DE102014005517A1 - Power split transmission - Google Patents

Abstract

Power split transmission (10) with a rotatably mounted, drive-side shaft (11) on which a drive toothing (12) is integrally formed; with a rotatably mounted, output-side shaft (13) on which an output gear (15) is integrally formed; with a first number of first planetary shafts (15), wherein on each of the first planetary shafts (15) in each case a first planetary gearing (17) and axially offset a second planetary gearing (18) is formed; with a second number of second planetary shafts (16), wherein on each of the second planetary shafts (16) in each case a third planetary gearing (21) and axially offset a fourth planetary gearing (22) is formed; wherein the first planetary gears (17) of the first planetary shafts (15) engage with the drive teeth (12) and the fourth planetary gears (22) of the second planetary shafts (16) engage with the driven teeth (15); the second planetary gears (18) of the first planetary shafts (15) meshing with the third planetary gears (21) of the second planetary shafts (16); and wherein the first planetary shafts (15) are distributed over the circumference with a non-uniform angular pitch.

Description

The invention relates to a power split transmission.

From the DE 10 2010 041 474 A1 is a power split transmission known, as it is used in particular in wind turbines. That from the DE 10 2010 041 474 A1 known power-split transmission has a rotatably mounted drive-side shaft having a drive toothing and a rotatably mounted output-side shaft having an output gear, wherein the output-side shaft is positioned coaxially with the drive-side shaft. Furthermore, this power split transmission has a plurality of first planetary shafts and a plurality of second planetary shafts, wherein on each of the first planetary shafts a first planetary toothing and axially offset second planetary toothing is formed, and wherein on each of the second planetary shafts in each case a third planetary toothing and axially offset one fourth planetary toothing is formed. After DE 10 2010 041 474 A1 the first planetary gears of the first planetary shafts are engaged with the driving teeth of the driving side shaft, and third planetary gears of the second planetary shafts are engaged with the second planetary gears of the first planetary shafts. The power split transmission of DE 10 2010 041 474 A1 has a total of four first planetary shafts, the first planetary gears are in engagement with the drive teeth of the drive-side shaft. With such a power split transmission already high powers can be transmitted with high ratios. However, a further increase in the ratio would lead to an increase in space for the power split transmission, so that an increase in gear ratio for the known from the prior art power split transmission is not immediately possible.

There is therefore a need for a power split transmission, which allows a translation increase in space-optimized space.

On this basis, the invention is based on the object to provide a novel power split transmission.

This object is achieved by a power split transmission according to claim 1. In the power split transmission according to the invention, the first planetary gears of the first planetary shafts mesh with the drive teeth and the fourth planetary gears of the second planetary shafts engage the output gears, the second planetary gears of the first planetary shafts engage with the third planetary gears of the second planetary shafts, and the first planetary shafts are distributed with a non-uniform angle division over the circumference. Due to the non-uniform angular pitch for the first planetary waves, the position of the first planetary waves and second planetary waves can be selected in a space-optimized manner. In particular, high total translations can be provided with space-optimized space.

According to an advantageous embodiment, the first planetary waves are distributed with a non-uniform angular pitch on the circumference, that alternately one of the first planetary waves is offset by a positive offset angle and one of the first planetary waves by a negative offset angle to the positions of a uniform angular pitch, so that alternately adjacent first planetary waves have a relatively large angular distance and a relatively small angular distance. The second planetary waves, the number of which preferably corresponds to half of the first planetary waves, are arranged in the circumferential direction in each case between two first planetary waves with a relatively large angular separation. This embodiment is particularly preferred for ensuring a high overall ratio with the least possible installation space.

Preferably, for the magnitude of the offset angle Δα: 1 ° ≦ Δα ≦ k · 360 ° / N1, where N1 is the first number of first planetary waves and k is a multiplication constant, and where 0.3 ≦ k ≦ 0.5. In particular, for the magnitude of the offset angle, Δα: ku * 360 ° / N1 ≦ Δα ≦ ko * 360 ° / N1, where N1 is the first number of first planetary waves, where ku and ko are multiplication constants, and where ku is 0.05 and ko Is 0.3. These interpretations for the offset angle are particularly preferred.

Preferred embodiments of the invention will become apparent from the dependent claims and the description below. Embodiments of the invention will be described, without being limited thereto, with reference to the drawings. Showing:

1 a schematic axial section of a power split transmission according to the invention;

2 FIG. 2 is a schematic perspective view of a power take-off end of the power split transmission of FIG 1 ; and

3 FIG. 2 is a schematic perspective view of a drive end of the power split transmission of FIG 1 ,

The invention relates to a power split transmission, in particular for use in wind turbines. 1 to 3 show an embodiment of a power split transmission according to the invention 10 , The power split transmission 10 has a rotatably mounted, drive-side shaft 11 , at the drive toothing 12 is formed, wherein in the exemplary embodiment, the drive toothing 12 as internal toothing of a ring gear 25 is trained. The power split transmission 10 of the 1 and 2 furthermore has a rotatably mounted output-side shaft 13 , on the output gear 14 is formed, wherein in the embodiment of the 1 the output toothing 14 as external teeth of a sun gear 26 is trained.

Furthermore, the power split transmission has 10 over a plurality of first planetary waves 15 and a plurality of second planetary shafts 16 , At each of the first planetary waves 15 is in each case a first planetary toothing 17 and axially offset a second planetary gearing 18 formed, wherein in the illustrated embodiment, the first planetary toothing 17 the first planetary waves 15 of first planet wheels 19 and the axially offset, second planetary gearing 18 axially displaced, second planetary gears 20 provided. Each of the second planetary waves 16 has a third planetary toothing 21 and a fourth planetary gearing 22 axially offset from the respective third planetary toothing 21 is, wherein the respective third planetary toothing 21 the second planetary waves 16 in the illustrated embodiment of third planetary gears 23 and the fourth planetary gears 22 the second planetary waves 16 of axially offset fourth planetary gears 24 are provided.

The first planetary gears 17 the first planetary waves 15 coming from the first planet wheels 19 are provided, stand with the drive teeth 12 in which it is, as already stated, a spur gear, in the example shown by an internal toothing of a ring gear 25 ,

The fourth planetary gears 22 the second planetary waves 16 coming from the fourth planet wheels 24 are provided, stand with the output teeth 14 engaged, as the external toothing of a sun gear 26 is trained.

Furthermore, there are the second planetary gears 18 the first planetary waves 15 coming from the second planet wheels 20 are provided, as well as the third planetary gears 21 the second planetary waves 16 coming from the third planet wheels 23 are engaged with each other.

The first planetary waves 15 are with a nonuniform angular pitch and the second planetary waves 16 preferably with a distributed to a tolerance deviation of less than 1 ° uniform angular pitch over the circumference. This is an optimal arrangement of the planetary waves at high desired overall ratios of the power split transmission 15 . 16 or planetary gears possible, so high overall ratios of the power split transmission 10 can be provided with optimized space.

The first number of the first planetary waves 15 is even and larger than the second number of second planetary waves 16 , The second number of second planetary waves 16 is even or odd. In the embodiment shown, the power split transmission comprises 10 six first planetary waves 15 and three second planetary waves 16 , The in the 1 to 3 shown number of first planetary waves 15 and second planetary waves 16 is purely exemplary nature. In contrast, it is also possible that the power split transmission 10 eight first planetary waves 15 and four second planetary waves 16 having. There are also other numbers of first planetary waves 15 and second planetary waves 16 possible, but with the number of first planetary waves 15 is straight, and the number of second planetary waves 16 preferably half the number of first planetary waves 15 equivalent.

The first planetary waves 15 are distributed with non-uniform angular pitch over the circumference that alternately one of the first planetary waves 15 by a positive offset angle + Δα and one of the first planetary waves 15 is offset by a negative offset angle -Δα from the positions of a uniform angular pitch. A positive offset angle corresponds to an offset of the respective first planetary shaft 15 in the clockwise direction and a negative offset angle offset the respective first planetary shaft 15 opposite to the clockwise direction.

Through this alternation of the first planetary waves 15 in the clockwise direction as well as in the counterclockwise direction by the positive offset angle and the negative offset angle, such as 3 can be taken, alternately pairs of side by side positioned first planetary waves 15 with a relatively large angular distance β1 and a relatively small angular distance β2. The angles β1, β2 are thus calculated as follows: β1 = β + Δα, β2 = β - Δα, where β = 360 ° / N1 and where N1 is the first number of first planetary waves 15 is.

For the magnitude of the offset angle Δα, 1 ° ≦ Δα ≦ k · 360 ° / N1, where N1 is the first number of first planetary waves and K is a multiplication constant. The multiplication constant k is preferably 0.4.

In particular, for Δα: ku * 360 ° / N1 ≦ Δα ≦ ko * 360 ° / N1, where N1 is the first number of first planetary waves, where ku and ko are multiplication constants, and where ku is 0.05 and ko is 0.3 ,

The second planetary waves 16 , which are preferably distributed in the circumferential direction with a uniform angular pitch over the circumference, are preferably between two first planetary shafts 19 arranged with the relatively large angular distance β1, particularly preferably in the middle between each two first planetary waves 15 with the relatively large angular distance β1.

LIST OF REFERENCE NUMBERS

10

Power split transmission

11

drive-side shaft

12

driving teeth

13

output shaft

14

driven teeth

15

first planetary waves

16

second planetary waves

17

first planetary gearing

18

second planetary gearing

19

first planetary gear

20

second planetary gear

21

third planetary gearing

22

fourth planetary gearing

23

third planetary gear

24

fourth planetary gear

25

ring gear

26

sun

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 102010041474 A1 [0002, 0002, 0002, 0002]

Claims (11)

Power split transmission ( 10 ), with a rotatably mounted, drive-side shaft ( 11 ), on which a drive toothing ( 12 ) is formed; a rotatably mounted, output-side shaft ( 13 ), on which an output toothing ( 15 ) is formed; a first number of first planetary waves ( 15 ), wherein on each of the first planetary waves ( 15 ) each have a first planetary gearing ( 17 ) and axially offset a second planetary gearing ( 18 ) is formed; a second number of second planetary waves ( 16 ), wherein on each of the second planetary waves ( 16 ) each have a third planetary toothing ( 21 ) and axially offset a fourth planetary gearing ( 22 ) is formed; wherein the first planetary gears ( 17 ) of the first planetary waves ( 15 ) with the drive toothing ( 12 ) and the fourth planetary gearing ( 22 ) of the second planetary waves ( 16 ) with the output toothing ( 15 ) are engaged; wherein the second planetary gears ( 18 ) of the first planetary waves ( 15 ) with the third planetary gearing ( 21 ) of the second planetary waves ( 16 ) are engaged; and wherein the first planetary waves ( 15 ) are distributed with a non-uniform angular pitch over the circumference. Power split transmission according to claim 1, characterized in that the first number of first planetary shafts ( 15 ) greater than the second number of second planetary waves ( 16 ), and that the first number of first planetary waves ( 15 ) straight and the second number of second planetary waves ( 16 ) is even or odd. Power split transmission according to claim 1 or 2, characterized in that the first planetary shafts ( 15 ) are distributed at a non-uniform angular pitch on the circumference such that alternately one of the first planetary shafts ( 15 ) by a positive offset angle and one of the first planetary waves ( 15 ) is offset by a negative offset angle from the positions of a uniform angular pitch. Power split transmission according to claim 3, characterized in that for the magnitude of the offset angle Δα: 1 ° ≤ Δα ≤ k · 360 ° / N1, where N1 is the first number of first planetary shafts and k is a multiplication constant. Power split transmission according to claim 4, characterized in that the multiplication constant k is 0.4. Power split transmission according to claim 3, characterized in that for the magnitude of the offset angle Δα: ku * 360 ° / N1 ≤ Δα ≤ ko · 360 ° / N1, where N1 is the first number of first planetary waves, and where ku and ko are multiplication constants are. Power split transmission according to claim 6, characterized in that the multiplication constant ku is 0.05 and the multiplication constant ko is 0.3. Power split transmission according to one of claims 1 to 7, characterized in that the planetary shafts ( 16 ) are distributed over the circumference with a uniform angular pitch. Power split transmission according to one of claims 1 to 8, characterized in that the second planetary shafts ( 16 ) in the circumferential direction in each case between two adjacent first planetary shafts ( 15 ), which are arranged at a relatively large angular distance from each other, are positioned. Power split transmission according to claim 9, characterized in that every second planetary shaft ( 16 ) in the circumferential direction in each case in the middle between two first planetary waves ( 15 ), which are arranged at a relatively large angular distance from each other, is positioned. Power split transmission according to one of claims 1 to 10, characterized in that the first number of first planetary shafts ( 15 ) twice the size of the second number of second planetary shafts ( 16 ).

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