• 专利附录
  • 专利说明
  • 权利要求
  • 类似技术
  • 同族专利
  • 引用文献
  • 法律状态
  • 优先权
    • 专利摘要:
    A power split transmission (10) having a first shaft (11), a second shaft (13), a plurality of first planetary shafts (15), and a plurality of second planetary shafts (16), the first planetary gears (17) of the first planetary shafts (15 ) and the third planetary gears (21) of the second planetary shafts (16) are engaged with the first shaft (11); and wherein said second / fourth planetary gears (18/22) of said first / second planetary shafts (15/16) are engaged by a first / second clutch shaft (26/27) with drive teeth (14).
    公开号:BE1023932B1
    申请号:E2013/0475
    申请日:2013-07-09
    公开日:2017-09-14
    发明作者:Valentin Meimann；Ingo Sommer；Markus Potthoff；Burkhard Pinnekamp
    申请人:Renk Aktiengesellschaft；
    IPC主号:
    专利说明:

    Power split transmission
    The invention relates to a power split transmission according to the preamble of claim 1.
    DE 10 2010 041 474 A1 discloses a power transmission mechanism which is used, in particular, in wind power plants. The DEV 10 2010 041 474 A1 known LeistungsVerzweigungsgétriebé 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 to the drive-side shaft. Furthermore, this power transmission has a plurality of first planetary shafts and a plurality of second planetary shafts, wherein a first planetary toothing and axially offset second planetary toothing is integrally formed on each of the first planetary shafts, and wherein on each of the second planetary shafts a third planetary toothing and axially offset one According to DE 10 2010 041 474 A1, the first planetary gears of the first planet are sometimes engaged with the drive teeth of the drive-side shaft, with third planetary gears of the second planetary shafts engaging 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 Planeteriwellen whose 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. However, a further increase in power would lead to a disproportionate increase in weight for the power split transmission, so that an increase in performance 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 is suitable for transmitting higher powers. On this basis, the object of the invention is to provide a novel power split transmission. This object is achieved by a power split transmission according to claim 1. According to the invention, the harvested planetary gears of the first planetary shafts and the third planetary gears of the second planetary shafts are engaged with the drive teeth, the second planetary gears of the first planetary shafts meshing with the output teeth via a first coupling shaft and the fourth planetary gears of the second planetary shafts via a second coupling shaft. With the inventive concept of the power split transmission, the transmittable power can be increased.
    Then, when three first planetary shafts and three second planetary shafts are present, the transmittable power can be increased by 50% compared with the power-split transmission known from DE 10 2010 041 474 A1.
    Preferably, the first planetary gears of the first planetary gears and the third planetary gears of the second planetary shafts are positioned in a common first plane, the second planetary gears of the first planetary gears being axially cross-linked to the first plane in a second plane and the fourth planetary gears of the second planetary shafts axially in a third plane offset to the first level and the second level are positioned.
    The arrangement of the second Planetenverzahnuhgen the first planetary times and the fourth planetary gear ments of the second planetary waves in separately to the first plane axially offset planes, namely in the second plane and the third plane, allows a particularly advantageous structural design or design of the power split transmission according to the invention.
    According to an advantageous development, the first coupling shaft has a first coupling toothing and axially offset second coupling toothing, the second coupling shaft having a third coupling toothing and axially offset fourth coupling toothing, wherein the first coupling toothing is in engagement with the second planetary toothings via a first sun gear, wherein the third clutch gear meshes with the fourth planetary gear teeth via an axially offset second sun gear, and wherein the second clutch gear and the fourth clutch gear mesh respectively with the output gear teeth. This makes it possible to independently collect the power transmitted by the first planetary shafts as well as the power transmitted from the second planetary shafts via the two sun gears and clutch shafts, thereby providing an ideal load distribution in the power split transmission. The power to be transmitted is split or distributed evenly in particular over all available planetary waves.
    Preferably, the output-side shaft, the first clutch shaft and the second clutch shaft are formed as coaxial, nested shafts, wherein the output-side shaft is formed as a hollow shaft which surrounds the first clutch shaft and the second Kupplungswejle radially outside partially concentric, and wherein the second Kupplüngswelle as Hollow shaft is formed, which surrounds the first clutch shaft radially outwardly in sections concentrically. The embodiment of the two clutch shafts and the output shaft as interleaved, coaxial shafts allows a particularly advantageous design of the power split transmission according to the invention.
    According to an advantageous development, at least the power split transmission has three first planetary shafts and three second planetary shafts. The provision of a total of six planetary shafts and the division thereof into two groups, each with three planetary shafts, is particularly preferred over the prior art according to DE 10 2010 041 474 A1 an increase of the transmittable power by 50%.
    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 shows a schematic axial section of a power branching transmission according to the invention according to a first embodiment;
    FIG. 2 is a schematic radial section of the power-split transmission of FIG. 1; FIG.
    3 shows a schematized axial section of a power split transmission according to the invention in a second exemplary embodiment, and
    Fig. 4; a schematic radial section of the power split transmission of Fig. 3rd
    The present invention relates to a power split transmission, in particular for use in wind turbines.
    Fig. 1 and 2 show a first, preferred embodiment of a power split transmission 10 according to the invention. The power split transmission 10 has a rotatably mounted, drive-side shaft 11 on which a drive toothing 12 is formed, wherein in the exemplary embodiment of FIG. 1 the drive toothing 12 is formed as internal toothing of a ring gear is.
    The power split transmission 10 of FIGS. 1 and 2 further has a rotatably mounted, abiriebsseitige shaft 13 to which an output gear 14 is formed.
    Further, the power split transmission 10 has a plurality of first planetary shafts 15 and a plurality of second planetary shafts 16.
    At each of the first planetary shafts 15, a first planetary toothing 17 and axially offset a second planetary toothing 18 is formed, wherein in the illustrated embodiment, the first planetary toothing 17 of the first planetary tenwelien 15 of first planetary gears 19 and the axially offset second planetary toothing 18 of axially offset , second planetary gears 20 is provided. Each of the second Planetenwellenén 16 has a third planetary toothing 21 and a fourth planetary gear 22 which is axially offset from the respective third planetary toothing 21, wherein the respective third planetary toothing 21 of the second planetary shaft 16 in the exemplary embodiment shown of third planetary gears 23 and the fourth planetary gears 22 of second planetary shafts 16 are provided by axially offset fourth planetary gears 24 thereof.
    The first planetary gears 17 of the first planetary shafts 15 and the third planetary gears 21 of the second planetary shafts 16 are respectively engaged with the driving teeth 12 of the driving-side shaft 11, the first planetary gears 17 of the first planetary shafts 15 and the third planetary gears 21 of the second planetary shafts 16 in one common first level 25 are positioned.
    The second planetary gears 18 of the first planetary shafts 15 are connected via a first coupling shaft 26 and the fourth. Planetary gears 22 of the second Planetenwelien 16 are connected via a second clutch shaft 27 respectively with the output gear 14 of the output side shaft 13 into engagement, wherein the second planetary gears 18 of the first planetary shafts 16 are positioned in a first plane 25 axially offset second plane 28, and wherein the fourth planetary gears 22 of the second planetary shafts 16 are positioned in a third plane 29 axially offset from the first plane 25 and the second plane 28.
    Accordingly, in the preferred embodiment shown, the first planetary gears 19 providing the first planetary gears 17 of the first planetary shafts 15 and the third planetary gears 23 providing the third planetary gears 21 of the second planetary gears 16 are arranged together in the first plane 25, whereas the second planetary gears 20, which provide the second planetary gears 18 of the first planetary shafts 15 are positioned in a second plane 28 axially offset therewith, while the fourth planetary gears 25 of the second planetary shafts 16 providing the fourth planetary gears 22 thereof are disposed in the third axially offset plane 29 ,
    The first Küpplungswefle 26, via which the second planetary gears 18 of the first planetary shafts 15 are engaged with the output teeth 14 of the output-side shaft 13, has a first coupling teeth 30 and axially offset via a second coupling teeth 31 The first Kupplungsver-toothing 30 of the first coupling shaft 26 is engaged with the second planetary gear teeth 18 of the first planetary shafts 15 via a first sun gear 32. The second clutch gear 31 of the first clutch shaft 26 is in engagement with the output gear 14 of the output side shaft 13, namely with a first output gear group 33 of the output gear 14. The second clutch shaft 27, via which the fourth planetary gears 22 of the second planetary shafts 16 with the output gear 14 of abtriebsseitigen while 13, has a third clutch teeth 34 and axially offset via a fourth clutch teeth 35, the third Kupplungsver-toothing 34 of the second clutch shaft 27 with the fourth planetary gears 22 of the second planetary shafts 16 via a second sun gear 36 is engaged The fourth clutch gear 35 of the second clutch shaft 27 in turn engages the output gear teeth 14 of the output side shaft 13, namely a second output gear group 37 of the output gear 14 axially offset from the first output gear ppe 33 of the output gear teeth 14 is positioned.
    The two sun gears 32 and 36, which are positioned in the different planes 28 and 29, are preferably designed as radially freely movable sun gears, which, as already mentioned, are connected via separate coupling shafts 26 and 27 to the output-side shaft 13. The articulation of the sun pinion can be done via Bogenzahnkupplungen.
    As already stated, the output-side shaft 13 is coaxial with the drive-side shaft 11, whereby the two clutch shafts 26 and 27 extend coaxially with the drive-side shaft 11.
    1, the output-side shaft 13, the first clutch shaft 26 and the second clutch shaft 27 are designed as coaxial, nested in each other, wherein in the Ausführungsbetspiel of FIG. 1, the output-side shaft 13 is designed as a hollow shaft, which is the first Kuppliwgswel-le 26 and the second clutch shaft 27 partially concentrically surrounds. Furthermore, the second clutch shaft 27 is designed as a hollow shaft which surrounds the first clutch shaft 26 radially outwardly in sections concentrically. The two output gear groups 33 and 37 of the output gear 14 of the output shaft 13 are each formed as internal gears, wherein the second Kupplungsschalt 31 of the first clutch shaft 26 and the fourth clutch teeth 35 of the second clutch shaft 27 are each formed as external teeth.
    In the illustrated preferred embodiment, in which three first planetary shafts 15 and three second planetary shafts 16 are present, the six planetary gears 17 and 21, ie the three first planetary gears 17 of the first planetary gears 15 and the three third planetary gears 21 of the second planetary shafts 16, each in engagement with the drive teeth 12 of the drive-side shaft 11, wherein the same are positioned in the common plane 25.
    The three second planetary gears 18 of the first planetary shafts 15 and the three fourth planetary gears 22 of the second planetary shafts 16 individually and separately engaged via the sun gears 32 and 36 and via correspondingly separate clutch shafts 26 and 27 with the output gear 13 of the driven-side shaft 13 , Are arranged in two axially to each other and axially offset to the plane 25 levels 28 and 29, wherein over all six power paths, the power to be transmitted from the power split transmission is evenly distributed.
    Although an embodiment with six power paths across three first planetary shafts 15 and three second planetary shafts 16 is preferred, there may be more than six power paths, for example eight power paths, then preferably four first planetary shafts 15 and four second planetary shafts 16 are present.
    In the embodiment of FIGS. 1 and 2, the drive-side shaft 11 is designed as a ring gear, wherein the drive toothing 12 is formed as an internal toothing. In contrast, FIGS. 3 and 4 show an exemplary embodiment of a power branching transmission 10 ', which differs from the power split transmission 10 of FIGS. 1 and 2 in that the drive-side shaft 11' is designed as a spur gear and the drive gear 12 'as external toothing of the spur gear. With this drive toothing 12 'in turn are the first planetary gears 17 of the first planetary shafts 15 and the third planetary gears 21 of the second planetary shafts 16 in engagement, With regard to all other details is true, the embodiment of FIGS. 3 and 4 with the embodiment of FIGS. 1 and 2 match, so to avoid unnecessary repetition for the same components same reference numerals are used to the above comments on the embodiment of FIGS. 1 and 2 is referenced.
    Both embodiments have in common that both the first planetary gears 17 of the first planetary shafts 15 and the third planetary gears 21 of the second planetary shafts 16 are in engagement with the drive teeth 12 and 12 'respectively. In the preferred embodiment in which a total of six planetary shafts 15, 16 are present, six power paths are thus provided for power transmission. The second planetary gears 18 of the first planetary shafts 15 and the fourth planetary gears 22 of the second planetary shafts 16 are arranged in two axially offset planes 28 and 29, wherein the same via separate sun gears 32 and 36 and separate Kupplungswelien 26 and 27 with the output-side shaft 13, namely the Abtriebsverzahnung 14 thereof are coupled. The planetary gears 32 and 36 are preferably as an independent, radially freely movable Sonhenritzel a.usge-leads, the sun gears are preferably articulated via curved teeth clutches. By suitable structural design of the planetary shafts 15,16 and their planetary gears, the clutch shafts 26,27 and the clutch gears and the sun gears 32, 36 aufgeteiit or distributed from the power split transmission 10 and 10'zu power evenly distributed to the individual power paths.
    10,10 'power split gear 11,11' drive side shaft 12, 12 'drive teeth 13 output side shaft 14 output gear 15 first planetary waves 16 second Ria neten waves 17 first planetary gear 18 second planetary gear 19 first planetary gear 20 second planetary gear 21 third Pianetenverzahnung 22 fourth planetary gear 23 third Pia neten rad 24 fourth planetary gear 25 first level 26 first clutch shaft 27 second clutch shaft 28 second level 29 third level 30 first clutch gear 31 second clutch gear 32 first sun gear 33 first output gear group 34 third clutch gear 35 fourth clutch gear 36 second sun gear 37 second output gear group
    权利要求:
    Claims (11)
    [1]
    claims
    1. power split transmission (10,10 '), with a rotatably mounted, drive-side shaft (11, 1Γ), on which a drive toothing (12,12') is integrally formed; a rotatably mounted, output-side shaft (13) on which a driven toothing (15) is integrally formed; a plurality 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 integrally formed; a plurality of second planetary shafts (16), wherein on each of the second planetary shafts (16) in each case a third planetary toothing (21) and axially offset a fourth planetary toothing (22) is integrally formed; wherein the first planetary gears (17) of the first planetary shafts (15) and the third planetary gears (21) of the second planetary shafts (16) are engaged with the drive teeth (12, 12 '); the second planetary gears (18) of the first planetary shafts (15) are in engagement with the output teeth (14) via a first coupling shaft (26) and the fourth planetary gears (22) of the second planetary shafts (16) via a second coupling shaft (27). characterized in that a first KupplungsVerzahnung (30) and axially offset a second coupling teeth (31) is integrally formed on the first coupling shaft (26) that at the second coupling shaft (27) a third coupling teeth (34) and axially offset a fourth coupling teeth (26) 35) is formed, wherein the first coupling toothing (30) with the second planetary gears (18) via a first sun gear (32) is engaged, wherein the third coupling toothing (34) with the fourth planetary gears (22) via a second sun gear (36 ), and wherein the second coupling toothing (31) and the fourth coupling toothing (35) respectively engage with the driven toothing (14).
    [2]
    2. power split transmission according to claim 1, characterized in that the first planetary gears (17) of the first planetary shafts (15) and the third planetary gears (21) of the second planetary shafts (16) in a common first plane (25) are positioned, and that the second planetary gears (18) of the first planetary shafts (15) in a second plane (28) and the fourth planetary gears (22) of the second planetary shafts (16) in a third plane (29) are each positioned axially offset from the first plane (25).
    [3]
    3. power split transmission according to claim 1 or 2, characterized in that the output gear (14) has a first output gear group (33) and axially offset a second output gear group (37), wherein the second KupphmgsVerzahnung (31) with the first output gear group (33) of Abtriebsverzahnung (14) and the fourth Kupplungsszahnung (35) with the second output gear group (37) of the output gear (14) is engaged.
    [4]
    4. power split transmission according to one of claims 1 to 3, characterized in that the sun gears (32,36) are designed as radially movable sun pinion.
    [5]
    5. Power-split transmission according to one of claims 1 to 3, characterized in that the output-side shaft (13), the first coupling shaft (25) and the second coupling shaft (27) coaxial with the drive-side shaft (11, 1Γ) extend.
    [6]
    6. power split transmission according to one of claims 1 to 4, characterized in that the output-side shaft (13), the first coupling shaft (26) and the second coupling shaft (27) are formed as coaxial, nested waves.
    [7]
    7. power split transmission according to claim 5, characterized in that the output-side shaft (13) is designed as a hollow shaft which surrounds the first clutch shaft (26) and the second clutch shaft (27) radially outwardly in sections concentrically, wherein the first output gear group (33) of Output gear (14) and the second Abtriebsverzahnungsgruppe (37) Abtrièbsverzahnung (14) are each formed as internal teeth, and wherein the second coupling teeth (31) of the first coupling shaft (26) and the fourth coupling teeth (35) of the second coupling shaft (27) respectively are designed as external teeth.
    [8]
    8. power split transmission according to claim 5 or 6, characterized in that the second coupling shaft (27) is designed as a hollow shaft which surrounds the first coupling shaft (26) radially outwardly in sections concentrically.
    [9]
    9. power split transmission according to one of claims 1 to 7, characterized in that the drive-side shaft (11) as a ring gear and the drive toothing (12) is designed as internal toothing of the ring gear, wherein the first planetary gears (17) of the first planetary shafts (15) and the third planetary gearing (21) of the second planetary shafts (16) engage with the internal gearing of the ring gear.
    [10]
    10. power split transmission according to one of claims 1 to 7, characterized in that the drive-side shaft (1Γ) as a spur gear and the drive toothing (12 ') is formed as external toothing of the spur gear, wherein the first planetary gears (17) of the first planetary shafts (15) and the third planetary teeth (21) of the second planetary shafts (16) engage the external teeth of the spur gear.
    [11]
    11. power split transmission according to one of claims 1 to 7, characterized by at least three first planetary shafts (15) and at least three second planetary shafts (16).
    类似技术:
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    同族专利:
    公开号 | 公开日
    FI20135764A|2014-01-14|
    CN103542038A|2014-01-29|
    KR20140009053A|2014-01-22|
    FI127148B|2017-12-15|
    DE102012013834A1|2014-01-16|
    CN103542038B|2018-10-09|
    KR101970836B1|2019-04-19|
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    法律状态:
    2017-12-13| FG| Patent granted|Effective date: 20170914 |
    2021-04-28| MM| Lapsed because of non-payment of the annual fee|Effective date: 20200731 |
    优先权:
    申请号 | 申请日 | 专利标题
    DE201210013834|DE102012013834A1|2012-07-13|2012-07-13|Power-split transmission for use in wind power plant, has drive tooth formed at drive-sided shaft, and planetary gearings engaged with output tooth over respective coupling shafts, where coupling shafts run coaxial to drive-sided shaft|
    DE102012013834.2|2012-07-13|
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