DE102017129591A1 - Assembly for a gear arrangement and gear arrangement with the module - Google Patents

Abstract

In transmissions, subassemblies must be supplied with lubricant. For this purpose, various concepts are known, how individual components or complete subassemblies are supplied. For example, dry sump or wet sump lubrication is used. It is also necessary to provide sufficient lubrication in planetary gears. An assembly (1) for a gear arrangement (2) is proposed with a sun gear (5), with a plurality of planet gears (6), the planet wheels (6) with the sun gear (5) are in engagement, with a planet carrier (8), wherein the planetary gears (6) on the planet carrier (8) in a partial circle radius (TR) about a major axis (H) are arranged, wherein the planet carrier (8) when rotating about the major axis (H) on the outside defines a carrier rotational space radius (TRR), the planet wheels (6) in their entirety define a wheel rotational space radius (RRR) when rotating about the major axis (H) on the outside, the difference between the wheel rotation space radius (RRR) and the carrier rotation space radius (TRR) defines a dip distance (E), wherein half the tip circle diameter of the planet wheels (6) defines a wheel radius (RR), the Amount of immersion distance (E) is less than half of the wheel radius (RR).

Description

The invention relates to an assembly for a transmission assembly having the features of the preamble of claim 1. The invention further relates to the transmission assembly with the assembly.

In transmissions, subassemblies must be supplied with lubricant. For this purpose, various concepts are known, how individual components or complete subassemblies are supplied. For example, dry sump or wet sump lubrication is used. For planetary gearboxes it is also necessary to provide adequate lubrication.

In this context, the DE 10 2012 202 453 A1 in a planetary gear, to provide special inlet openings for a lubricant.

In the publication JP 600 87008 B2 , which probably forms the closest prior art, a planetary gear is shown with a planet carrier, wherein the planet carrier is formed in several parts and a plurality of mutually parallel arranged disc sections, which are connected to each other via wedge-shaped axial sections. Between the axial sections of the planet gears are arranged.

It is an object of the present invention to provide an assembly for a gear assembly, which is characterized by improved lubrication. This object is achieved by an assembly having the features of claim 1 and by a gear assembly having the features of claim 10. Preferred or advantageous embodiments will become apparent from the dependent claims, the following description and the accompanying drawings.

The invention relates to an assembly which is suitable and / or designed for a gear arrangement. The module is designed in particular as a planetary drive or as a planetary gear. In particular, this is realized as a Stirnradplanetentrieb or Stirnradplanetengetriebe. It is preferred that the wheels in the assembly are at least partially or all formed as spur gears.

The gear arrangement is preferably suitable and / or designed for a vehicle. In particular, the gear arrangement serves to transmit a traction torque for driving the vehicle. Particularly preferably, the gear arrangement is formed as part of a drive train of the vehicle. As a traction motor, the gear arrangement particularly preferably has an electric motor. For example, the gear assembly is formed as an electrical axle for the vehicle.

The assembly has at least or a single sun gear, wherein the sun gear can rotate about or define a major axis of the assembly. Further, the assembly has a plurality of planet gears, wherein the planet gears are in engagement with the sun gear. The planet gears each have an axis of rotation, which are arranged parallel to the main axis, but are distributed in a pitch radius around the main axis.

The assembly has a planet carrier, wherein the planetary gears are arranged on the planet carrier and / or are supported by this. In particular, the planet gears are mounted on the planet carrier. The planetary gears are in particular bolt or shaft bearings in or on the planet carrier.

During a rotation of the planetary carrier defines this by its radial outer side, a Trägerrotationsraumradius. The planet carrier is thus considered as a rotation body, wherein the radial outer side of the rotation body defines the Trägerrotationsraumradius.

Looking at the planetary gears in their entirety in the rotation about the major axis, they define a Radrotationsraumradius by the radial outer side. The planetary gears are thus considered as rotation bodies about the main axis, wherein the radial outer side of the rotation body defines the Radrotationsraumradius.

The difference between the Radrotationsraumradius and the Trägerrotationsraumradius defines a dip distance, especially for the planetary gears. The immersion distance is defined as positive if the planetary gears protrude beyond the contour of the planetary carrier and / or over the carrier rotational space radius. The dip distance is defined as negative when the planetary gears are located in the planetary carrier and / or are reset in their entirety relative to the carrier rotational space radius.

For purposes of definition, it is determined that half the tip circle diameter of the planet gears defines a wheel radius. Under the tip diameter diameter is understood, which is formed by the tooth tips of the teeth of the respective planetary gear.

In the context of the invention, it is proposed that the amount of immersion distance is less than half the radius of the wheel. In other words the Radrotationsraumradius and the Trägerrotationsraumradius less than half of the wheel radius.

The radii or diameters described are preferably viewed or measured in a common radial plane.

It is a consideration of the invention that the planetary gears receive a housing in the radial direction, which allows a homogeneous rotation of the assembly through an oil sump. This enclosure reduces the projected area of the planetary gears that protrude beyond the planetary carrier so that a more homogeneous rotational movement through the oil sump can take place. As a result, losses, in particular churning losses are reduced by a pulse-like immersion of the planetary gears in a rotation of the planet carrier. At the same time can be displaced by the volume of the planet carrier oil in the oil sump, so that the necessary amount of oil can be reduced to achieve a predetermined oil level. The reduced oil volume also reduces the associated churning losses.

After the beneficial effect of the invention gradually increases, the smaller the amount of dip spacing is formed, it is particularly preferred that the amount of dip distance be less than 1/4, preferably less than 1/8 and most preferably less than 1/16 of the wheel radius is.

A further improvement can be achieved if the amount of immersion distance is set in comparison with the simple distance between the tip circle diameter and the root diameter of the planet gears as a reference value. The simple distance is the difference between the corresponding radii. The root diameter of the planetary gears is preferably given by the diameter, which is given by the lowest point of the tooth roots. Alternatively or additionally, the amount of the immersion distance is set in a comparison with the tooth height of the planet gears as a reference value. It is preferably provided that the amount of the immersion distance is set to be smaller than or equal to three times, preferably twice again, and in particular as the simple reference value.

In a structural embodiment, it is provided that the planet gears are arranged radially projecting in the planet carrier. In this structural embodiment, it is particularly preferred that the assembly has a ring gear, wherein the planet gears mesh with the ring gear. In other words, the planet gears are preferably only so far over the planet carrier, so that engagement between the planet gears and ring gear is enabled. It is therefore preferred that the amount of dip distance be greater than the simple distance between the tip circle diameter and the root diameter of the planetary gears and / or greater than the tooth height of the teeth of the planet gears.

In an alternative structural design, the planetary gears in the planet carrier are set back radially or flush. In the alternative structural design, the planet gears are radially outward in no meshed contact with another transmission component. In particular, no ring gear is provided. The alternative structural design further reduces the pulse-like immersion of the planet gears, so that the churning losses are further reduced.

In a preferred embodiment, it is provided that the planetary gears are each part of a multiple planetary gear. For example, it is formed multiple times planetary gear as a Doppelplanetenrad. The planetary gears described above have the largest tip diameter in the multi-planetary gear. In the development, the other planetary gears of the multiple planet gears may be radially outward in a meshing contact with one or more other transmission components. For example, the other planetary gears of the multiple planet gears mesh with a ring gear, which preferably forms a component of the assembly.

Despite the flush or recessed arrangement of the planet gears in the planet carrier, it is preferred that the planet carrier is open in the radial direction, so that the planetary gears can dip in a radial direction in one or the oil sump.

Preferably, the planet carrier has webs, wherein recordings for the planetary gears are formed between the webs. At least one of the webs is disposed adjacent to one of the planetary gears. Preferably, each planetary gear is associated with an adjacent web, as will be described below.

It is preferred that the web has a Leitflächenabschnitt which faces the adjacent planetary gear. The guide surface portion is formed as a surface or as a surface portion. Between the Leitflächenabschnitt and the adjacent planetary gear an annular gap area is formed. The annular gap region preferably has a radially inner and a radially outer boundary, which are arranged coaxially and / or concentrically with one another. The annular gap region is aligned coaxially and / or concentrically with the axis of rotation of the adjacent planetary gear. The radially outer boundary is through formed the Leitflächenabschnitt. The radially inner boundary is formed by the interference contour of the adjacent planetary gear. The interference contour is formed as a cylinder whose outer diameter is defined by the outer diameter and / or top circle radius of the planetary. The annular gap area is fluidically open radially outward to an environment of the planet carrier device and / or the module open. Radially inward, the annular gap area is open to the sun gear. As a result, a fluidic channel between the environment and the sun gear is formed, can be passed over the lubricant from the environment to the sun gear.

Particular advantages arise in operation, since the lubricant is actively guided or even pumped through the annular gap area by the rotation of the planetary gear. It can thus be absorbed by the environment of oil, in particular transmission oil, on the outward opening of the annular gap area, actively conveyed through the annular gap area and delivered to the sun gear. This particular design of the web contour, which is adapted to the outer contour of the planet gear in the manner described, an active lubrication of the sun gear is implemented, so that the lubrication of the assembly and thus the lubrication of the gear assembly is improved.

Alternatively or additionally, the guide surface portion is formed concentrically to a tip circle of the adjacent planetary gear, so that the annular gap region is formed in axial plan view through the tip circle and the guide surface portion.

With the aim of achieving effective transport of the lubricant, it is preferable for the width of the annular gap region, in particular the radial distance between the guide surface section and the tip circle or the interference contour of the adjacent planetary gear, to be smaller than the tooth height of the adjacent planetary gear. This dimensioning ensures that the oil in the annular gap area is reliably transported from the environment to the sun gear.

Particularly preferably, the annular gap region extends over an angular range about the axis of rotation of the adjacent planetary gear of at least 30 °, preferably of at least 45 °. Alternatively or additionally, it is preferred that the axial width of the guide surface section and / or the annular gap region is at least 50%, preferably at least 80% of the axial width or depth of the adjacent planetary gear, in particular the toothing of the adjacent planetary gear.

In a preferred development of the invention, a funnel surface section adjoins the guide surface section on the web, so that a funnel region, which is opened into the environment, adjoins the annular gap region. Thus, the funnel area is opened over the annular gap area into the environment. The hopper area opens to the environment so that the lubricant is collected over the hopper area and directed into the annulus area. By this development, the recorded amount of lubricant is increased, thereby further improving the lubrication.

Structurally, it is preferred that the web has a guide leg, an outer support leg and / or an inner support leg. On the guide leg of the Leitflächenabschnitt and the funnel section are arranged. The outer support leg adjoins the guide leg at an outer end of the guide leg and extends in the direction of rotation about the main axis of the planet carrier device. The inner support leg adjoins an inner end of the guide leg and extends in the direction of rotation about the main axis of the planet carrier device, in particular in the same direction as the outer support leg. In an axial plan view of the web and an adjacent web is formed trapezoidal with the two support legs and the guide leg.

Structurally, it is preferred that the inner and / or the outer support leg is or are formed as a partial circle section around the main axis of the planet carrier. In particular, for the inner support leg this forms a lubricant guide for lubricant, which has already reached the sun gear.

In a preferred embodiment of the invention, the planet carrier comprising the web and at least or exactly one of the side cheeks in one piece and designed in particular as a primary molded part. In this embodiment, the web structure can be integrated virtually free of cost in the planet carrier. Particularly preferably, the planet carrier is designed as a sintered part or casting, in particular as a metal casting.

Another object of the invention relates to a transmission assembly for a vehicle with the assembly as it has been previously described or according to any one of the preceding claims. The gear arrangement is particularly preferably designed as an electric drive and includes an electric motor as a traction motor. The assembly particularly preferably forms an input transmission in the transmission assembly, with the function to convert a higher input speed to a lower output speed. Preferably, the sun gear operatively connected to the electric motor. The planet carrier forms an intermediate output from the input gear and at the same time an intermediate input z. B. in a subsequent differential stage or a manual transmission.

• 1 eine schematische Darstellung der Baugruppe in einem ersten Ausführungsbeispiel der Erfindung;
• 2 eine schematische Darstellung der Baugruppe in einem zweiten Ausführungsbeispiel;
• 3 eine axiale Draufsicht auf eine Baugruppe für eine Getriebeanordnung als ein Ausführungsbeispiel der Erfindung in der Gestaltung des zweiten Ausführungsbeispiels;
• 4 eine schematische Darstellung einer Getriebeanordnung mit der Baugruppe.

Further features, advantages and effects of the invention will become apparent from the following description of a preferred embodiment of the invention and the accompanying figure. This shows:

• 1 a schematic representation of the assembly in a first embodiment of the invention;
• 2 a schematic representation of the assembly in a second embodiment;
• 3 an axial plan view of an assembly for a gear assembly as an embodiment of the invention in the design of the second embodiment;
• 4 a schematic representation of a gear assembly with the module.

The 1 shows an assembly in an axial plan view 1 for a gear arrangement 2 for a vehicle 3 , The gear arrangement 2 is for example as an electrical axis or as an electric drive unit for the vehicle 3 be formed and has an electric motor 4 on, which forms a traction engine. The assembly 1 the 1 or the following figures, for example, is designed as an input gear and has the function of a high input speed from the electric motor 4 to convert at the input to a lower output speed at the output. The assembly 1 however, it can also be used in other applications.

The assembly 1 has a sun wheel 5 on, which in the application shown with the electric motor 4 is coupled drove, so the sun gear 5 an input to the module 1 forms. Furthermore, the assembly has 1 a plurality of planet gears 6 on. The sun wheel 5 and the planet wheels 6 each have a spur gear toothing. The planet wheels 6 are in mesh with the sun gear 5 , The sun wheel 5 defines a major axis H , each of the planet gears 6 has its own rotation axis R on which parallel to the main axis H , but in a pitch circle radius TR around the main axis H are arranged distributed. Optionally, the assembly points 1 an indicated only schematically ring gear 7 on, with the planetary gears 6 with the ring gear 7 in meshing engagement. The assembly 1 has a planet carrier 8th on. The planet carrier 8th carries the planet wheels 6 ,

During a rotation around the main axis H takes the planet carrier 8th a rotational volume, wherein through the radial outer side of the rotary volume and / or the planet carrier 8th a carrier rotational space radius TRR is defined.

The planet wheels 6 take in their entirety when rotating around the major axis H a rotational volume, wherein the radial outer side of the rotary volume and / or the planet wheels 6 a wheel rotation space radius RRR Are defined.

The carrier rotation space radius TRR and the wheel rotation space radius RRR are determined in the same plane of rotation, this plane of rotation being the teeth of the planet gears 6 cuts.

The difference between the Radrotationsraumradius RRR and the carrier rotational space radius TRR is considered immersion distance e Are defined. The immersion distance e is positive when the planetary gears 6 in the radial direction over the planet carrier 8th survive, the immersion distance e is negative when the planetary gears 6 set back in the radial direction relative to the planet carrier 8th are arranged.

Furthermore, the half head circle diameter of the planet gears 6 as a bike radius RR Are defined. Half the root diameter of the planetary gears is called foot radius FR Are defined.

As can be seen from the schematic representation in the 1 results is the immersion distance e as large or nearly as large as the tooth height, so the difference or the simple distance between the wheel radius the RR and the foot radius FR , This embodiment has the advantage that during a rotation of the planet carrier 8th a pulse-like immersion of the planet gears 6 in an only schematically indicated oil sump 9 is avoided, so that a more homogeneous rotational movement can take place through the oil sump. As a result, the losses due to the pulse-like immersion of the planet gears 6 in the oil sump 9 reduced.

The 2 shows a second embodiment of the invention, wherein the same designations denote the same sizes or components. Unlike the assembly 1 in the 1 points the planet carrier 8th in the 2 a carrier rotational space radius TRR which is equal to or slightly larger than the wheel rotational space radius RRR is, in particular so that the immersion distance is negative or zero. In this embodiment, it is preferably provided that the planet gears 6 on the radial outside with no other gear component comb. The planet carrier 8th However, it is open in the radial direction, so that the planet gears 6 in the oil sump 9 dive in and out of the oil sump 9 can be lubricated. In the second embodiment, the planet carrier forms 8th a housing for the planet wheels 6 , so that a homogeneous rotation through the oil sump 9 the assembly 1 is possible. As a result, the losses due to the pulse-like immersion of the planet gears 6 in the oil sump 9 further reduced.

An advantage of both embodiments is that the large volume formed in the radial direction of the planet carrier 8th Oil in the oil sump 9 is displaced, so that the necessary amount of oil to achieve a given oil punch can be reduced. The reduced oil volume further reduces the associated churning losses.

The 3 shows the assembly 1 in a possible structural design in an axial plan view. In the 3 are the parameters carrier rotation space radius TRR , Radrotationsraumradius RRR as well as immersion distance e located. From the illustration it follows that the carrier rotation space radius TRR and the wheel rotation space radius RRR are formed the same, the recordings for the planetary gears 6 are opened radially outward, leaving oil from the oil sump 9 to the planet wheels 6 and the sun wheel 5 can be promoted. The flush arrangement of the planet wheels 6 in the planet carrier 8th has the advantage that neither by a radial projection nor a radial set back the planetary gears 6 a fluidic resistance in the oil sump 9 form. Thus, by the flush arrangement of the planet gears 6 and / or the same size of carrier rotational space radius TRR and wheel rotation space radius RRR minimizes churning losses.

The planet carrier device 8th has webs 11 on which extends in the axial direction to the main axis H extend. The webs may enclose a cavity or be formed as a solid body areas. The bridges 11 are in the direction of rotation between the planet gears 6 arranged. In addition to the support function, the webs 11 integrated lubricant guiding functions.

The bridges 11 have at least one, in the representation of two extending in the radial direction guide legs 12 and an inner support leg 13 and an outer support leg 14 on. The guide leg 12 is in its radial course respectively to the adjacent planetary gear 6 adjusted so that the planetary gear 6 facing side with the top circle of the planetary gear 6 corresponds. The outer support leg 14 closes at an outer end of the guide legs 12 on, the inner support leg 13 closes at an inner end of the guide legs 12 on. The inner support leg 13 , the outer supporting leg 14 and the guide leg 12 embrace a trapezoidal area 15 ,
The outside of the leading leg 12 is the adjacent planetary gear 6 facing. On the outside of the leading leg 12 are a fugitive section 16 and a funnel surface portion 17 arranged as surfaces. The baffle section 16 extends or runs concentrically to a tip circle of the adjacent planetary gear 6 , This forms between the adjacent planetary gear 6 or its tip circle and the guide surface section 16 an annular gap area 18 out. The annular gap area 18 is formed as a hollow cylinder portion, which is concentric and / or coaxial with the axis of rotation R of the adjacent planetary gear 6 runs. The annular gap area 18 extends over an angular range of at least 30 ° about the axis of rotation R of the planetary gear 6 , The axial depth or width of the annular gap area 18 is equal to or greater than the axial depth or width of the teeth of the adjacent planetary gear 6 , The radial width or width in the circumferential direction of the annular gap area 18 is smaller than the tooth height of the adjacent planetary gear 6 , Radially inward is an exit of the annular gap area 18 to the sun wheel 5 open. Radially outward is the annular gap area 18 over a funnel area 19 to an environment U the assembly 1 open. The annular gap area 18 on the one hand by the adjacent planetary gear 6 and, on the other hand, through the funnel surface portion 17 formed, with funnel surface section 17 and the adjacent planetary gear 6 together the opening out funnel area 19 form.

Due to the larger outer diameter of the planet carrier 8th Oil can be promoted through the scoop-like wall, even if the oil level is reduced initially or in dynamic operation, for example due to turbulence. By the rotation of the planet wheels 6 , especially at high speeds, the oil can hold only a short time in the teeth of the planetary gear, as it is thrown off to the outside and in the tangential direction. By now pulled down enclosure around the planet around even this oil can now be collected and further promoted.

The planet carrier device 8th comprising the webs 11 or portions thereof, is formed as a master part. For example, the planet carrier device 8th be realized as a casting or as a sintered component. Due to the design as a molded part, the web geometry can almost cost neutral in the planet carrier 8th to get integrated.

Functionally, the adjacent planetary wheel rotates 6 so that lubricant from the environment U or lubricant, which is in the teeth of the planetary gear 6 located through the annular gap area 18 in the direction of rotation about the axis of rotation R in the direction of the sun wheel 5 transported or promoted. By this pumping effect, the lubricant supply of the sun gear 5 significantly improved. The promotion will particularly favored or only allows that between the bridge 11 and the adjacent planetary gear 6 the annular gap area 18 in the direction of rotation of the planetary gear 6 is provided, which prevents the lubricant can spray away radially by centrifugal forces, but by the rotational movement of the planetary gear 6 to the sun wheel 5 is encouraged. The Ölförderungsweg is in the 3 indicated by arrows.

The 4 shows a schematic representation of the transmission device 2 with the assembly 1 as a further embodiment of the invention. The electric motor 4 or its rotor is connected to the sun gear 5 geared coupled or rotatably connected as shown here. The assembly 1 has multiple planet gears 20 , in this case dual planetary gears, on, with the planetary gears 6 in each case a subsection of the multiple planet gears 20 form. Further, each of the multiple planet wheels 20 another planetary gear 21 on which coaxial and rotatably connected to the planetary gear 6 is. The other planetary gear 21 has a smaller diameter than the planetary gear 6 , Thus, the planetary gear 6 the largest tip diameter in the multi planetary gear 20 on. The other planetary gear 21 meshes with the ring gear 7 , The planet carrier 8th forms - as this particular already in the 2 and 3 is shown - a housing for the planet gears 6 , The assembly 1 in particular forms a gear to a high speed of the electric motor 4 to convert to a low speed. In particular, the sun gear forms an entrance and the planet carrier 8th an output or intermediate output from the transmission.

LIST OF REFERENCE NUMBERS

1

module

2

transmission assembly

3

vehicle

4

electric motor

5

sun

6

planetary gears

7

ring gear

8th

planet carrier

9

oil sump

10

empty

11

Stege

12

guide limb

13

inner support leg

14

outer support legs

15

trapezoidal area

16

Leitflächenabschnitt

17

Funnel surface section

18

Annulus area

19

funnel area

20

Multiple planetary gears

21

further planetary gears

H

main axis

R

axis of rotation

TR

Pitch radius

TRR

Carrier rotation space radius

RRR

Radrotationsraumradius

RR

wheel radius

FR

root radius

e

Immersion distance

a

distance

U

Surroundings

QUOTES INCLUDE IN THE DESCRIPTION

This list of the documents listed by the applicant has been generated automatically and is included solely for the better information of the reader. The list is not part of the German patent or utility model application. The DPMA assumes no liability for any errors or omissions.

Cited patent literature

• DE 102012202453 A1 [0003]
• JP 60087008 B2 [0004]

Claims (10)

An assembly (1) for a transmission assembly (2) comprising a sun gear (5) having a plurality of planetary gears (6), the planetary gears (6) being engaged with the sun gear (5), with a planetary carrier (8) the planetary gears (6) are arranged on the planetary carrier (8) in a partial circle radius (TR) about a major axis (H), the planetary carrier (8) defining a carrier rotational space radius (TRR) on rotation about the major axis (H) on the outside wherein the planet wheels (6) in their entirety define a wheel rotation space radius (RRR) when rotating about the main axis (H), the difference between the wheel rotation space radius (RRR) and the carrier rotation space radius (TRR) defining a dip distance (E) wherein the half head circle diameter of the planet gears (6) defines a wheel radius (RR), characterized in that the amount of the dip distance (E) is less than half of the wheel radius (RR). Assembly (1) after Claim 1 , characterized in that the amount of the immersion distance (E) is less than a quarter, preferably less than one-eighth of the wheel radius (RR). Assembly (1) after Claim 1 or 2 , characterized in that the amount of the immersion distance (E) is less than or equal to three times, preferably twice, in particular the simple distance between the tip circle diameter and the root diameter of the planetary gears (R) and / or the tooth height of the planet gears (&). Assembly (1) according to one of the preceding claims, characterized in that the planet wheels (6) in the planet carrier (8) are arranged radially projecting. Assembly (1) after Claim 4 , characterized in that the amount of the immersion distance (E) is greater than the simple distance between the tip circle diameter and the root diameter and / or the tooth height of the planetary gears (6). Assembly (1) according to one of the preceding Claims 1 to 3 , characterized in that the planetary gears (6) are set back radially or flush in the planet carrier. Assembly (1) after Claim 6 , characterized in that the planet gears (6) are each part of a Mehrfachplanetenrads (20), wherein the planetary gears (6) in the Mehrfachplanetenrad (20) have the largest tip diameter. Assembly (1) according to one of the preceding claims, characterized in that the planet carrier (6) is open in the radial direction, so that the planet wheels (6) can dip in the radial direction in an oil sump (9). Assembly (1) according to one of the preceding claims, characterized in that the planet carrier (8) webs (11), wherein at least one of the webs (11) adjacent to one of the planetary gears (6) is arranged, wherein the web (11) has a An airfoil portion (16), wherein between the Leitflächenabschnitt (16) and the adjacent planetary gear (6) an annular gap region (18) is formed, wherein the annular gap region (18) radially outwardly to an environment (U) and radially inwardly to the sun gear (5) is open, so that an oil from the environment (U) via the annular gap region (18) to the sun gear (5) is conductive. Gear arrangement (2) for a vehicle (1), characterized by the assembly (1) according to one of the preceding claims.

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