Planetary gear with bridging cup and drive unit with such a planetary gear

Abstract

Planetary gear with a bridging cup and drive unit with such a planetary gear. The invention relates to a planetary gear with a planetary gear set (1) comprising a sun wheel (2) which is configured to be connected in a driving action with a drive machine (10) and a ring gear (3) which is configured to be connected in a driving action with a driven shaft (15) and a planet carrier (4) with a plurality of planet wheels (5) which are arranged at least indirectly thereon. The planet carrier (4) is statically fixed at a housing (7) and is connected in an anti-rotation manner with the housing (7) via a bridging cup (6) which axially spans the planetary gear set (1).

Description

Technical Field

[0001] This invention relates to a planetary transmission with a bridging cup. It also relates to a drive unit for a motor vehicle drive system incorporating such a planetary transmission. Background Technology

[0002] For example, document DE19915926A1 discloses a drive system for a motor vehicle, comprising: an internal combustion engine with a crankshaft connected to the input shaft of a shift transmission via an intermediate clutch; and an electric motor having a stator and a rotor disposed in the drive system. The electric motor is operatively connected to the crankshaft and / or the input shaft of the transmission via a reduction gear to reduce the motor speed. The reduction gear is configured as a planetary transmission having a sun gear, a ring gear, and a number of planet gears. The sun gear is configured as the drive shaft of the planetary transmission, the ring gear is configured as the driven shaft of the planetary transmission, and the planet carrier is connected to the housing in a rotationally inverse manner. Summary of the Invention

[0003] The objective of this invention is to create an improved planetary transmission for a drive unit in a motor vehicle drive system. In particular, the planetary transmission and the drive unit thereby created should be constructed to be more compact. This objective is achieved by the features of independent claims 1 and 10. Advantageous embodiments are described in the subject matter of the dependent claims, the following description, and the accompanying drawings.

[0004] According to a first aspect, a planetary transmission device with a planetary gear set is proposed. The planetary transmission device includes a sun gear configured to be connected to a drive motor in a driving action. Furthermore, the planetary transmission device includes a ring gear configured to be connected to a driven shaft in a driving action. The planetary transmission device also includes a planet carrier with a plurality of planet gears arranged at least indirectly thereon. The planet carrier is statically fixed to a housing. For this purpose, the planet carrier is axially connected to the housing to resist relative rotation via a bridging cup surrounding the planetary gear set.

[0005] Therefore, the bridging cup is arranged in a functional manner between the housing and the planet carrier so as to statically fix the planet carrier to the housing. Thus, the planet carrier is permanently connected to the housing against relative rotation. This is achieved by ensuring that the planetary transmission has no clutch between the housing and the planet carrier that can be disengaged during operation of the planetary transmission.

[0006] The planetary gears mesh with the sun gear on one side and the ring gear on the other, and are rotatably supported on the planet carrier. The bridging cup extends from the driving side of the planetary gear set to the driven side, thereby axially circumferentially surrounding the planetary gear set. In this sense, "axial circumferentially surrounding" means that the bridging cup extends axially along the outer periphery of the planetary gear set from one end to the other. Specifically, the bridging cup has axially extending, substantially sleeve-shaped sections and radially extending, substantially annular disc-shaped sections, which are interconnected.

[0007] Preferably, the planetary carrier and the bridging cup are connected in a form-locking manner. This allows them to be coupled to each other in a releasable manner. This significantly simplifies the assembly of the planetary transmission. Thus, during planetary transmission assembly, the planetary gear set can be introduced into the bridging cup from one end, whereby the bridging cup and planetary carrier are connected in a form-locking manner, either directly or subsequently.

[0008] According to one embodiment, the bridging cup has a first section for anti-rotational connection to the planetary carrier and a second section for anti-rotational connection to the housing. Preferably, the first section is substantially sleeve-shaped and extends axially from one end of the planetary gear set to the other end along the outer periphery of the planetary gear set. Thus, a connection with the planetary carrier can be formed at the free end of the first section. Preferably, the second section is substantially annular disc-shaped and extends substantially radially along one end of the planetary gear set. Thus, a connection with the housing can be formed at the free end of the second section. In other words, the first and second sections can be arranged at axially opposite ends of the bridging cup, thereby optimizing the use of available installation space.

[0009] In other words, the bridging cup is a component of the planetary gear set, which axially surrounds the planetary gear set and statically fixes the planet carrier to the housing. The bridging cup is specifically composed of a sleeve-shaped section extending along the outer periphery of the planetary gear set and an annular disc-shaped section arranged at the end of the planetary gear set. The bridging cup ensures a compact configuration and enables a stable connection between the planet carrier and the housing.

[0010] Preferably, the first segment has a larger diameter than the second segment. This optimizes the connection between the planetary carrier and the housing, particularly saving installation space. Preferably, the profile of the bridging cup substantially follows the profile of the gear set, such that the gear set is surrounded by the bridging cup at least on its outer periphery and one of its two end sides. Preferably, the first and second segments are connected as a single piece. Therefore, the bridging cup can be constructed as a single piece. The bridging cup can then be manufactured by primary forming and / or machining methods. For example, the bridging cup is constructed as an aluminum die casting. Alternatively, the first and second segments can be connected by material locking (e.g., by welding). Thus, the first segment can be made of sheet metal, while the second segment can be manufactured as a sub-component by shaping, primary forming, and / or machining methods.

[0011] According to one embodiment, the bridging cup includes a first section with internal teeth for connecting the bridging cup to the planet carrier in a form-locking manner and at least resisting relative rotation. The planet carrier, in particular, has external teeth corresponding to the internal teeth of the first section, thereby completing this connection. Preferably, the internal teeth are constructed at the free end of the first section. Using these teeth facilitates the assembly of the planet carrier into the bridging cup.

[0012] The second section may have at least one hole, preferably multiple holes, for each fastening element to pass through, these fastening elements for connecting the bridging cup to the housing in a way that prevents relative rotation. The fastening elements are, for example, screws or bolts. The housing has additional holes corresponding to the fastening elements, such as threaded holes, thereby completing this connection. In particular, the at least one hole is constructed in a reinforced region of the second section. The number of holes in the second region of the bridging cup may vary depending on requirements. Specifically, these holes are constructed axially in the second section and are evenly distributed in the circumferential direction.

[0013] The second section may have external teeth for connecting the bridging cup to the housing in a form-locking manner and at least in a way that resists relative rotation. The housing, in particular, has internal teeth that correspond to and cooperate with the external teeth of the second section, thereby achieving this connection that resists relative rotation. In particular, the external teeth of the bridging cup are constructed in the reinforcing region of the second section.

[0014] According to one embodiment, at least one notch is constructed in the first section for lubricant to pass through. Preferably, multiple such notches are provided. In particular, at least one notch is arranged to allow lubricant to drain from the bridging cup in the assembled and operational-ready state of the planetary gear set. Thus, at least one notch can be arranged on the bottom side of the bridging cup. Lubricant guided through the planetary gear set for lubrication and cooling can then flow away from the bridging cup via the notch.

[0015] According to one embodiment, the bridging cup has at least one positioning element for accurately aligning the bridging cup with respect to the housing. This simplifies the assembly of the bridging cup in the correct position relative to the housing, thereby ensuring that the bridging cup always occupies a predetermined position relative to the housing. The positioning element is specifically configured to align the bridging cup with respect to the housing in the circumferential and / or radial directions. Preferably, the positioning element is constructed in a second section and configured to cooperate with another corresponding positioning element constructed in the housing. Correct positioning of the bridging cup in the housing is particularly advantageous when at least one notch for lubricant penetration is constructed in a specific region of the bridging cup.

[0016] The positioning element of the bridging cup can be configured as a recess at the bridging cup. Therefore, to align the bridging cup, the pin can be guided both into the recess at the bridging cup and into the hole at the housing. This recess can be easily manufactured. Thus, this positioning can be achieved very economically and efficiently.

[0017] The positioning element of the bridging cup can be configured as teeth at the bridging cup. The teeth can be non-uniformly constructed so that they can only mate with corresponding teeth at the housing when the bridging cup is correctly positioned. By using teeth as positioning elements, positioning can be achieved in a single assembly step. For this purpose, the bridging cup can have tooth gaps within the teeth for aligning the bridging cup at the housing. These tooth gaps are configured to be distinct from all other tooth gaps in the bridging cup, for example, their size is twice that of the other tooth gaps. In particular, these tooth gaps are filled with complementary teeth of the mating teeth at the housing. Here, the positioning element or tooth gap can be formed, particularly by the external teeth at the second section of the bridging cup.

[0018] According to one embodiment, the planetary transmission includes the drive motor, wherein the drive motor is configured as an electric drive motor. Here, at least the planetary gear set is radially arranged within the drive motor. Thus, at least the planetary gear set (i.e., the sun gear, the ring gear, and the planet gears disposed therebetween and housed on the planet carrier) overlaps axially and is arranged within the drive motor. This radial stacking of the drive motor and the planetary gear set saves axial installation space. Preferably, the bridging cup is also radially arranged within the drive motor.

[0019] The sun gear is preferably configured as the drive shaft of the planetary gear set and is designed to feed drive power from the electric drive motor. The ring gear is configured as the driven shaft of the planetary gear set. Therefore, the ring gear can be coupled at least indirectly (e.g., via a ring gear carrier) to the driven shaft of the planetary transmission or another transmission stage. However, preferably, the planetary gear set does not include any other planetary gear sets. The planet gears mesh with the sun gear and the ring gear, wherein the planet carrier, which houses the planet gears via planet gear pins, is stationary and connected to the housing or a component fixed to the housing via a bridging cup.

[0020] The rotor of the electric drive is preferably permanently connected to the sun gear in a way that prevents relative rotation. This connection can be directly configured, allowing the planetary transmission to form a very compact drive unit. Here, the rotor and sun gear always have the same direction and speed of rotation. This can be achieved by ensuring that the planetary transmission does not have any clutch and / or gear ratio mechanism between the rotor and sun gear that can be disengaged during the operation of the planetary transmission.

[0021] According to a second aspect, a drive unit for a motor vehicle drive system is provided, wherein the drive unit includes the planetary transmission device described in the first aspect. Here, the drive unit includes the housing and the electric drive motor, which is arranged cooperatively with the planetary transmission device within the interior space of the housing. The definitions and statements above regarding the technical effects, advantages, and preferred embodiments of the planetary transmission device according to the present invention can also be applied analogously to the drive unit according to the present invention.

[0022] Preferably, the motor vehicle is configured as an electric vehicle or a hybrid vehicle. According to the implementation scheme, the motor vehicle drive system can be purely electric or can be driven in conjunction with an internal combustion engine.

[0023] The drive unit can be a hybrid power module for a motor vehicle's hybrid drive system. The drive unit can be configured to be located at the power input end of the multi-speed transmission of the drive system. Thus, the drive unit can be positioned between the internal combustion engine and the multi-speed transmission in the power flow of the drive system. Therefore, the drive unit can at least temporarily replace or cooperate with the internal combustion engine to drive the vehicle.

[0024] Similarly, the drive unit can be used alone or in conjunction with one or more other electric drive units to drive the vehicle's drive system. Thus, an internal combustion engine can be eliminated from the drive system.

[0025] The drive unit can be configured to use an electric drive motor for both driving and energy recovery as needed. The drive unit can have a separate control and regulation unit for the electric drive motor. The drive unit can have a separate inverter and / or converter for feeding power to the electric drive motor. The drive unit can have a separate lubrication circuit for lubricating the planetary transmission. The drive unit can have a separate heat exchanger for cooling the lubricant in the planetary transmission. The drive unit can be single-gear configured, meaning that the drive unit constantly provides a single preset gear ratio between the input and output ends. The drive unit can be flanged to a multi-gear transmission in the vehicle's drive system or configured to be flanged to such a transmission, particularly on the driven side of the drive unit. The multi-gear transmission can be configured as a countershaft type transmission. The drive unit can be flanged to an internal combustion engine in the vehicle's drive system or configured to be flanged to such an internal combustion engine, particularly on the drive side of the drive unit. The drive unit can have a clutch housing for accommodating a disengaged clutch. The clutch housing can be formed through the housing of the drive unit. The clutch housing can be configured to be flanged to the internal combustion engine. The internal space of the clutch housing for accommodating the disengaged clutch can be hermetically isolated from the internal space of the planetary gear set accommodating the drive unit. The disengaged clutch can be configured to selectively couple and decouple the drive unit from the internal combustion engine in terms of drive technology.

[0026] Preferably, the drive unit comprises only the aforementioned planetary gear set and only the aforementioned electric drive motor. That is, the drive unit does not have any additional planetary gear sets or any additional electric drive motors for driving the motor vehicle. Preferably, the drive unit does not have any switchable clutch. Through these measures, the drive unit can be implemented very compactly.

[0027] In principle, the present invention may also relate to a motor vehicle drive system having all or some of the above-described components. The present invention may also relate to a motor vehicle having such a drive system. Attached Figure Description

[0028] Advantageous embodiments of the present invention will now be described with reference to the accompanying drawings, wherein the same or similar elements are given the same reference numerals. In the drawings:

[0029] Figure 1 A partial schematic diagram of a planetary transmission mechanism is shown;

[0030] Figure 2 It shows that according to Figure 1 A schematic longitudinal sectional view of the implemented planetary transmission device;

[0031] Figure 3 It shows that according to Figure 1 and Figure 2 A 3D diagram of the bridging cup;

[0032] Figure 4 It shows that according to Figure 3 Another three-dimensional view of the bridging cup;

[0033] Figure 5 It shows that according to Figure 1 and Figure 2 A schematic longitudinal sectional view of another part of the planetary transmission mechanism;

[0034] Figure 6 An embodiment according to another embodiment is shown. Figure 1 A schematic cross-sectional view of a portion of the planetary transmission device shown;

[0035] Figure 7 An embodiment according to another embodiment is shown. Figure 1 A partial schematic longitudinal sectional view of the planetary transmission device shown; and

[0036] Figure 8 An embodiment according to another embodiment is shown. Figure 1 A schematic longitudinal sectional view of a portion of the planetary transmission device shown. Detailed Implementation

[0037] Figure 1 A planetary transmission with an electric drive 10 is shown. The electric drive 10 has a stator 11 and a rotor 12. The planetary transmission also includes a planetary gear set 1 radially arranged within the drive 10. The planetary gear set 1 includes a sun gear 2, a ring gear 3, and a planet carrier 4 with a plurality of planet gears 5 rotatably arranged thereon.

[0038] The main axis of rotation of the planetary gear set 1 is marked with reference numeral 9. This axis of rotation 9 also forms the longitudinal axis of the planetary transmission. Therefore, spatial terms such as "axial," "radial," or "in the circumferential direction" refer to this axis of rotation 9 unless otherwise specified.

[0039] Here, the planet carrier 4 of the planetary gear set is statically fixed to the housing 7 via the bridging cup 6. The planet carrier 4 and the bridging cup 6 are thus always connected to the housing 7 against relative rotation. The bridging cup 6 surrounds the planetary gear set 1 and extends from the first end side of the planetary gear set 1 to the opposite second end side of the planetary gear set 1.

[0040] Planetary transmissions are preferably configured as drive units for motor vehicle drive systems. Such drive units can be used in hybrid powertrains where an internal combustion engine is configured as a separate drive source. In this case, the drive unit can be constructed as a hybrid module. For this purpose, the hybrid module can be located at the power input of a multi-speed transmission. However, the drive unit can also be used as the sole drive source in a motor vehicle drive system. The drive unit then provides at least temporary electric drive for the drive system.

[0041] The housing 7 may be the housing of the drive unit and enclose the planetary transmission, such that the electric drive motor 10 and the planetary gear set 1 are arranged within the interior space of the housing 7. Preferably, the planetary transmission and the drive unit created therefrom have only the electric drive motor 10 and the planetary gear set 1, that is, no additional electric drive motor and planetary gear set.

[0042] Here, the sun gear 2 is directly and anti-rotationally connected to the rotor 12 of the drive motor 10. Therefore, no transmission ratio mechanism or clutch mechanism is arranged between them. Thus, the sun gear 2 and the rotor 12 always have the same direction of rotation and speed. The gear ring 3 is also directly and anti-rotationally connected to the driven shaft 15. Therefore, no transmission ratio mechanism or clutch mechanism is arranged between them. Thus, the gear ring 2 and the driven shaft 15 always have the same direction of rotation and speed.

[0043] Driven shaft 15 preferably forms the driven end of the drive unit. When the drive unit is used as a hybrid power module, driven shaft 15 can serve as a transmission input shaft connected to a multi-speed transmission or be coupled to such a transmission input shaft at least in a manner resistant to relative rotation.

[0044] The sun gear 2 and ring gear 3 rotate at different speeds about the axis of rotation 9, while the planet carrier 4 and bridging cup 6 are statically fixed to the housing 7, thereby preventing their rotation. The bridging cup 6 enables a particularly compact structure for the planetary gear set 1, i.e., the bridging cup surrounds the planetary gear set 1, and statically fixes the planet carrier 4, which extends from the planetary gear set 1 on the driving side, to the housing 7 on the driven side. Furthermore, this allows for a favorable axial overlap between the planetary gear set 1 and the drive unit 10, thereby saving axial installation space in particular.

[0045] Figure 2 It shows that according to Figure 1 A partial longitudinal sectional view of the designed planetary gear transmission. The bridging cup 6 has a first section 20 with internal teeth 21. The internal teeth 21 engage with the complementary external teeth on the planet carrier 4 to establish a form-locking connection. Furthermore, the bridging cup 6 has a second section 30 with external teeth 31. The external teeth 31 engage with the complementary internal teeth on the housing 7 to establish a form-locking connection. The outline of the bridging cup 6 substantially follows the outline of the planetary gear set 1, such that the planetary gear set 1 is surrounded by the bridging cup 6 at least on its outer periphery and end sides.

[0046] The first segment 20 of the bridging cup 6 (in the example shown, the internal teeth 21 are located in the first segment) has a larger diameter than the second segment 30 (in the example shown, the external teeth 31 are located in the second segment). The teeth 21 and 31 are preferably configured as insert teeth, thereby simplifying the assembly of the bridging cup 6 on the housing 7 and the planetary carrier 4. The first segment 20 and the second segment 30 are connected as a single piece. Therefore, the bridging cup 6 has a single-piece construction.

[0047] Multiple planetary gear pins 16 are housed at the planetary carrier 4, which is fixed to the housing, to resist relative rotation. For example... Figure 2 As exemplarily shown, each of these planetary gear pins rotatably carries one of the planetary gears 5 of the planetary gear set 1. To support the planetary gear 5, a radial bearing, such as a needle roller bearing or a roller bearing, can be provided between the planetary gear pin 16 and the planetary gear 5. Similarly... Figure 2 As exemplarily shown, the planetary gear pin 16 can be protected from rotation by means of a pin that is radially guided through the planet carrier 4 and the planetary gear pin 16.

[0048] In addition, from Figure 2 It can be seen that the gear ring 3 is preferably directly anti-rotationally connected to the driven shaft 15 via the gear ring holder 14. The rotor 12 has a rotor holder 13, which is rotatably supported on the housing 7 via at least one rolling bearing 17. The rotor 12 is directly anti-rotationally connected to the sun gear 2 via the rotor holder 13 (see...). Figure 1 ).

[0049] A radial orifice 19 is configured to allow lubricant to pass through the sun gear 2, and a lubricant distribution device 18 is arranged radially outward therefrom. The lubricant distribution device 18 is fluid-guiding and statically positioned at the planetary gear pins 16 and / or the planet carrier 4. Thus, the lubricant distribution device 18 is also fixed to the housing, i.e., it does not rotate. The lubricant distribution device 18 is arranged with an inlet opening on the outer periphery of the sun gear 2, such that the lubricant ejected from the radial orifice 19 is directly collected by the lubricant distribution device 18. The lubricant distribution device 18 guides the collected lubricant through outlet openings of a guide vane device 18 configured for this purpose, these outlet openings being transverse to the inlet opening. Each outlet opening is fluidly connected to a central hole 22 in each planetary gear pin 16. This allows the collected lubricant to be guided via the central hole 22 to the rotatably supported planetary gear 5. In particular, multiple circumferentially distributed radial orifices are arranged at each planetary gear pin 16, causing the lubricant to tend to flow downwards from the central hole 22 due to gravity. In this way, the toothed areas between the planetary gears 5, the sun gear 2, and the ring gear 3 are efficiently lubricated and cooled. Lubricant can be introduced into the stationary planetary gear pins 16 without additional equipment, thereby further reducing assembly costs and saving weight, materials, and installation space.

[0050] Figure 3 and Figure 4 It shows that according to Figure 1 and Figure 2 Different perspective views of the bridging cup 6 are shown in these figures. The cup-shaped structure of the bridging cup 6 can be seen from these figures. The first section 20 is essentially sleeve-shaped and is configured to extend axially from one end of the planetary gear set 1 to the other end along the outer periphery of the planetary gear set 1. Internal teeth 21 for connecting the planet carrier 4 to the bridging cup 6 are constructed at the free end of the first section 20. The second section 30 is essentially annular disc-shaped and is configured to extend substantially radially along one end of the planetary gear set 1. External teeth 31 for connecting the bridging cup 6 to the housing 7 are constructed at the free end of the second section 30. The first section 20 and the second section 30 are integrally connected, making the bridging cup 6 a single-piece construction. The bridging cup 6 can be formed, for example, by primary forming, especially as an aluminum die-casting.

[0051] according to Figure 3 and Figure 4 The bridging cup 6 also has at least one positioning element 34, here in the form of a recess 34, which is used to accurately align the bridging cup 6 at a predetermined position within the housing 7. (Reference) Figure 5 The empty space 34, which is described further, is constructed in the second section 30.

[0052] according to Figure 4 The bridging cup 6 in the first section 20 also has one or more notches 8 for lubricant to pass through. The notches 8 are configured to guide the lubricant through the planetary gear set 1 and allow it to flow away from the bridging cup 6, thereby preventing lubricant accumulation in the bridging cup 6 and reducing lubricant splashing losses in the planetary gear set 1. For this purpose, in the assembled and operational-ready state of the planetary gear transmission, the notches 8 are downward-facing and / or positioned on the bottom side of the bridging cup 6.

[0053] Figure 5 Detailed illustrations Figure 1 and Figure 2This is a longitudinal sectional view of another portion of the planetary transmission shown. This portion shows the lower part of the planetary transmission in its assembled and operational-ready state. A recess 34 is constructed in the second section 30 of the bridging cup 6 and serves to align the bridging cup 6 with the housing 7. Here, an additional positioning element in the form of a pin 35 is arranged in this recess. The pin 35 further penetrates a hole 36 provided for this purpose in the housing 7 and is thereby secured to the housing 7. In addition, the bridging cup 6 is always accurately aligned with the housing 7. Thus, the recess 34, pin 35, and hole 36 serve as positioning elements for correctly aligning the bridging cup 6 with the housing 7. This positioning causes the notch 8 of the bridging cup 6 to be arranged on the lower side of the planetary transmission in the operational-ready state. This allows the lubricant guided through the planetary gear set 1 to flow downward from the bridging cup 6.

[0054] Figure 6 It shows Figure 1 The diagram shows a partial transverse sectional view of an alternative embodiment of the planetary transmission within the second section 30 of the bridging cup 6. This partial view shows a portion of the external teeth 31 of the bridging cup 6. (Alternatively...) Figure 5 The pin 35 and the recess 34 shown here have a special toothed portion with a toothed gap 35 provided for the external toothed portion 31. Here, the external toothed portion 31 and the toothed gap 35 serve as positioning elements for correctly aligning the bridging cup 6 with the housing 7. The toothed gap 35 has a different shape than the other toothed gaps of the external toothed portion 31. The toothed gap 35 matches the complementary tooth of the mating toothed portion (internal toothed portion) at the housing 7 and is filled by the tooth in the assembled state. In this way, the tooth forms the positioning element to which the housing 7 belongs. In this way, the bridging cup 6 can only be introduced into the housing 7 at a predetermined position, wherein the notch 8 of the bridging cup 6 is lower. In addition, the description of the foregoing figures also applies to the following figures. Figure 6 The implementation method.

[0055] Figure 7 An illustration according to another embodiment is shown. Figure 1 The diagram shows a partial cross-sectional view of the planetary transmission device. Accordingly, the bridging cup 6 has a two-piece construction. The first section 20 and the second section 30 of the bridging cup 6 are connected to each other by a material-locking method. Thus, the first section 20 can be made of sheet metal, and the second section 30 can be manufactured as a secondary component, for example, by machining. Here, a weld 37 is constructed between the two radially extending regions of sections 20 and 30 in the bridging cup 6. Furthermore, the descriptions of the foregoing figures also apply to the following... Figure 7 The implementation method.

[0056] Figure 8 An embodiment according to another embodiment is shown. Figure 1The diagram shows a partial schematic cross-sectional view of the planetary transmission device. Here, the bridging cup 6 is, for example, a single-piece construction. The bridging cup 6 has a first section 20 with internal teeth 21 for engagement with the planet carrier 4. A plurality of holes 32 are provided in the second section 30. These holes 32 are preferably arranged evenly in the circumferential direction. These holes are for through which various fastening elements 33 pass, which are used to engage the bridging cup 6 with resistance to relative rotation to the housing 7. Only one of the fastening elements 33 is shown here. The fastening element 33 is constructed as a screw, which is screwed into a threaded hole 38 in the housing 7. Thus, the bridging cup 6 is securely screwed to the housing 7. Due to the relative to the Figure 2 This embodiment can omit the external teeth 31 at the bridging cup 6, and it has advantages in manufacturing the bridging cup 6 at the housing 7. Here, in Figure 8 It can also be seen that the rolling bearing used to support the rotor of the electric drive motor is simultaneously clamped between the housing 7 and the bridge cup 6, thereby fixing the rolling bearing axially. Furthermore, the descriptions in the foregoing figures also apply to the following... Figure 8 The implementation method.

[0057] List of reference numerals

[0058] 1 Planetary gear set

[0059] 2. Sun Gear

[0060] 3 Gear ring

[0061] 4 Planetary Carrier

[0062] 5 Planetary Wheels

[0063] 6 Bridging Cups

[0064] 7. Housing

[0065] 8 gaps

[0066] 9. Rotation axis

[0067] 10 drive units

[0068] 11 Stator

[0069] 12 rotors

[0070] 13 Rotor frame

[0071] 14 Gear Carrier

[0072] 15 Driven Shaft

[0073] 16 Planetary gear pins

[0074] 17 Rolling bearings

[0075] 18 Lubricant dispensing equipment

[0076] 19 Radial holes

[0077] 20 First Section

[0078] 21 Internal teeth

[0079] 22 Central Hole

[0080] 30 Second Section

[0081] 31 External teeth

[0082] 32 holes

[0083] 33 Fastening elements

[0084] 34. Positioning element (reserved area)

[0085] 35. Positioning elements (pins, backlash)

[0086] 36 holes

[0087] 37 Weld

[0088] 38 threaded hole

Claims

1. A planetary transmission device with a planetary gear set (1), the planetary gear set comprising: Sun gear (2), which is configured to be connected to the drive motor (10) in terms of driving action; and a gear ring (3), which is configured to be connected to the driven shaft (15) in terms of driving action; and a planet carrier (4) having a plurality of planet gears (5) arranged at least indirectly on the planet carrier, wherein the planet carrier (4) is statically fixed at the housing (7), characterized in that the planet carrier (4) is connected to the housing (7) against relative rotation via a bridging cup (6) axially surrounding the planet gear set (1).

2. The planetary transmission device according to claim 1, wherein, The bridging cup (6) has a first section (20) for connecting to the planetary carrier (4) and a second section (30) for connecting to the housing (7).

3. The planetary transmission device according to claim 2, wherein, The first segment (20) has a larger diameter than the second segment (30).

4. The planetary transmission device according to claim 2 or 3, wherein, The first section (20) and the second section (30) are arranged at the axially opposite ends of the bridging cup (6).

5. The planetary transmission device according to any one of claims 2 to 4, wherein, The first section (20) has internal teeth (21) to allow the bridging cup (6) to be connected to the planetary carrier (4).

6. The planetary transmission device according to any one of claims 2 to 5, wherein, The second section (30) has external teeth (31) to allow the bridging cup (6) to engage with the housing (7), and / or has at least one hole (32) for a fastening element (33) to pass through.

7. The planetary transmission device according to any one of claims 2 to 6, wherein, At least one notch (8) is constructed in the first section (20) for lubricant to pass through.

8. The planetary transmission device according to any one of the preceding claims, wherein, The bridging cup (6) has at least one positioning element (34, 35) for aligning the bridging cup (6) with respect to the housing (7).

9. The planetary transmission device according to any one of the preceding claims, wherein the planetary transmission device has the drive motor (10), wherein, The drive is an electric drive (10), and the planetary gear set (1) is radially arranged within the drive (10).

10. A drive unit for a motor vehicle drive system, the drive unit having a housing (7) and an electric drive motor (10) disposed within the interior space of the housing and a planetary transmission device disposed within the interior space, characterized in that, The planetary transmission device is constructed according to any one of claims 1 to 9.

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