KR20140009053A - Power split transmission - Google Patents

Abstract

A power split transmission (10) comprises a driving shaft (11) which is integrally formed with a driving gear ring (12) and pivotally supported; an output shaft (13) which is pivotally supported and integrally formed with an output gearing (14); and a plurality of first and second planetary shafts (13, 15). In this case, a second planetary gearing (18) offset in the axial direction to a first planetary gearing (17) is integrally formed in the first planetary shaft (15). A fourth planetary gearing (22) offset in the axial direction to a third planetary gearing (21) is integrally formed in the second planetary shaft (16) and in this case, the first planetary gearing (17) of the first planetary shaft (15) and the third planetary gearing (21) of the second planetary shaft (16) are connected to the driving gearing (12); the second planetary gearing (18) of the first planetary shaft (15) is connected to the output gearing (14) through a first coupling shaft (26); and the fourth planetary gearing (22) of the second planetary shaft (16) is connected to the output gearing through a second coupling shaft (27).

Description

POWER SPLIT TRANSMISSION < RTI ID = 0.0 >

The present invention relates to a power split transmission according to the preamble of claim 1.

DE 10 2010 041 474 A1 discloses power split transmissions, particularly those used in wind power plants. A power split transmission known in DE 10 2010 041 474 A1 has a drive side shaft including drive gearing and a rotatably supported drive side shaft and an output side shaft rotatably supported with output gearing, Is coaxially positioned with respect to the drive-side shaft. In addition, the power transmission includes a plurality of first planetary shafts and a plurality of second planetary shafts, wherein each first planetary shaft is provided with a first planetary gearing and an axially offset second planetary gearing integrally And a third planetary gearing and an axially offset fourth planetary gear ring are integrally formed on each second planetary shaft. According to DE 10 2010 041 474 A1, the first planetary gearing of the first planetary shaft engages the drive gearing of the drive-side shaft, in which case the third planetary gearing of the second planetary shaft is engaged with the second planetary gearing of the first planetary shaft Lt; / RTI > The power split transmission of DE 10 2010 041 474 A1 comprises a total of four first planetary shafts, the first planetary gearing of which engages with the drive gearing of the drive shaft. High power can be delivered by this power split transmission. However, the continued power increase may result in an increased weight increase of the power split transmission, so that the power increase of the power split transmission known in the prior art is directly impossible.

Therefore, there is a need for a power split transmission suitable for delivering higher power. It is an object of the present invention to provide a new type of power split transmission.

The above problem is solved by a power split transmission according to claim 1.

In accordance with the present invention, the first planetary gearing of the first planetary shaft and the third planetary gearing of the second planetary shaft engage the drive gearing, in which case the second planetary gearing of the planetary shaft is engaged through the first coupling shaft, The fourth planetary gearing of the planetary shaft engages the output gearing through the second coupling shaft. The power transferable by the concept of the power split type transmission according to the present invention can be increased. When three first planetary shafts and three second planetary shafts are provided, the transferable power can be increased by 50% compared to the power split transmission known from DE 10 2010 041 474 A1.

Preferably, the first planetary gears of the first planetary shaft and the third planetary gears of the second planetary shaft are positioned in a common plane, wherein the second planetary gearings of the first planetary shaft are axially The fourth planetary gears of the second planetary shaft are positioned in a third plane offset axially with respect to the first and second planes. By disposing the second planetary gears of the first planetary shaft and the fourth planetary gears of the second planetary shaft in a separate plane that is axially offset with respect to the first plane, i.e., in the second and third planes, A particularly advantageous structural implementation or structural configuration of the power-split transmission is achieved.

According to a preferred refinement, the first coupling shaft comprises a first coupling gearing and an axially offset second coupling gearing, the second coupling shaft comprises a third coupling gearing and an axially offset fourth Wherein the first coupling gearing is coupled to the second planetary coupling via a first sun gear, wherein the third coupling gearing is coupled to the second sun gear through an axially offset second sun gear, 4 planetary gearing, and the second and fourth coupling gearings engage output gearing, respectively. As a result, the power transmitted from the first planetary shaft and the power transmitted from the second planetary shaft can be collected through the two sun gears and the coupling shaft independently, thereby providing a desirable power distribution to the power split transmission . The power to be delivered is distributed or distributed evenly across all the planetary shafts provided.

Preferably, the output shaft, the first coupling shaft and the second coupling shaft are formed as coaxially interconnected shafts, wherein the output shaft is formed as a hollow shaft, the hollow shaft having a first coupling shaft and a second coupling shaft, The second coupling shaft is formed as a hollow shaft, the hollow shaft partially concentrically surrounding the first coupling shaft radially outwardly. The two coupling shafts and the output shafts are embodied as interconnected coaxial shafts to enable a particularly advantageous structural configuration of the power split transmission according to the present invention.

According to a preferred refinement, the at least one power split transmission comprises three first planetary shafts and three second planetary shafts. The arrangement of a total of six planetary shafts and dividing them into two groups, each containing three planetary shafts, is particularly advantageous, in particular by a 50% increase in transmittable power compared to the prior art according to DE 10 2010 041 474 A1.

Preferred embodiments of the invention are set forth in the dependent claims and the following description. The embodiments of the present invention are not limited thereto and are described with reference to the drawings.

In accordance with the present invention, a power split transmission suitable for delivering higher power is provided.

1 is a schematic axial sectional view of a power split transmission according to the invention in accordance with a first embodiment;
Figure 2 is a schematic radial cross-sectional view of the power split transmission of Figure 1;
3 is a schematic axial sectional view of a power split transmission according to the invention in accordance with a second embodiment;
4 is a schematic axial sectional view of the power split transmission of FIG. 3;

The present invention relates generally to power split transmissions for use in wind power plants.

1 and 2 show a first preferred embodiment of a power split transmission 10 according to the present invention. The power split transmission 10 includes a drive side shaft 11 rotatably supported and a drive gearing 12 integrally formed on the shaft and in this case the drive gearing 12 are formed as internal gearings of the hollow gear.

In addition, the power split transmission 10 of Figs. 1 and 2 includes an output shaft 13, which is rotatably supported, and an output gear ring 14 is integrally formed on the shaft.

In addition, the power split transmission 10 includes a plurality of first planetary shafts 15 and a plurality of second planetary shafts 16.

A first planetary gear ring 17 and an axially offset second planetary gear ring 18 are integrally formed on each first planetary shaft 15 and in this case the first planetary shaft 15 Is provided by the first planetary gears 19 and the axially offset second planetary gearing 18 is axially offset by the second planetary gears 20 / RTI > Each second planetary shaft 16 includes a third planetary gearing 21 and a fourth planetary gearing 22 that is axially offset with respect to the third planetary gearing 21, In this case, each third planetary gear ring 21 of the second planetary shaft 16 is provided by third planetary gears 23 in the illustrated embodiment, and the fourth planetary gearing 21 of the second planetary shaft 16 (22) is provided by fourth planetary gears (24) offset in the axial direction of the second planetary shaft.

The first planetary gear ring 17 of the first planetary shaft 15 and the third planetary gear ring 21 of the second planetary shaft 16 are engaged with the drive gear ring 12 of the drive shaft 11, The first planetary gear ring 17 of the first planetary shaft 15 and the third planetary gear ring 21 of the second planetary shaft 16 are positioned in a common first plane 25.

The second planetary gearing 18 of the first planetary shaft 15 is connected to the first coupling shaft 26 and the fourth planetary gearing 22 of the second planetary shaft 16 is coupled to the second coupling shaft 27 The second planetary gearing 18 of the first planetary shaft 15 is coupled to the output gearing 14 of the output side shaft 13 via the first planetary gear 15, 2 planes 28 and the fourth planetary gearing 22 of the second planetary shaft 16 is positioned in a third plane that is axially offset with respect to the first plane 25 and the second plane 28 29).

The first planetary gears 19 provide the first planetary gearing 17 of the first planetary shaft 15 and the third planetary gearing 21 of the second planetary shaft 16 in the illustrated preferred embodiment The third planetary gears 23 disposed on the first planetary gears 23 are commonly disposed on the first plane 25 whereas the second planetary gears 20 providing the second planetary gearing 18 on the first planetary shaft 15, Of the second planetary gearing (22) of the second planetary shaft while being positioned in a second plane (28) offset axially relative to the plane, and the fourth planetary gears (24) is again placed in the third plane (29) offset in the axial direction.

The first coupling shaft 26 coupling the second planetary gearing 18 of the first planetary shaft 15 to the output gear ring 14 of the output shaft 13 is connected to the first coupling gearing 30 and the axial direction And a second coupling gearing 31 offset to the second coupling gearing 31. The first coupling gear ring 30 of the first coupling shaft 26 engages the second planetary gear ring 18 of the first planetary shaft 15 through the first sun gear 32. The second coupling gear ring 31 of the first coupling shaft 26 engages the output gearing 14 of the output shaft 13 and thus the first output gearing group 33 of the output gear ring 14. The second coupling shaft 27 coupling the fourth planetary gearing 22 of the second planetary shaft 16 to the output gear ring 14 of the output shaft 13 is connected to the third coupling gearing 34 and the axial direction Wherein the third coupling gearing 34 of the second coupling shaft 27 is connected to the second planetary shaft 16 via the second sun gear 36, Of the fourth planetary gearing 22 of FIG. The fourth coupling gear ring 35 of the second coupling shaft 27 is engaged with the output gear ring 14 of the output shaft 13 and the second output gear ring group 37 of the output gear ring 14 And the second output gearing group is positioned offset in the axial direction with respect to the first output gearing group 33 of the output gearing 14. [

The two sun gears 32, 36 positioned in the different planes 28, 29 are preferably embodied as a line pinion which is freely movable in the radial direction, and the line pinion is connected to a separate coupling shaft 26 And 27, respectively. The connection of the sun pinion can be done through a curved gear coupling.

The output side shaft 13 extends coaxially with respect to the drive side shaft 11 and in this case the two coupling shafts 26 and 27 also coaxially extend with respect to the drive side shaft 11 .

1, the output shaft 13, the first coupling shaft 26, and the second coupling shaft 27 are embodied as interconnected coaxial shafts, in this case in the embodiment of FIG. 1, The shaft 13 is embodied as a hollow shaft, and the hollow shaft partially surrounds the first coupling shaft 26 and the second coupling shaft 27 in a concentric manner. The second coupling shaft 27 is also embodied as a hollow shaft, which concentrically surrounds the first coupling shaft 26 radially outwardly. The two output gearing groups 33 and 37 of the output gearing 14 of the first output shaft 13 are each formed as an internal gearing in which case the second coupling gearing of the first coupling shaft 26 31 and the fourth coupling gear ring 35 of the second coupling shaft 27 are formed as external gearings, respectively.

In the illustrated preferred embodiment in which three first planetary shafts 15 and three second planetary shafts 16 are provided, six planetary gearings 17, 21, i.e. three of the first planetary shafts 15 The three third planetary gears 21 of the first planetary gearing 17 and the second planetary shaft 16 are respectively engaged with the drive gearings 12 of the drive shaft 11, As shown in FIG.

Three of the first planetary shafts 15 that individually or separately couple with the output gearing 14 of the output shaft 13 through the sun gears 32 and 36 and the correspondingly separated coupling shafts 26 and 27, The three fourth planetary gearings 22 of the second planetary gearing 18 and the second planetary shaft 16 are axially offset from each other by two planes 28, 29 offset axially with respect to the plane 25, In which case the power to be delivered from the power split transmission over a total of six power paths is evenly distributed.

Although an embodiment including six power paths through three first planetary shafts 15 and three second planetary shafts 16 is preferred, six or more power paths may be provided, e. G. Eight, In this case, preferably, four first planetary shafts 15 and four second planetary shafts 16 are provided.

In the embodiment of Figures 1 and 2, the drive shaft 11 is embodied as a hollow gear, in which case the drive gear ring 12 is formed as an internal gear ring. 3 and 4 illustrate an embodiment of a power split transmission 10 ', wherein the difference between the transmission and the power split transmission 10 of FIGS. 1 and 2 is that the drive shaft 11' Is implemented as a spur gear and the drive gearing 12 'is implemented as an external gearing of the spur gear. The first planetary gearing 17 of the first planetary shaft 15 and the third planetary gearing 21 of the second planetary shaft 16 are engaged with the drive gearing 12 '. Because the embodiment of Figures 3 and 4 is the same as the embodiment of Figures 1 and 2 with respect to all other details, the same reference numerals are used for the same part assembly to avoid unnecessary repetition, Reference is made to the foregoing description of an embodiment of the second embodiment.

In both embodiments, the first planetary gearing 17 of the first planetary shaft 15 and the third planetary gearing 21 of the second planetary shaft 16 are engaged with the drive gearing 12 or 12 ' do. In a preferred embodiment in which a total of six planetary shafts 15,16 are provided, therefore, six power paths are provided for power transmission. The second planetary gearing 18 of the first planetary shaft 15 and the fourth planetary gearing 22 of the second planetary shaft 16 are disposed in two axially offset planes 28, 29, The gearings are coupled to the output shaft 13, i.e., the output gear ring 14 of the output shaft, via separate sun gears 32, 36 and separate coupling shafts 26, 27. The planetary gears 32, 26 are preferably embodied as independent line pinions which are freely movable in the radial direction, in which case the line pinions are preferably connected via curved gear couplings. The power split transmission 10 or 10 'is provided by a suitable structural implementation of the planetary shafts 15 and 16 and the planetary gearing, coupling shafts 26 and 27, coupling gearing and sun gears 32 and 36 of the shaft. Is distributed or distributed uniformly to the individual power paths.

10, 10 'power split transmission
11, 11 'drive shaft
12, 12 'drive gearing
13 Output shaft
14 Output Gearing
15 1st planetary shaft
16 2nd planetary shaft
17 1st planetary gearing
18 2nd planetary gearing
19 1st planetary gear
20 second planetary gear
21 Third planetary gearing
22 Fourth planetary gearing
23 3rd planetary gear
24 Fourth planetary gear
25 First plane
26 first coupling shaft
27 second coupling shaft
28 Second plane
29 Third plane
30 1st coupling gearing
31 2nd coupling gearing
32 first-line gear
33 1st Output Gearing Group
34 3rd coupling gearing
35th coupling gearing
36 2nd line gear
37 2nd Output Gearing Group

Claims (12)

A power split transmission (10, 10 ') comprising:
A drive shaft (11, 11 ') rotatably supported and integrally formed with the drive gearing (12, 12');
An output shaft (13) rotatably supported, the output gearing (14) being integrally formed;
A plurality of first planetary shafts (15) integrally formed with a first planetary gear ring (17) and an axially offset second planetary gear ring (18), respectively;
A power split transmission comprising a plurality of second planetary shafts (16) integrally formed with a third planetary gear ring (21) and an axially offset fourth planetary gear ring (22)
The first planetary gear ring 17 of the first planetary shaft 15 and the third planetary gear ring 21 of the second planetary shaft 16 engage with the drive gear rings 12 and 12 '
Wherein the second planetary gearing 18 of the first planetary shaft 15 is connected to the second planetary gearing 22 via the first coupling shaft 26 and the fourth planetary gearing 22 of the second planetary shaft 16 is connected to the second Is coupled to the output gear ring (14) via a coupling shaft (27). 2. A planetary gear set according to claim 1, wherein said first planetary gearing (17) of said first planetary shaft (15) and said third planetary gear ring (21) of said second planetary shaft (16) And the second planetary gear ring 18 of the first planetary shaft 15 is positioned in the second plane 28 and the fourth planetary gear ring 22 of the second planetary shaft 16 is positioned Is positioned in a third plane (29) axially offset relative to said first plane (25). ≪ Desc / Clms Page number 13 > 3. The transmission according to claim 1 or 2, wherein a first coupling gear ring (30) and an axially offset second coupling gear ring (31) are integrally formed on the first coupling shaft (26) The third coupling gearing 34 and the axially offset fourth coupling gearing 35 are integrally formed on the first coupling gear 27 and the second coupling gear 27. In this case, Is coupled to the second planetary gear ring 18 via the sun gear 32 and in this case the third coupling gear ring 34 is coupled to the fourth planetary gear ring 22 via the second sun gear 36. [ , Wherein the second coupling gearing (31) and the fourth coupling gearing (35) engage the output gearing (14). 4. The transmission according to claim 3, wherein the output gearing (14) comprises a first output gearing group (33) and an axially offset second output gearing group (37) Is coupled to the first output gearing group (33) of the output gearing (14) and the fourth coupling gearing (35) engages the second output gearing group (37) of the output gearing Wherein said power split transmission is a power split transmission. 5. The power split transmission of claim 3 or 4, wherein the sun gears (32, 26) are embodied as a radial moveable line pinion. 5. The drive shaft according to any one of claims 1 to 4, wherein the output shaft (13), the first coupling shaft (26) and the second coupling shaft (27) Wherein the first and second gears extend coaxially with respect to one another. 6. A method according to any one of claims 1 to 5, wherein the output shaft (13), the first coupling shaft (26) and the second coupling shaft (27) are formed as interconnected coaxial shafts Wherein said power split transmission is a power split transmission. 7. The apparatus according to claim 6, wherein the output shaft (13) is formed as a hollow shaft and the hollow shaft is partially concentric with the first coupling shaft (26) and the second coupling shaft In which case the first output gearing group 33 of the output gearing 14 and the second output gearing group 37 of the output gearing 14 are formed as internal gearing, Characterized in that the second coupling gearing (31) of the coupling shaft (26) and the fourth coupling gearing (35) of the second coupling shaft (27) are each formed as an external gearing Transmission. 8. A method as claimed in claim 6 or 7, wherein the second coupling shaft (27) is formed as a hollow shaft, the hollow shaft partially concentrically surrounding the first coupling shaft (26) radially outward Wherein said power split transmission is a power split transmission. A drive gear according to any one of claims 1 to 8, wherein the drive shaft (11) is formed as a hollow gear and the drive gear ring (12) is formed as an internal gearing of the hollow gear, Characterized in that the first planetary gear ring (17) of the planetary shaft (15) and the third planetary gear ring (21) of the second planetary shaft (16) engage the internal gear ring of the hollow gear Transmission. The drive gear according to any one of claims 1 to 8, characterized in that the drive shaft (11 ') is formed as a spur gear and the drive gear ring (12') is formed as an external gear ring of the spur gear, Characterized in that the first planetary gearing (17) of the planetary shaft (15) and the third planetary gear ring (21) of the second planetary shaft (16) engage the external gearing of the spur gear . 9. Power split type transmission according to any one of claims 1 to 8, characterized in that at least three first planetary shafts (15) and at least three second planetary shafts (16) are provided.

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