Planetary gears for wind turbines

Abstract

The invention relates to a planetary transmission (4) of a wind turbine (1), comprising a ring gear (10), a sun gear (9), a plurality of planetary gears (11) and a planet carrier (15), wherein the planetary gears (11) are slidably mounted on a planet shaft (12) of the planet carrier, wherein the planetary gears (11) are arranged coaxially on the planet shaft relative to the planet shaft (12), and the planetary transmission comprises a surface (13.1; 13.2) of one of two sliding fittings (11, 12) in sliding contact with each other. at least one cavity (23) on a surface (13.1; 13.2) of a corresponding sliding partner (11; 12), wherein each cavity (23) extends axially and in the circumferential direction on a surface (13.1; 13.2) of the corresponding sliding partner (11; 12) and is formed as a radial recess relative to the remainder of the housing contour of the sliding partner (11; 12), and the planetary transmission comprises a lubricant distribution unit (18; 20, 21), which is fed by a pump (19) and has a first opening (22.1), wherein the first opening (22.1) ends in one or more cavities (23). In order to improve the formation of the lubricant film, it is proposed that each cavity provided on the surface (13.1; 13.2) of one of the two sliding fittings (11; 12) in sliding contact with each other is a lubricant recess (23), wherein the axial length L of the lubricant recess is at least 60% of the axial width (B) of the planetary gear (11); circumferential grooves (24; 30.1, 30.2) are provided, which are completely opposite to the surface of the planetary gear (11) provided with at least one lubricant recess ( 23) and / or the circumferential groove extends in a sliding fit (11; 12) arranged coaxially with another sliding fit (11; 12) and / or the circumferential groove extends in a sliding fit (11; 12) provided with at least one lubricant recess (23) on its circumference and only between the lubricant recesses (23); and the lubricant distribution unit (18) comprises a second opening (22.2) which ends in the circumferential groove (24; 30.1, 30.2) or ends opposite the circumferential groove.

Description

Technical Field

[0001] The present invention relates to a planetary transmission of a wind turbine, and in particular to a sliding bearing of a planetary gear on a planet shaft of such a planetary transmission. Background Art

[0002] A wind turbine typically includes a generator, located within the nacelle, for converting wind energy into electrical energy. This generator is driven by a rotor driven by the wind. To increase the relatively low speed generated by the rotor to a speed suitable for generating electricity and for the generator, a planetary transmission, also located within the nacelle of the wind turbine, has been developed. To achieve this, the speed of the rotor, connected to the transmission input shaft, is converted from a slow speed to a high speed by the planetary transmission and supplied to the generator via the transmission output shaft.

[0003] This type of planetary transmission is typically configured so that the ring gear is coaxially arranged with the sun gear, with the sun gear having an external toothing and the ring gear having an internal toothing. Planetary gears with external teeth are arranged at a radial distance between the sun gear and the ring gear. These external teeth of the planetary gears mesh with corresponding teeth of the ring gear and the sun gear. To rotatably mount the planetary gears, a planetary shaft is provided that rotatably accommodates the planetary gears and is non-rotatably connected to a planetary carrier. In addition to this conventional mounting of the planetary gears, it is also possible for the planetary gears to be non-rotatably connected to the planetary shaft, with the planetary shaft being rotatably mounted in the planetary carrier.

[0004] Typically, such planetary gears are rotatably mounted on the planet shaft by means of roller bearings.

[0005] In addition to such roller bearings, sliding bearings for planetary gears on planetary shafts are also known. DE 10 2013 221 265 A1 shows a planetary transmission in which the respective planetary gears are in exclusive sliding contact with the respective planetary shafts. To improve the mutual sliding of the surfaces involved and dissipate the generated heat, a lubricant film is formed between the surfaces involved. In this lubricant film, a lubricant bath is provided, through which the planetary gears pass as they rotate around the sun gear.

[0006] In addition to this type of bath lubrication, plain bearings are also known in which the lubricant is introduced directly between the sliding surfaces in sliding contact. This type of lubrication is known from DE 2702321 A1, in which a cavity is introduced into one of the sliding surfaces involved, into which the opening of the lubricant distribution unit terminates. The end of the lubricant distribution unit remote from the opening is functionally connected to a pump, which pumps the lubricant into the lubricant distribution unit, where it is then discharged at the opening and fills the cavity.

[0007] Continuously filling these cavities with a sufficient amount of lubricant ensures that lubricant reaches the load zone of the plain bearing during rotation of the sliding parts involved, forming a lubricant film that separates the two sliding parts under the prevailing hydrodynamic pressure conditions. This filling of the cavities can also be achieved by pumping lubricant at high pressure into the lubricant distribution unit, compensating for the inevitable lubricant losses. However, this is undesirable because such high pump pressures inevitably increase the amount of lubricant that escapes the plain bearing. If one wishes to avoid excessive lubricant escaping from the plain bearing, one can also fill the cavities sufficiently by introducing a large amount of lubricant into the cavities at low pump pressure. However, this requires a lubricant distribution unit with a larger cross-section, as the lubricant distribution unit has either a large number of channels with small cross-sections or a small number of channels with large cross-sections. However, since the channels of the lubricant distribution unit that supply the cavities of the plain bearing are routed through at least one of the sliding parts, such channels weaken the corresponding sliding part. If one wishes to compensate for this weakening of the sliding partner so that it can still transmit greater loads, this can only be achieved by making the corresponding sliding partner or the entire sliding bearing larger. Besides the installation space required, such a larger design inevitably leads to greater weight, which is undesirable in wind turbines, since such planetary gears are housed in the nacelle.

[0008] The invention is therefore based on the object of providing a planetary transmission for a wind turbine, the planetary gears of which have improved sliding bearings on the planet shafts which eliminate the above-mentioned disadvantages. Summary of the Invention

[0009] The sliding bearing is always sufficiently filled with lubricant at a low pump pressure if each cavity provided on the surface of one of the two sliding partners in sliding contact with each other is a lubricant recess having an axial length L of at least 60% of the axial width B of the planetary gear, a circumferential groove is provided which extends completely in the sliding partner arranged coaxially with respect to the other sliding partner provided with at least one lubricant recess of this type, and / or the circumferential groove extends in the sliding partner provided with at least one lubricant recess over its circumference and only between the lubricant recesses, and the lubricant distribution unit comprises a second opening which ends in the circumferential groove or ends opposite the circumferential groove.

[0010] This is based on the finding that providing the circumferential groove creates a lubricant reservoir in the plain bearing itself, which can be filled at a low pump pressure via one or two radial channels, from which the lubricant then flows into the lubricant recesses and ensures that these are sufficiently filled with lubricant - even if the axial length L of the lubricant recess is greater than / equal to 60% of the axial width B of the planet gear - to ensure good separation of the two sliding partners in the load area of the plain bearing.

[0011] If the axial width B1 of the circumferential groove is greater than the diameter D of the second opening and smaller than the axial length L of the at least one lubricant recess, assembly is simplified because the larger width B1 of the circumferential groove always means that, even if the two sliding partners are misaligned due to tolerances, the second opening always ends completely in the corresponding circumferential groove, i.e. the diameter D of the second opening is not covered by the misalignment.

[0012] If the respective lubricant recess has a continuation at its axial end, which has an extension B4 at least in the circumferential direction that is reduced compared to the extension B5 of the lubricant recess in the circumferential direction and the radial depression depth T1, edge slip on the sliding bearing is avoided when the planet gear is offset on the planet shaft.

[0013] If the axial symmetry axis of each lubricant recess holds an angle α between 90° and 120° relative to the center of the load zone LZ of the two sliding partners in sliding contact, the formation of a lubricant film in the load zone LZ of the sliding bearing is facilitated.

[0014] Compared to large and heavy planetary gears or planetary shafts, the production of the planetary transmission or the formation of sliding bearings on the planetary gears and planetary shafts can be handled more easily if a sleeve is provided: a first lateral surface of the sleeve is non-rotatably connected to the inner bore of the planetary gear or to the outer periphery of the planetary shaft and is penetrated by a radial opening, and a second lateral surface of the sleeve, which extends at a radial distance from the first lateral surface, is a surface that is in sliding contact with the surface of the corresponding other sliding partner.

[0015] The lateral surface opposite to the first lateral surface forms a surface in sliding contact with a surface of the other sliding fitting.

[0016] Alignment of the sleeve on the planet gear or the planet shaft is simplified if the lubricant distribution unit comprises a radial channel extending in one of the sliding partners, a circumferential groove being provided on a first lateral surface of the sleeve or on a circumferential surface of the planet gear or the planet shaft, with which the sleeve is non-rotatably connected,

[0017] And if the lubricant flow is not impeded by radial channels, radial channels with an axial width smaller than the axial width of the circumferential grooves lead to the corresponding grooves, since axially wider grooves also allow slight axial misalignment of the sleeve with the planet gear or with the planet shaft.

[0018] Axial starting is improved if an axial disk is provided on the planetary gear or the planet carrier, an annular edge of which is in axial sliding contact with the axial sliding partner.

[0019] When the surface of one sliding partner has a greater hardness than the surface of the other sliding partner, the sliding bearing has good wear resistance.

[0020] Simple production and good sliding properties with little wear are achieved if the low hardness of the surface of one sliding partner is pure steel hardness and if the harder surface of the respective other sliding partner is formed by a coating of a hard material. BRIEF DESCRIPTION OF THE DRAWINGS

[0021] In the attached figure:

[0022] Figure 1 A first embodiment of a planetary transmission for a wind turbine is shown;

[0023] Figure 2 Shown according to Figure 1 The second embodiment of the present invention;

[0024] Figure 3 Shown according to Figure 1 A third embodiment of the present invention;

[0025] Figure 4 Shown according to Figure 1 A fourth embodiment of the present invention;

[0026] Figure 5 A view showing a wind turbine is shown;

[0027] Figure 6a and Figure 6b Two sections through the planet axis are shown, and

[0028] Figure 7a and Figure 7b Another embodiment of a sleeve is shown. DETAILED DESCRIPTION

[0029] The present invention will now be described in more detail with reference to the accompanying drawings.

[0030] exist Figure 5 , a wind turbine 1 is schematically shown, which in particular houses a planetary transmission 4 and a generator 5 in a nacelle 3 mounted on a tower 2. Furthermore, a rotor 7 is provided, which is connected to a transmission input shaft 6. If wind blows towards this rotor 7, the transmission input shaft 6 starts to rotate, and the speed of the transmission input shaft 6 is changed from slower to faster by means of the planetary transmission 4 and is transmitted to the generator 5 via a transmission output shaft 8.

[0031] exist Figure 1 In FIG, a first embodiment of a planetary gear 4 of a wind turbine 1 is shown. The planetary gear 4 is formed by a ring gear 9 and a sun gear 10, wherein the sun gear 10 and the ring gear 9 are arranged coaxially with respect to each other. Planetary gears 11 are arranged in the radial distance between the ring gear 9 and the sun gear 10. Figures 1 to 4 Only one of the planetary gears 11 can be seen in the figure. The outer teeth (not shown) of the planetary gear 11 mesh with the outer teeth (not shown) of the sun gear 9 and the inner teeth (not shown) of the ring gear 10. Each planetary gear 11 is rotatably arranged on a planetary shaft 12. Due to the coaxial arrangement of the respective planetary gears 11 on the respective planetary shafts 12, a sliding bearing is formed between the inner surface 13.1 of the planetary gear 11 as a sliding partner and the outer surface 13.2 of the planetary shaft 12 as the other sliding partner. If the planetary transmission 4 is installed, then Figure 1 There is a narrow annular gap 14 between the surfaces 13.1, 13.2 of the sliding fittings 11, 12 involved in the present invention, which is shown in FIG. Figure 1 、 Figures 2 to 4 and shown in an enlarged size in FIG. 7 .

[0032] like Figure 1 As shown, the planet shaft 12 is connected to the planet carrier 15 in a non-rotatable manner.

[0033] Furthermore, two axial disks 16 are provided on the planet shafts 12, each of which is arranged between the planet carrier 15 and the planet gears 11 and is connected to the planet carrier 15, maintaining a small axial distance A1 from the planet gears 11 and forming an axial sliding bearing together with the planet gears 11 due to the annular edges 33 of the axial disks 16 being in axial sliding contact with the planet gears 11. For the sake of completeness, it should be pointed out that in another exemplary embodiment (not shown), the axial disks 16 can also be connected to the planet gears 11, wherein the planet carrier 15 then forms another axial sliding partner.

[0034] In order to improve the lubricity and long-term stability of the planetary shaft 12 and the planetary gear 11, both of which are made of steel, it is provided that the surface 13.1, 13.2 of one of the two sliding partners 11, 12 is only hardened, i.e. has only the hardness of steel, and the surface 13.1, 13.2 of the other sliding partner 11, 12 is additionally coated with a coating 17 made of a hard material, which has a hardness greater than the steel hardness of the other surface 13.1, 13.2. In particular, the hard material coating can be formed as an oxidized, nitrided, oxynitrided or carburized coating 17. In particular, in a first preferred embodiment, the hard material layer contains one of the elements titanium, aluminum, chromium and molybdenum. The hard material layer is preferably formed of at least one material selected from the group consisting of TiN, TiCN, Al2O3, TiAlN, CrN, AlCrN, MoN. In another preferred embodiment, the first layer is designed as an amorphous carbon layer or a diamond layer. Figure 1 In the exemplary embodiment shown, the outer surface 13.1 of the planet shaft 12 made of steel is coated with a coating made of Triondur CX + A coating 17 is formed of a DLC coating known from the applicant and having a layer hardness greater than or equal to 1000 HV. This coated surface 13.2 of the planet shaft 12 is in direct sliding contact with the inner surface 13.1 of the planet gear 11, which has a surface hardness corresponding only to a steel hardness of 55 to 62 HRC. For the sake of completeness, it should be noted that embodiments of the present invention are not necessarily limited to coating 17 on the stationary component, i.e., the surface 13.2 of the planet shaft 12. On the contrary, in another exemplary embodiment, the surface 13.2 of the planet shaft 12 may also have only one steel hardness, and the surface 13.1 of the planet gear 11 may be coated with one of the aforementioned coatings 17 to achieve a hardness greater than the steel hardness of the surface 13.2 of the planet shaft 12.

[0035] The description of the radial sliding bearings between the planetary gears 11 and the planetary shafts 12 in the previous paragraph is also applicable to the axial sliding bearings between the planetary carrier 15 and the axial disk 16 or between the axial disk 16 and the planetary gears 11. Figure 1 In FIG. 1 , the axial disk 16 is also provided with a coating 17 made of a hard material on its side facing the planetary gears 11 .

[0036] Figure 1 The radial and axial plain bearings shown are hydrodynamic plain bearings. These hydrodynamic plain bearings are based on the concept of independently generating a sufficiently high lubricant pressure separating the two sliding parts 11, 12 at the point in the bearing where force transmission occurs between them. As with roller bearings, since force transmission in plain bearings also occurs in the bearing's load zone LZ—that is, where the load absorbed by one of the sliding parts attempts to support the other—the annular gap 14 contracts almost wedge-shaped in the region of the load zone LZ. Any lubricant present outside this wedge-shaped contraction in the annular gap 14 is drawn into this contraction by the rotation of the sliding parts 11, 12 relative to the other sliding part 12, 11, resulting in a lubricant film with a sufficiently high lubricant pressure separating the two sliding parts 11, 12.

[0037] In order to ensure that the annular gap 14 is adequately filled with lubricant, a lubricant distribution unit 18 is provided, which is fed by a pump 19. Figure 1 This is achieved by pumping lubricant at a low pressure of less than 5 bar into an axial channel 20 extending through the planet shaft 12. This axial channel 20 is followed by radial channels 21.1-3 arranged in three groups. The radial channels 21.1-3 belonging to one group are spaced axially apart from the radial channels 21.1-3 of each other group at a distance A2 along the planet shaft 12 and have a diameter D. Furthermore, the radial channels 21.1-3 are open toward the annular gap 14 because they have a first opening 22.1 and a second opening 22.2. These (open) openings 22.1, 22.2 ensure that lubricant conveyed from outside the plain bearing ultimately reaches the annular gap 14.

[0038] like Figure 1 And shows that according to Figure 1 Sections bb, aa, and cc Figure 6a and Figure 6bTwo cavities in the form of lubricant recesses 23 are built into the surface 13 . 2 of the planet shaft 12 , wherein in this exemplary embodiment the respective axial length L of the lubricant recesses is approximately 90% of the width B of the planet gear 11 and the lubricant recesses are therefore suitable for generating a hydrodynamic state between the two sliding partners 11 , 12 during operation of the sliding bearing even at low pump pressures in almost the entire area in which the planet gear 12 covers the planet shaft 11 .

[0039] These lubricant recesses 23 are formed in a planar surface which is introduced into the original circular housing contour of the planet shaft 12, for example by milling. Figure 6a and Figure 6b It can be observed that Figure 1 The axial symmetry axis of each of the two lubricant recesses 23 in the exemplary embodiment shown in FIG is respectively at an angle α of 90° to the center of the load zone LZ, which angle can be increased to 120° in another embodiment (not shown) in order to optimize the hydrodynamic effect of the corresponding plain bearing.

[0040] like Figure 1 、 Figure 6a and Figure 6b What is disclosed, Figure 1 The sliding characteristics of the sliding bearing shown in FIG are essentially due to the sufficient filling of the lubricant recess 23 with lubricant, because this ensures that when the two sliding partners move relative to each other, a sufficiently large amount of lubricant is always delivered to the load zone LZ of the sliding bearing so that the two sliding partners are separated from each other by means of the hydrodynamic pressure generated in the load zone. However, since lubricant inevitably overflows from the sliding bearing during operation of the hydrodynamic sliding bearing, a first opening 22.1 and a second opening 22.2 are provided, through which the lubricant delivered by the pump 19 via the channels 20, 21 exits and compensates for the losses generated. As shown in FIG. Figure 6b - This view shows the Figure 1As can be easily seen from the cross-section aa or cc, the first opening 22.1 ends directly in the lubricant recess 23. On the other hand, the second opening 22.2 is only indirectly in contact with the lubricant recess 23, since the second opening opens outwardly relative to the circumferential groove 24, which has an axial width B1 that is slightly greater than the diameter D of the radial channel 22.1 and which has already been introduced into the planetary gear, for example by making a circuit in the surface 13.1 of the planetary gear 11, and thus the lubricant delivered by the pump 19 first enters the circumferential groove 24 and then flows into the lubricant recess 23 in the overlapping area between the lubricant recess 23 and the circumferential groove 24. Therefore, it is crucial that the lubricant recess 23 is filled more tangentially by the second opening 22.2 and the circumferential groove 24, since a sufficient amount of lubricant is always stored in the plain bearing itself via the circumferential groove 24, which is suitable for compensating for a lack of lubricant in the lubricant recess 23 by subsequently flowing into the lubricant recess 23, even if the pump pressure is temporarily unavailable. This deficiency could of course also be compensated by radial channels 21 having only first openings 22.1 that terminate only in the lubricant recess 23. However, this would have the disadvantage that a large number of thin radial channels 21 or a few thick radial channels 21 would have to be provided in order to provide a sufficiently large and rapidly flowing lubricant volume, which would, however, lead to a weakening of the planet shaft 12 due to the large number of radial channels or the thicker radial channels 21, which would inevitably lead to undesirable implementations (in the field of wind turbines) since larger and heavier planet shafts 12 or planetary gears 4 would be required to compensate for the reduced strength. In another exemplary embodiment (not shown), this pronounced effect of the interaction of the second openings 22.2 and the circumferential groove 24 for filling the lubricant recess 23 with lubricant can even lead to the radial channel 21.1 or 21.3 having the first openings 22.1, 22.3 ending directly in the lubricant recess 23 being omitted, and the lubricant recess 23 being filled exclusively with the lubricant located in the circumferential groove 24 and subsequently pumped via the second openings 23.2.

[0041] according to Figure 2 Exemplary embodiments and according to Figure 1 The exemplary embodiment of φ 2 differs in that the channels 20 , 21 extend in the planetary gear 11 , wherein, however, only one radial channel 21 . 2 is provided, which opens outwardly into a circumferential groove 24 on the planetary gear 11 .

[0042] According to Figure 1 Compared with the implementation method of Figure 3In the embodiment of the invention, a sleeve 25 is provided, the first lateral surface 27.1 of which is non-rotatably connected to the outer peripheral surface 32 of the planet gear 12. Consequently, the second lateral surface 27.2 of the sleeve 25, which is at a distance X from the first lateral surface 27.1, forms a sliding fit of the planet shaft 12, which sliding fit is in sliding contact with the planet gear 11 as a further sliding fit. For the sake of completeness, it should be mentioned that the second lateral surface 27.2 of the sleeve 25 - being the surface 13.3 in sliding contact with the planet gear 11 - is also provided with a coating 17 made of a hard material and therefore has a greater hardness than the surface 13.2 of the planet gear 11 which has only the hardness of steel. Similar to the embodiment according to Figure 1 The planetary axis 12, according to Figure 3 The planet shaft 12 is passed through by channels 20, 21. Figure 3 In the embodiment of the present invention, the radial channel 21 is continuous with the radial tubular opening 26 in the sleeve 25 in alignment with the radial channel 21 in the planet shaft 12, but instead of the radial channel 21, the radial opening 26 is provided with corresponding openings 22.1, 22.2, and the first opening 22.1 is thus introduced directly into the lubricant recess 23 embedded in the sleeve 25 or ends therein, and the second opening 22.2 emerges from the sleeve 25, thereby being opposite the circumferential groove 24 remaining in the planet gear 11. In addition, on a first lateral surface 27.1 of the sleeve 25 there are circumferential grooves 28, which adjoin the radial openings 26 in the sleeve 25. These grooves 28 facilitate the assembly of the sleeve 25 on the planet shaft 12, since, in accordance with Figure 3 In contrast to the illustration of FIG, the radial openings 26 and the radial channels 21 do not have to be aligned in the circumferential direction in order to ensure a reliable flow of lubricant through the sleeve 25. In addition, the grooves 28 and the radial channels 21 do not have to be precisely aligned in the axial direction during assembly because the grooves 28 have an axial width B3 that is greater than the axial width B2 of the radial channels 21. Even if the grooves 28 are aligned according to Figure 3 The same advantages naturally arise if the embodiment is arranged on the sleeve 25, when the groove 28 is arranged directly in the planet shaft 12, that is to say directly where the radial channel 21 ends.

[0043] Figure 4 Shown for Figure 2 Therefore, unlike the sleeve solution according to Figure 3In the embodiment of the present invention, the sleeve 25 is non-rotatably connected to the inner circumferential surface 32 of the planet gear 11 via the first lateral surface 27.1. The radial channel 21 extending in the planet gear 11 is also continuous with the radial opening 26 in the sleeve 25, wherein a groove 28 is also provided in the sleeve 25 in order to facilitate the alignment of the sleeve 25 on the planet gear 11 in the manner already described. By using the sleeve 25, the circumferential groove 2 into which the radial opening 26 opens is not as in the embodiment according to Figure 2 In the embodiment according to the invention, it is not introduced into the planetary gear 11, but into the sleeve 25. Figure 2 In contrast to the embodiment of FIG, in the embodiment according to the figure, it is not the planet shaft 12 but the sleeve 25 that is provided with a coating 17 made of a hard material.

[0044] In the preceding exemplary embodiments, it was assumed that the respective lubricant recess 23 was formed by a single flat surface lowered into the circular contour of the respective sliding partner. Figure 3 The sleeve 25 shown is different in that Figure 7a and Figure 7b In the embodiment of the sleeve 25 shown in FIG, the continuation 29 extending in the axial direction is connected to the axial end of the corresponding lubricant recess 23. Figure 7a As clearly shown, the width B4 of these continuations 29 in the circumferential direction is slightly reduced compared to the width B5 of the lubricant recess 23 in the circumferential direction. This setback ensures that, in the event of unavoidable bending of the corresponding sliding partner, edge slippage is avoided, which would otherwise result in the case of the continuation 29 having a width B5 corresponding to the lubricant recess 23. Even Figure 7b The cross section in FIG shows that the continuation portion 29 having a radial depression depth T1 has a depression depth T1 that is reduced compared to the radial depression depth T2 of the lubricant recess 23. In another exemplary embodiment (not shown), the continuation portion 29 can of course also have the same depression depth T2 as the lubricant recess 23 in order to increase the lubricant volume.

[0045] With the help of Figure 7a and Figure 7b The embodiment shown as an example of a sleeve 25 also differs from the previous embodiments in that the circumferential groove 24 is not formed in a sliding partner without lubricant recesses 23, but in a sliding partner provided with at least one lubricant recess 23, it extends along its circumference and only between the lubricant recesses 23. Figure 7a The sleeve 25 shown in FIG is provided with Figure 6a and Figure 6b The two opposite lubricant recesses 23 are shown in FIG. Figure 7a and Figure 7bIn the embodiment of the present invention, there is also a circumferential groove 24 formed by two partial sections 30.1, 30.2. These sections 30.1, 30.2 extend along the circumferential edge 30 of the sleeve 25 only between the respective lubricant recesses 23 before the sections open into a given lubricant recess 23 and thus ensure that the lubricant flows tangentially into the lubricant recess 23. Figure 7a and Figure 7b The sleeve 25 corresponds to Figure 3 The embodiment shown in FIG is connected to the planet shaft 12 (in Figure 7a and Figure 7b The sleeve is not shown in FIG. Figure 7a and Figure 7b In the embodiment according to Figure 7b As can be seen in the illustration of FIG, the sleeve 25 is also penetrated by radial openings 26. Figure 3 Compared with the implementation method of Figure 7a and Figure 7b In the embodiment of the radial extension 26 and its (second) opening 22.2, the radial extension 26 and its (second) opening 22.2 are therefore not as Figure 3 Instead of terminating on the second lateral surface 27.2 of the sleeve 25, it ends in the partial sections 30.1, 30.2 of the circumferential groove 24. If the lubricant reservoir formed by the sections 30.1, 30.2 is not yet suitable for providing sufficient lubricant for subsequent flow into the lubricant recess 23, then Figure 7b In the planetary gear 11 shown around the sleeve 25, an additional circumferential groove 24' can also be provided opposite one of the segments 30.1, 30.2. Since this additional circumferential groove 24' is only provided when required, it is only shown in dashed lines. For the sake of completeness, it should also be pointed out that Figure 7a and Figure 7b The many second openings 22 . 2 shown in FIG. 1 are merely examples and may also be limited to one or two such second openings 22 . 2 in another exemplary embodiment (not shown).

[0046] Description of Reference Numerals

[0047] 1 Wind turbine 2 Tower 3 Nacelle 4 Planetary transmission 5 Generator 6 Transmission input shaft 7 Rotor 8 Transmission output shaft 9 Sun gear 10 Ring gear 11 Planet gears 12 Planet shafts 13.n surface 14 Annular gap 15 Planet carrier 16 Axial disk 17 Coating 18 Lubricant distribution unit 19 Pump 20 Axial channel 21 Radial channel 22.1, 22.2 First and second opening 23 Lubricant recess 24 Circumferential groove 25 Sleeve 26 Radial opening 27.1, 27.2 First and second lateral surface 28 Circumferential groove 29 Continuation 30.1, 30.2 Segment 31 Circumferential edge 32 Circumferential surface 33 Annular edge

Claims

1. A planetary transmission device for a wind turbine, The planetary transmission device comprises a ring gear (10), a sun gear (9), a plurality of planetary gears (11) and a planetary carrier (15), wherein the planetary gears (11) are slidably mounted on the planetary shafts (12) of the planetary carrier, wherein: The planetary gear (11) is coaxially arranged on the planetary shaft (12). The planetary transmission has a surface (13.1; 13.2), wherein each cavity (23) extends axially and in the circumferential direction on the surface (13.1; 13.2) of the corresponding sliding partner and is formed as a radial recess relative to the rest of the housing contour of the sliding partner, and The planetary gear has a lubricant distribution unit (18; 20, 21), which is fed by a pump (19) and has first openings (22.1), wherein these first openings (22.1) end in the chamber (23), It is characterized in that Each cavity provided on the surface (13.1; 13.2) of one of the two sliding fittings in sliding contact with each other is a lubricant recess (23), the axial length L of the lubricant recess being at least 60% of the axial width B of the planetary gear (11), A circumferential groove (24; 30.1, 30.2) is provided, which extends completely in a sliding fitting arranged coaxially with respect to another sliding fitting provided with at least one lubricant recess (23) of this type and / or extends in the sliding fitting provided with the at least one lubricant recess (23) on its circumference and only between the lubricant recesses (23), and the lubricant distribution unit (18) comprises a second opening (22.2) which ends in the circumferential groove (24; 30.1, 30.2) or ends opposite the circumferential groove, The respective lubricant recess (23) has a continuation (29) at its axial end, the continuation having an extension B4 at least in the circumferential direction that is reduced compared to an extension B5 of the lubricant recess (23) in the circumferential direction.

2. The planetary transmission device of a wind turbine according to claim 1, It is characterized in that The axial width B1 of the circumferential groove (24; 30.1, 30.2) is greater than the diameter D of the second opening (22.2) and smaller than the axial length L of the at least one lubricant recess (23).

3. The planetary transmission device of a wind turbine according to claim 1 or 2, It is characterized in that The axial symmetry axis of each lubricant recess (23) maintains an angle α between 90° and 120° relative to the center of the load zone LZ of the two sliding partners in sliding contact.

4. The planetary transmission device of a wind turbine according to claim 1 or 2, It is characterized in that A sleeve (25) is provided, the first lateral surface (27.1) of which is non-rotatably connected to the inner bore of the planetary gear (11) or to the outer periphery of the planetary shaft (12) and is traversed by a radial opening (26), and A second lateral surface (27.2) extending at a radial distance X from said first lateral surface (27.1) is a surface (13.3) in sliding contact with a surface (13.1; 13.2) of a respective other sliding partner.

5. The planetary transmission device of a wind turbine according to claim 4, It is characterized in that The lubricant distribution unit (18) comprises a radial channel (21) extending in one of the sliding fittings, A circumferential groove (28) is provided, which is located on the first lateral surface (27.1) of the sleeve (25) or on a circumferential surface (32) of the planet shaft (12) or the planet gear (11), to which the sleeve (25) is non-rotatably connected, and Radial channels (21) having an axial width smaller than the axial width of the circumferential grooves (28) open into the corresponding grooves (28).

6. The planetary transmission device of a wind turbine according to claim 1 or 2, It is characterized in that An axial disk (16) is provided on the planetary gear (11) or the planetary carrier (15), and an annular edge (33) of the axial disk is in axial sliding contact with an axial sliding fitting.

7. The planetary transmission device of a wind turbine according to claim 1 or 2, It is characterized in that The surface (13.1, 13.2, 13.3) of one sliding fit has a greater hardness than the surface (13.1, 13.2, 13.3) of the respective other sliding fit.

8. The planetary transmission device of a wind turbine according to claim 7, It is characterized in that The low hardness of the surface (13.1, 13.2, 13.3) of a sliding fit is pure steel hardness, and The greater hardness of the surface (13.1, 13.2, 13.3) of the respective other sliding fitting is formed by a coating (17) made of a hard material.

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