DE102019207924A1 - Gear, especially for a single wheel drive unit - Google Patents

Abstract

The invention relates to a transmission which is provided in particular within a single wheel drive unit and which has a transmission carrier, an input shaft that can be driven rotatably about an axis, at least one planetary gear stage with a first externally toothed sun gear that can be driven via the input shaft, with an internally toothed ring gear that is on the gear carrier is rotatably mounted, and with a rotatably mounted planetary web on which at least one externally toothed planetary gear that engages with both the sun gear and the ring gear is rotatably mounted and which has internal teeth. A further gear stage comprises at least one spur gear, which is rotatably mounted on a bearing pin which is stationary with respect to the gear carrier and which is arranged with its axis at a distance from the axis of the input shaft and which meshes with the ring gear. There is a second externally toothed sun gear. Such a transmission can be designed as a two-speed transmission that the two components of the second externally toothed sun gear and input shaft are axially displaceable between two end positions relative to one another, that in a first end position the second externally toothed sun gear and the input shaft are coupled to one another in a rotationally fixed manner and rotate at the same speed and the power flow from the input shaft via the planetary gear stage to the second externally toothed sun gear is interrupted.

Description

The invention relates to a transmission which is provided in particular within a single wheel drive unit and which has a transmission carrier, an input shaft that can be rotated about an axis, at least one planetary gear stage with a first externally toothed sun gear that can be driven via the input shaft, with an internally toothed ring gear that can be driven on the gear carrier is rotatably mounted, and with a rotatably mounted planetary web on which at least one externally toothed planetary gear that engages with both the sun gear and the ring gear is rotatably mounted and which has internal teeth. A further gear stage comprises at least one spur gear, which is rotatably mounted on a bearing pin that is stationary with respect to the gear carrier and is arranged with its axis at a distance from the axis of the input shaft and is in meshing engagement with the ring gear. There is a second externally toothed sun gear.

Such transmissions are mainly used within single wheel drives of mobile work machines, in particular construction machines or agricultural machines, or transport units. In practice, such machines first drive on a road or an access route to the place of use, for example to a field, and then do work in the field. On the drive to the scene, the torque required is small, while a high speed is desired. The field is then usually driven with high torque and low speed. This gives rise to the requirement to design a transmission of the type described above with multiple or at least two speeds.

From the DE 10 2004 031 009 B4 a transmission with the features listed at the beginning is already known. There, the planetary gear stage and the gear stage, which have a common ring gear representing the output of the gear, are preceded by a further planetary gear stage with a sun gear, a ring gear and a planetary web with planet gears that mesh with the sun gear and the ring gear. The planetary web is non-rotatably connected to the sun gear of the subordinate planetary gear stage. Depending on the state of two multi-plate clutches, the ring gear of the further planetary gear stage is fixed to the housing or connected to the sun gear of the further planetary gear stage so that the planetary web rotates more slowly than the sun gear or at the same speed as the sun gear of the further planetary gear stage. Two gears of the transmission are thus implemented.

The object of the present invention is a transmission which is provided in particular within a single wheel drive unit and which firstly has a transmission carrier, secondly an input shaft that can be rotated about an axis, thirdly at least one planetary gear stage with a first externally toothed sun gear that can be driven via the input shaft an internally toothed ring gear, which is rotatably mounted on the gear carrier, and with a rotatably mounted planetary web on which at least one externally toothed planetary gear, which engages with both the sun gear and the ring gear, is rotatably mounted and which has internal teeth, fourthly another Gear stage, which comprises at least one spur gear, which is rotatably mounted on a bearing pin which is stationary with respect to the gear carrier and is arranged with its axis at a distance from the axis of the input shaft and which is in tooth engagement with the ring gear, and fifth a second externally toothed sun gear d has to be further developed in such a way that two different courses with a small number of components and thus low complexity and costs and largely without wear and tear of components are obtained.

The object is achieved in that, in a transmission of the specified type, the two components, the second externally toothed sun gear and the input shaft, are axially displaceable between two end positions relative to one another, that in a first end position of the two components, the second externally toothed sun gear and the input shaft relative to one another, the second externally toothed sun gear and the input shaft are rotatably coupled to each other and rotate at the same speed and the power flow from the input shaft via the planetary gear stage to the second externally toothed sun gear is interrupted and that in the second end position the second externally toothed sun gear meshes with the internal teeth of the planetary web without direct coupling with the input shaft and over the planetary gear stage can be driven by the input shaft.

According to the invention, the two gears are not implemented with the aid of multi-plate clutches, but rather by changing the relative position between the input shaft and the second externally toothed sun gear. There are only a few components with a low level of complexity. The transmittable torque does not depend on the force with which the plates of a multi-plate clutch are pressed together.

A transmission according to the invention can be further developed in an advantageous manner.

In a particularly advantageous development, one is between the two End positions located intermediate position of the two components second externally toothed sun gear and input shaft relative to each other the second externally toothed sun gear on the one hand rotatably coupled to the input shaft and on the other hand is in a power flow from the input shaft via the planetary gear stage. The input shaft is in mesh with the planetary gears via the first sun gear and in parallel therewith in mesh with the second sun gear. The transmission is now locked. It is not possible to turn the ring gear and the input shaft.

In the first end position of the two components, the second externally toothed sun gear and the input shaft relative to one another, one of the two components is decoupled from the planetary gear stage to interrupt the flow of force from the input shaft via the planetary gear stage to the second externally toothed sun gear.

In a transmission according to the invention with only one planetary gear stage, the sun gear of the planetary gear stage can be driven at the same speed as the input shaft and the second externally toothed sun gear can be driven at the same speed by the planetary web of the planetary gear stage. The sun gear of the planetary gear stage rotates when it is coupled to the input shaft at the same speed as the input shaft and the second sun gear rotates when it is coupled to the planetary carrier at the same speed as the planet carrier

Advantageously, only one of the two components, the second externally toothed sun gear and the input shaft, is axially displaceable relative to the transmission carrier.

In a special development, the input shaft is arranged stationary in the axial direction with respect to the transmission carrier and the second externally toothed sun gear is axially displaceable relative to the input shaft.

In another special development, the second externally toothed sun gear is arranged stationary in the axial direction with respect to the transmission carrier and the input shaft is axially displaceable relative to the second externally toothed sun gear. This solution is particularly advantageous when there are at least two planetary gear stages, the second planetary gear stage arranged in the power flow after the first planetary gear stage being closer to a drive motor than the first planetary gear stage. With such a structure of the transmission, it is easier to move the input shaft than the second sun gear. Rather, this is non-rotatably connected to the planetary web of the first planetary gear stage and meshes with the planet gears of the second planetary gear stage.

However, it is also conceivable that in a transmission with two planetary gear stages, the third sun gear can be displaced and is non-rotatably connected in one position to the planetary web of the second planetary gear stage and meshes with the spur gears of the further gear stage and in a second position by the planetary web of the second planetary gear stage is decoupled and is directly non-rotatably connected to the input shaft. With such a solution, the difference in the gear ratios between the two gear steps would be very large.

The second externally toothed sun gear and the input shaft can be coupled to one another in a rotationally fixed manner by means of a splined shaft or a toothed shaft connection.

In a preferred manner, one of the two components, the second externally toothed sun gear and the input shaft, is axially displaceable with a fluid piston, in particular with a hydraulic fluid piston.

The fluid piston is preferably designed to be single-acting and adjoins a pressure chamber, the axially displaceable component being movable by the fluid piston in the direction of the second end position when pressure medium is fed into the pressure chamber and in the direction of the first end position by a spring means while displacing pressure medium from the pressure chamber is.

Two embodiments of a transmission according to the invention are shown in the drawings. The invention will now be explained in more detail using the figures of these drawings.

• 1 einen axialen Schnitt durch das erste Ausführungsbeispiel, das genau eine Planetengetriebestufe aufweist und bei dem das zweite Sonnenrad axial verschiebbar ist und sich in einer Endposition befindet, die dem der ersten Gang entspricht,
• 2 einen axialen Schnitt durch das erste Ausführungsbeispiel, wobei sich das zweite Sonnenrad in einer Zwischenposition befindet und das Getriebe gesperrt ist,
• 3 einen axialen Schnitt durch das erste Ausführungsbeispiel, wobei sich das zweite
• Sonnenrad in einer zweiten Endposition befindet, die dem zweiten Gang entspricht, 4 einen axialen Schnitt durch das zweite Ausführungsbeispiel, das genau zwei Planetengetriebestufen aufweist und bei dem die Eingangswelle axial verschiebbar ist und sich in einer Endposition befindet, die dem der ersten Gang entspricht,
• 5 einen axialen Schnitt durch das zweite Ausführungsbeispiel, wobei sich die Eingangswelle in einer Zwischenposition befindet und das Getriebe gesperrt ist, und
• 6 einen axialen Schnitt durch das zweite Ausführungsbeispiel, wobei sich die Eingangswelle in einer zweiten Endposition befindet, die dem zweiten Gang entspricht.

Show it

• 1 an axial section through the first embodiment, which has exactly one planetary gear stage and in which the second sun gear is axially displaceable and in a The end position that corresponds to the first gear,
• 2 an axial section through the first embodiment, wherein the second sun gear is in an intermediate position and the transmission is locked,
• 3 an axial section through the first embodiment, wherein the second
• Sun gear is in a second end position, which corresponds to second gear, 4th an axial section through the second embodiment, which has exactly two planetary gear stages and in which the input shaft is axially displaceable and is in an end position that corresponds to that of the first gear,
• 5 an axial section through the second embodiment, wherein the input shaft is in an intermediate position and the transmission is locked, and
• 6th an axial section through the second embodiment, wherein the input shaft is in a second end position, which corresponds to the second gear.

The transmission according to the 1 to 3 includes a gear carrier 8th with a mounting flange 9 , with which the transmission mount can be attached to the chassis of a vehicle. The gear carrier 8th is a hollow body that has wall sections on the outside and inside which differ from one another in their diameters.

The transmission also includes a planetary gear stage 10 and another gear stage 11 . The gear stages are from a motor, in this case from a hydraulic motor 12 in bent axis design, which is only shown in the figures in a highly schematic manner, via a driver sleeve 13 and an input shaft 14th drivable. At the end of the input shaft remote from the engine 14th this is provided in one piece with external teeth that form the sun gear 18th the planetary gear stage 10 forms. Beyond the sun gear 18th is the input shaft 14th with a roller bearing 19th rotatably mounted.

The sun gear 18th meshes with several externally toothed planet gears 25th which are at equal distances from each other via double-row roller bearings rotatable on bearing journals 26th of a planet bar 27 are stored. The planet gears 25th comb except with the sun gear 18th still with an internally toothed ring gear 28 that has a mounting flange 29 has with which it can be attached to the rim of a wheel. The ring gear 28 thus forms the wheel-side output of the transmission. It is with the help of two tapered roller bearings installed in an O arrangement 30th outside on the gear carrier 8th from one end face of the ring gear 28 protrudes into this, rotatably mounted. The other end is in the ring gear 28 a lid 31 used of the rolling bearing 19th for the input shaft 13 wearing.

The planetary bridge 27 is with internal teeth 35 provided, in the non-rotatable connection a sleeve-shaped, with external teeth 36 provided, second sun gear 37 can be inserted, and via collar bolts 38 that are in holes 34 of the gear carrier 5 are used and are supported on this, and on collar bolts 39 that is on the lid 31 support axially guided. The sun gear 37 is coaxial with the input shaft 14th arranged.

On the gear box 8th are around the input shaft 14th around at the same angular distances from one another several axially aligned bearing journals 41 formed, each of which has a two-row rolling bearing arrangement 42 an externally toothed spur gear 43 stores that with both the sun gear 37 as well as with the ring gear 28 combs. The holes 34 for the axial guidance of the planetary web 27 serving collar bolts 38 are located in the journal 41 . The holes 34 are inward to the axis of the input shaft 13 are offset and eccentric to the axes of the bearing journals.

As the journal 41 occupy a fixed position with respect to the gear carrier, the second gear stage 11 no rotating planet gears. Because of the compared to the planetary gear stage 10 Similar arrangement of the gears, however, the second gear stage is often referred to as the planetary gear stage.

The second sun gear 37 protrudes over the spur gears 43 out and engages over a certain distance over the driver sleeve 13 .and the driver part 14th of the input shaft are in the embodiments according to 1 to 3 arranged axially overlapping, the driver part 14th in the sun gear 37 immersed.

The sun gear 37 is axially displaceable between a first end position and a second end position. Regardless of its position, it always meshes with the spur gears 43 . In the first end position, the 1 shows, it engages with its external teeth 36 into the internal teeth 35 of the planet bar 27 and rotates at the same speed as the planet carrier. In the second end position, the 3 shows it is off the planetary bridge 27 submerged and with internal teeth 44 in an external toothing 45 the input shaft 14th inserted. The second sun gear is in the second end position 37 so from the planetary bridge 27 decoupled and non-rotatably with the input shaft 14th coupled and rotates at the same speed as the input shaft.

In an intermediate position that is in 2 is shown, engages the second sun gear 37 both with its external teeth 36 into the internal teeth 35 of the planet bar 27 as well as with its internal teeth 44 into the external toothing 45 the input shaft. In this intermediate position of the sun gear 37 the transmission is locked.

For the axial displacement of the second sun gear 37 in one direction one serves as an annular piston 50 trained hydraulic fluid piston, which is in the transmission carrier 8th is led. A sealing ring 51 seals the radial gap between the annular piston and the gearbox carrier 8th from. The annular piston 50 is single acting. The sun gear is therefore only in one direction from the annular piston 50 postponed. In the opposite direction is the sun gear 37 moved by spring force. And that becomes the second sun gear 37 from the annular piston 50 acted upon with a force in the direction of the second end position and with the spring force in the direction of the first end position.

To do this, it is first between the annular piston 50 and one in the gearbox carrier 8th inserted and by a snap ring 52 secured floor 53 a pressure room 54 educated. This is via a connection hole 55 , an inclined hole 56 and a round milling slot 57 fluidically connectable to a hydraulic pressure source and to a pressure sink. The annular piston 50 is not stepped on the outside and has the same outer diameter as the actual annular piston 50 owning soil 58 on. In this and in the sun gear 37 is axially fixed a ball bearing 59 used, which is a pivot bearing between the annular piston 50 and the sun gear 37 forms and the annular piston via its inner ring and outer ring 50 and the sun gear 37 axially on the one hand on a shoulder of the annular piston or the sun gear 37 and on the other hand rest against snap rings inserted in the annular piston and in the sun gear, are axially fixed to one another.

In relation to the actual ring piston 50 outer side of the floor 58 becomes the ring piston 50 of helical compression springs 62 applied. One helical compression spring each 62 dips into a blind hole 63 one that extends into a bearing journal 41 extends into it, and is supported on the bottom of the blind hole. The number of blind holes 63 and thus also the number of helical compression springs 62 is equal to the number of journals 41 . The axis of a blind hole 63 is aligned with one opposite the blind hole 63 a smaller diameter bore 34 , with the hole 34 to the corresponding blind hole 63 is open. In this way, the two holes 34 and 63 manufacture in a simple way.

In 1 the first embodiment is shown in a state in which the second sun gear 37 and the planetary bridge 27 with their teeth 35 and 36 are nested, while the teeth 44 and 45 from sun gear 37 and input shaft 14th are disengaged. The printing room 54 is pressurized and the annular piston 50 against the force of the helical compression springs 62 up to a stop on the gearbox carrier 8th postponed. The second sun gear 37 rotates at the same speed as the planet carrier 27 and meshes with the meshing with the ring gear 28 stationary spur gears 43 . This means that the transmission ratio is at its maximum. First gear is engaged. In the pressure room 54 a pressure generating a predominant pressure force over the spring forces is maintained as long as this first gear is to be used.

The pressure chamber is used to engage the second gear 54 connected to a volume, for example a tank, in which there is only a low pressure or atmospheric pressure. The helical compression springs 62 can then use the piston 50 and the sun gear 37 move towards a second end position. Will the pressure room 54 then locked when the second sun gear 37 not quite off the planetary bridge yet 27 immersed and with its gearing 44 already a little way into the gearing 45 the input shaft 14th is immersed and occupies an intermediate position between its two end positions, the transmission is locked.

Will the pressure room 54 on the other hand not locked, the helical compression springs slide 62 the annular piston 50 and the sun gear 37 in the in 3 shown first end position. In this is the sun gear 37 from the planetary bridge 27 decoupled and with the input shaft 14th non-rotatably connected. In the second gear that is now engaged, the transmission ratio is only due to the number of teeth on the sun gear 37 and the ring gear 28 determined and much smaller than in first gear.

The transmission according to the 4th to 6th includes like the transmission according to the 1 to 3 a gear carrier 8th with a mounting flange 9 , with which the transmission mount can be attached to the chassis of a vehicle. The gear carrier 8th is a hollow body that has wall sections on the outside and inside which differ from one another in their diameters.

The transmission according to the 4th to 6th includes like the transmission according to the 1 to 3 a planetary gear stage 10 with on a planetary bridge 27 rotatably mounted planetary gears 25th and another gear stage 11 with a sun gear 67 that with spur gears 43 the further gear stage 11 combs. It is another planetary gear stage 70 with on a planetary bridge 71 rotatably mounted planetary gears 72 present that like the planetary gears 25th with the ring gear 28 are engaged. The planetary bridge 71 is with internal teeth 73 provided in which the sun gear 67 with its external teeth 74 axially immersed so that the sun gear 67 and the planetary bridge 71 rotate at the same speed. The sun gear 67 is constant with the planetary bridge 71 and the spur gears 43 the further gear stage 11 coupled.

The planetary bridge 27 the planetary gear stage 10 has as in the embodiment from the 1 to 3 an internal toothing 35 , in the a sun gear 37 ' with its external teeth 36 intervenes with this external toothing 36 also with the planet gears 72 the planetary gear stage 70 combs. Unlike the embodiment according to the 1 to 3 is the axial position of the sun gear 37 ' of the embodiment according to 4th to 6th not changeable.

The transmission according to the 4th to 6th has an input shaft 80 those with a cup-shaped and internally toothed end have an externally toothed shaft stub 81 of the hydraulic motor 12 overlaps and rotatably with the stub shaft 81 connected is. At the other end, the input shaft carries 80 outside a toothing or corrugation, via which they are connected to a correspondingly toothed or corrugated sun gear on the inside 18 ' the planetary gear stage 10 is rotatably connected. The inside of the sun gear has the same toothing or corrugation as the sun gear 18 ′ 37 ' . The teeth or corrugation on the input shaft 80 as well as on the sun gear 18 ' and the sun gear 37 ' is of such a nature that an axial displacement of the input shaft 80 relative to the sun wheels 18 ' and 37 ' is possible. Because just as in the embodiment according to the 1 to 3 by changing the relative axial position between the input shaft 14th and the sun gear 37 so in the embodiment according to 4th to 6th by changing the relative axial position between the input shaft 80 and the sun gear 37 ' Changed between two courses. However, in the embodiment according to 4th to 6th the input shaft is axially displaced relative to the other transmission parts and not the sun gear.

For axial displacement of the input shaft 80 serves in one direction as in the embodiment according to the 1 to 3 again as an annular piston 50 trained hydraulic fluid piston, which is in the transmission carrier 8th is performed against helical compression springs 62 works and has a ball bearing 59 axially fixed, but rotatable with the input shaft 80 is coupled. The arrangement and the shape of the annular piston 50 comprehensive sliding mechanism for the input shaft 80 is the same as the sliding mechanism for the sun gear, apart from minor details 37 from the 1 to 3 so that it is not discussed in more detail here, but reference is made to the corresponding description above.

In 4th the second embodiment is shown in a state in which the input shaft in the sun gear 18 ' stuck and no direct coupling between the input shaft 80 and the sun gear 37 ' consists. The printing room 54 is pressurized and the annular piston 50 against the force of the helical compression springs 62 up to a stop on the gearbox carrier 8th postponed. The sun gear 18 ' is via the input shaft 80 driven and meshes with the also with the ring gear 28 meshing planet gears 25th . This causes the planet bar to rotate 27 and takes the sun gear 37 ' With. This meshes with the ring gear as well 28 meshing planet gears 72 . This causes the planet bar to rotate 71 and takes the sun gear 67 With. This meshes with the spur gears 43 . With the power flow described, the gear ratio is at its maximum. First gear is engaged. In the pressure room 54 a pressure generating a predominant pressure force over the spring forces is maintained as long as this first gear is to be used.

The pressure chamber is used to engage the second gear 54 connected to a volume, for example a tank, in which there is only a low pressure or atmospheric pressure. The helical compression springs 62 can then use the piston 50 and the input shaft 80 from the second end position according to 4th move towards a first end position. Will the pressure room 54 locked when the input shaft 80 not quite out of the sun gear yet 18 ' immersed and with their external teeth or external corrugation already a little way into the sun gear 37 ' is immersed and one in 5 assumes the intermediate position shown between its two end positions, the transmission is locked.

Will the pressure room 54 on the other hand not locked, the helical compression springs slide 62 the annular piston 50 and the input shaft 80 in the in 6th shown first end position. In this is the input shaft 80 from the sun gear 18 ' decoupled and with the sun gear 37 ' non-rotatably connected. The planetary stage is in the now engaged second gear 10 is no longer included in the translation. This is now smaller than when the input shaft is coupled 80 with the sun gear 18 ' . Second gear is engaged.

List of reference symbols

8th

Gear carrier

9

Mounting flange on 8

10

Planetary gear stage

11

further gear stage

12

Hydraulic motor

13

Driving sleeve

14th

Input shaft

18th

Sun gear

18 '

Sun gear

19th

roller bearing

25th

Planetary gear

26th

Journal

27

Planetary bridge

28

Ring gear

29

Mounting flange on 28

30th

Tapered roller bearings

31

cover

34

drilling

35

Internal toothing of 27

36

External toothing of 37

37

second sun gear

37 '

second sun gear

38

Collar bolt

39

Collar bolt

41

Bearing journal on 8

42

Rolling bearing arrangement

43

Spur gear

44

Internal toothing of 37

45

External toothing of 14

50

hydraulic annular piston

51

Sealing ring

52

Snap ring

53

ground

54

Printing room

55

Connection hole

56

Inclined hole

57

Milled slot

58

Floor of 50

59

ball-bearing

62

Helical compression spring

63

Blind hole

70

Planetary gear stage

71

Planet bar from 70

72

Planet gears from 70

73

Internal teeth on 71

74

External toothing of 67

80

Input shaft

81

Stub shaft of 12

QUOTES INCLUDED IN THE DESCRIPTION

This list of the documents listed by the applicant was 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.

Patent literature cited

• DE 102004031009 B4 [0003]

Claims (11)

Transmission, which is provided in particular within a single wheel drive unit and which has a transmission carrier (8), an input shaft (14) that can be driven rotatably about an axis, at least one planetary gear stage (10) with a first externally toothed sun gear (18, 18 '), which via the input shaft (14) can be driven, with an internally toothed ring gear (28) which is rotatably mounted on the gear carrier (8), and with a rotatably mounted planetary web (27) on which at least one externally toothed, both with the sun gear (18, 18 ' ) and with the ring gear (28) in engagement planet gear (25) is rotatably mounted and which has an internal toothing (35), a further gear stage (11) which comprises at least one spur gear (43) which is on a with respect to the gear carrier (8) is rotatably mounted on a stationary bearing pin (41) with its axis spaced apart from the axis of the input shaft (14) and meshes with the ring gear (28), and a second externally toothed sun en gear (37, 37 '), characterized in that the two components of the second externally toothed sun gear (37, 37') and input shaft (14) are axially displaceable between two end positions relative to one another, that in a first end position of the two components, the second externally toothed sun gear (37, 37 ') and input shaft (14) relative to each other, the second externally toothed sun gear (37, 37') and the input shaft (14) are rotatably coupled to each other and rotate at the same speed and the power flow from the input shaft (14) via the planetary gear stage (10) to the second externally toothed sun gear (37, 37 ') is interrupted and that in the second end position the second externally toothed sun gear (37, 37') without direct coupling to the input shaft (14) with the internal toothing (35) of the planetary web (27 ) meshes and can be driven by the input shaft (14) via the planetary gear stage (10). Gearbox after Claim 1 , wherein in an intermediate position of the two components located between the two end positions, the second externally toothed sun gear (37, 37 ') and input shaft (14) relative to one another, the second externally toothed sun gear (37, 37') is coupled to the input shaft (14) in a rotationally fixed manner also lies in a power flow from the input shaft (14) via the planetary gear stage (10). Gearbox after Claim 1 , wherein in the first end position of the two components, the second externally toothed sun gear (37, 37 ') and input shaft (14) relative to one another, one of the two components (14; 37) is decoupled from the planetary gear stage (10). Transmission according to one of the preceding claims, wherein the sun gear (18, 18 ') of the planetary gear stage (10) can be driven by the input shaft (14) at the same speed and the second externally toothed sun gear (37, 37') at the same speed from the planetary web (27) the planetary gear stage (10) can be driven. Transmission according to one of the preceding claims, only one of the two components, second externally toothed sun gear (37, 37 ') and input shaft (14) being axially displaceable relative to the transmission carrier (8). Gearbox after Claim 5 , wherein the input shaft (14) is arranged in the axial direction fixed to the gear carrier (8) and the second externally toothed sun gear (37) is axially displaceable relative to the input shaft (14). Gearbox after Claim 5 , wherein the second externally toothed sun gear (37 ') is arranged in the axial direction fixed to the gear carrier (8) and the input shaft (14) is axially displaceable relative to the second externally toothed sun gear (37'). Gearbox after Claim 7 , wherein at least two planetary gear stages (10, 70) are present and wherein the second externally toothed sun gear (37 ') is non-rotatably connected to the planetary web (27) of the first planetary gear stage (10) and to the planetary gears (72) of the second planetary gear stage (70) combs. Transmission according to one of the preceding claims, wherein the second externally toothed sun gear (37, 37 ') and the input shaft (14) can be coupled to one another in a rotationally fixed manner by means of a splined shaft or a toothed shaft connection. Transmission according to one of the preceding claims, wherein there is a fluid piston (50), in particular a hydraulic fluid piston, with which one of the two components, second externally toothed sun gear (37) and input shaft (14) can be axially displaced. Gearbox after Claim 10 , wherein the fluid piston (50) is single-acting and adjoins a pressure chamber (54) and wherein the axially displaceable component (14; 37) when pressure medium is fed into the pressure chamber (54) from the fluid piston (50) in the direction of the second end position and can be moved in the direction of the first end position by spring means (62) while displacing pressure medium from the pressure chamber (54).

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