a radial oil opening 25 – in this case, several radial oil openings 25 – wherein the respective radial oil opening 25 opens on one side into the axial blind opening 24 and on the other side onto an outer circumferential surface 26 of the planet gear bolt 5. Fig. Figure 1 shows that only a radially outwardly pointing wall portion 27 of the planet gear bolt 5 is penetrated by the radial oil opening 25.

[0031] The planetary gear 1 further comprises an oil supply device 28, the oil outlet opening 29 of which is directed towards the axial blind opening 24 of the planet gear pin 5, so that during operation of the planetary gear 1, oil is introduced into the axial blind opening 24 of the planet gear pin 5, from where it passes through the radial oil opening 25 and is conveyed into an inner area 30 of the centering sleeve 7. In this way, the oil reaches the tapered roller bearings 21, 22 and – through the centering sleeve openings 15 – both a planet gear-ring gear mesh and a sun gear-planet gear mesh. The oil supply device 28 has a radial oil channel 31, which is formed in the drive shaft 8 connected to the sun gear 2 and branches off from an axial oil supply channel 32 of the drive shaft 8. Furthermore, the oil supply device 28 includes an oil guide tray 33, which is attached to the planetary gear carrier 6.The oil is driven from the radial oil channel 31 of the rotating drive shaft 8 into the oil guide bowl 33 and from there conveyed into the axial blind opening 24 of the planet gear pin 5. In the present example, the drive shaft 8 has an optional sun gear oil channel 34 located in the area of ​​the sun gear 2, which branches radially from the oil supply channel 32 and opens axially between the sun gear parts 2a, 2b, so that oil is supplied directly to the sun gear-planet gear tooth mesh.

[0032] Fig. Figure 3 shows a schematic view of the rotational phase offset of the sun gear parts 2a, 2b of the sun gear 2 of the planetary gear 1. For clarity, in Fig. Figure 3 shows the drawing elements relating to the first sun gear part 2a in solid lines, whereas the drawing elements relating to the second sun gear part 2b are shown in dashed lines. The rotational phase offset is achieved by rotating the sun gear parts 2a and 2b relative to each other such that a respective end face 35 of teeth 36 of the first sun gear part 2a is axially opposite a respective tooth gap 37 of the second sun gear part 2b. The respective tooth gap 37 is formed by two teeth 38 of the second sun gear part 2b that are directly consecutive along one circumferential direction of the second sun gear part 2b. Accordingly, the ring gear parts 3a and 3b are arranged rotated relative to each other so that the planet gear parts 4a and 4b can maintain their common axial arrangement along the longitudinal center axis of the planet gear 4. The planet gear parts 4a and 4b compensate for the rotational phase offset.

[0033] Out of Fig.Figure 1 further shows that in the present example, the ring gear 3 and the ring gear carrier 11 are connected to each other in a rotationally fixed manner, wherein a housing 39 of the planetary gear 1 has a mounting body 40 which is connected to the ring gear carrier 11 in a rotationally fixed manner, but axially and / or radially movable – in this case by means of a radially movable ring gear carrier splined shaft 41. In order to create the radial movement of the ring gear carrier splined shaft 41, it is provided in this case that a splined hub portion 41a of the ring gear carrier splined shaft 41 is arranged on the ring gear carrier 11, whereas a splined shaft portion 41b of the ring gear carrier splined shaft 41, which engages in the splined hub portion 41a, is arranged on the mounting body 40.The wedges of the splined hub portion 41a and the splined shaft portion 41b are designed with respect to their radial wedge height such that the wedge flanks of the wedges can slide against each other in the radial direction, but only to such an extent that they remain in engagement with each other at the point of a circumferential ovalization in the circumferential direction of the ring gear carrier 11 (caused by the planet gear 4 rolling on the ring gear 3).

[0034] The motor vehicle has one or more such planetary gear sets 1, for example, to provide a transmission ratio between a rotor shaft of an electric drive motor of the motor vehicle and a wheel drive shaft of the motor vehicle. This means that the planetary gear set 1, in its intended installation position, forms an integral part of the motor vehicle. Therefore, the motor vehicle is, for example, a purely electric or hybrid-electric vehicle.

[0035] The planetary gear set 1 and the motor vehicle each demonstrate a particularly simple and cost-effective solution for transmitting high power and torque using a radially compact gearbox, especially without compromising comfort (such as reduced NVH quality). The core idea is to use double gear stages in a common planetary gear set, so that axial forces cancel each other out thanks to the opposing helical gearing. Thus, the bearings of the planetary gear set 1 (for example, a sun gear bearing 42, a planet carrier bearing 43, a drive shaft bearing 44, etc.) do not have to absorb any gear forces, resulting in exceptionally high efficiency for the planetary gear set 1.Additional efficiency gains are achieved through the planetary bearing arrangement using tapered roller bearings 21, 22, which eliminates the need for thrust washers, thus reducing the number of components in the planetary gear set 1. The assembly and alignment of the planetary gear parts 4a, 4b are facilitated by the chosen connection of the ring gear 3 to the ring gear carrier 11. Integrated lubrication ensures optimal oil supply to the gear teeth and bearings of the planetary gear set 1. Reference symbol list 1 planetary gear 2 sun wheel 2a first sun gear part 2b second sun wheel part 3. Ring gear 3a first ring gear part 3b second ring gear part 4 planetary gear 4a first planetary gear part 4b second planetary gear part 5 planetary gear bolts 6 planetary gear carriers 7 Centering sleeve 8 Drive shaft 9 Sun gear spline 10 Bundmutter 11 Hollow wheel carrier 12 Ring gear spline teeth 13 Clamping ring 14 Clamping ring groove 15 Centering sleeve opening 16 planetary gear shoulder 17 Centering sleeve end face 18 planetary gear gap 19 Spacing device 20 spacer collars 20a Spacer collar proportion 20b Spacer collar proportion 21 first tapered roller bearing 22 second tapered roller bearing 23 Safety pin 24 Axial bag opening 25 Radial oil opening 26 Outer circumferential surface of the planetary gear bolt 27 Wall area of ​​the planetary gear bolt 28 Oil supply device 29 Oil outlet opening 30 Inner area of ​​the centering sleeve 31 radial oil channel 32 axial oil supply channel 33 Oil guide plate 34 Sun gear oil channel 35 Front end of a tooth of the first sun gear part 36th tooth of the first sun gear part 37 Tooth gap of the second sun gear part 38th tooth of the second sun gear part 39 cases 40 Fasteners 41 Hollow gear carrier splined connection 41a Wedge hub share 41b Splined shaft proportion 42 Sun gear bearing 43 Planetary carrier bearing 44 Drive shaft bearing QUOTES INCLUDED IN THE DESCRIPTION

[0000] This list of documents cited by the applicant was automatically generated and is included solely for the reader's convenience. The list is not part of the German patent or utility model application. The DPMA accepts no liability for any errors or omissions. Cited patent literature

[0000] DE 10 2011 085 119 B3

[0003] DE 1 963 831 B

[0003] DE 10 2016 115 011 A1

[0003]

Claims

[1] Planetary gear (1), comprising: - a sun gear (2) with a left-handed first sun gear part (2a) and a right-handed second sun gear part (2b), - a ring gear (3) with a left-handed first ring gear part (3a) and a right-handed second ring gear part (3b), - a planetary gear (4) which is mounted on a planetary gear carrier (6) of the planetary gear (1) by means of a planetary gear bolt (5) and meshes with both the sun gear (2) and the ring gear (3), comprising: - a right-handed first planetary gear part (4a) and a left-handed second planetary gear part (4b) manufactured separately from the first planetary gear part (4a), - a centering sleeve (7), by means of which the planetary gear parts (4a, 4b) are mounted axially and rotatably relative to one another. [2] Planetary gear (1) according to claim 1, characterized bythat the centering sleeve (7) and one of the planetary gear parts (4a, 4b) are integrally connected to one another. [3] Planetary gear (1) according to claim 1 or 2, characterized by that the centering sleeve (7) is penetrated axially between the planetary gear parts (4a, 4b) by a radial centering sleeve opening (15). [4] Planetary gear (1) according to one of the preceding claims, characterized by that the planetary gear parts (4a, 4b) are axially spaced from one another via a planetary gear gap (18) by means of a spacing device (19) of the planetary gear (4), wherein the spacing device (19) comprises as spacing element or spacing elements: - the centering sleeve (7), which is axially long enough that the planetary gear parts (4a, 4b) are spaced apart from each other via the planetary gear gap (18), and / or - a spacer collar (20) arranged between the planetary gear parts (4a, 4b) which is axially as long as the planetary gear gap (18). [5] Planetary gear (1) according to one of the preceding claims, characterized by that the first planetary gear part (4a) is mounted on the planetary gear bolt (5) by means of a first tapered roller bearing (21) and the second planetary gear part (4b) is mounted on the planetary gear bolt (5) by means of a second tapered roller bearing (22). [6] Planetary gear (1) according to one of the preceding claims, characterized by that the planet gear bolt (5) and the planet carrier (6) are fixed to each other in a rotationally fixed manner. [7] Planetary gear (1) according to one of the preceding claims, characterized by in that the planetary gear bolt (5) has a central axial pocket opening (24) and a radial oil opening (25) which opens on the one hand into the axial pocket opening (24) and on the other hand at an outer circumferential surface (26) of the planetary gear bolt (5), wherein an oil outlet opening (29) of an oil supply device (28) of the planetary gear (1) is directed towards the axial pocket opening (24). [8] Planetary gear (1) according to claim 6 and 7, characterized by that only a wall portion (27) of the planetary gear bolt (5), which points radially outwards in the axial section of the planetary gear (1), is penetrated by the radial oil opening (25). [9] Planetary gear (1) according to one of the preceding claims, characterized by , that - one of the sun gear parts (2a, 2b) and a drive shaft (8) of the planetary gear (1) are connected to one another in a rotationally fixed manner by means of a sun gear spline (9), wherein the other of the sun gear parts (2a, 2b) and the drive shaft (8) are connected to one another in a materially bonded manner, or - both sun gear parts (2a, 2b) and a drive shaft (8) of the planetary gear (1) are connected to one another in a rotationally fixed manner by means of a sun gear spline (9) or - both sun gear parts (2a, 2b) and a drive shaft () of the planetary gear (1) are integrally connected to one another. [10] Planetary gear (1) according to one of the preceding claims, characterized bythat the sun gear parts (2a, 2b) are rotated relative to one another in such a way that a respective front end (35) of teeth (36) of the first sun gear part (2a) is axially inwardly located directly opposite a respective tooth space (37) of the second sun gear part (2b). [11] Planetary gear (1) according to one of the preceding claims, characterized by that the ring gear (3) and a ring gear carrier (11) of the planetary gear (1) are connected to one another in a rotationally fixed manner, wherein a housing (39) of the planetary gear (1) has a fastening body (40) which is connected to the ring gear carrier (11) in a rotationally fixed manner but is axially and / or radially movable. [12] Planetary gear (1) according to claim 11, characterized by that the ring gear carrier (11) and the fastening body (40) are connected to one another in a rotationally fixed but axially and / or radially movable manner by means of a radially movable ring gear carrier spline (41). [13] Planetary gear (1) according to claim 11 or 12, characterized by, that - one of the ring gear parts (3a, 3b) and the ring gear carrier (11) are connected to one another in a rotationally fixed manner by means of a ring gear spline (12), wherein the other of the ring gear parts (3a, 3b) and the ring gear carrier (11) are connected to one another in a materially bonded manner, or - both ring gear parts (3a, 3b) and the ring gear carrier (11) are connected to each other in a rotationally fixed manner by means of a ring gear spline (12) or - both ring gear parts (3a, 3b) and the ring gear carrier (11) are integrally connected to one another. [14] Motor vehicle with a planetary gear (1) designed according to one of the preceding claims.

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