• 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:
    The invention relates to a wind turbine gearbox (1) with an axle (5) and a toothed wheel (2), between which a conical plain bearing bush (4) and optionally a second conical plain bearing bush (20) is arranged, wherein the plain bearing bush (4, 20) a having a first end face (8) with a smaller diameter d (10) and a second end face (9) with a larger diameter D (11). Gear (2) and plain bearing bush (4, 20) are interconnected by a conical interference fit. The gear (2) has a radial projection (12), which forms a contact surface (13) for the second, larger end face (9) of the plain bearing bush (4, 20).
    公开号:AT513516A9
    申请号:T50067/2013
    申请日:2013-01-30
    公开日:2014-09-15
    发明作者:
    申请人:Miba Gleitlager Gmbh；
    IPC主号:
    专利说明:

    1
    The invention relates to a wind turbine transmission with an axle and a gear, wherein between the axle and the gear at least one plain bearing bush is arranged, and a wind turbine with a wind turbine gearbox.
    Current commercial solutions for the storage of planetary gears in planetary gears for wind turbines are only rolling bearing solutions. In these bearings, the problem often occurs that rotate due to circulating cyclic loads, the outer rings and as a result of additional axial forces, the bearings and axially leave their desired position and emigrate. To overcome this problem, bearing solutions without outer rings have been proposed.
    Plain bearing solutions for planetary gears of wind turbines have also been described, but so far not yet commercially implemented. However, the likelihood that slide bearings also emigrate due to the acting loads is very high.
    The present invention is therefore an object of the invention to provide a sliding bearing for wind turbine gearbox, in which the migration of the plain bearings is prevented.
    To solve the problem is provided in a wind turbine gearbox, that the at least one plain bearing bush is connected via a conical interference fit with the gear, wherein the plain bearing bush has a first end face and one of these along a longitudinal center axis through the Gleitlagerbusche a second end face, and wherein the first end face a diameter d and 2/23 N2012 / 31800 2 have the second end face a diameter D, wherein the diameter D is greater than the diameter d and wherein subsequently to the end face with the diameter D a contact surface is formed for the at least one plain bearing bush, and in the case of the wind power plant mentioned at the outset, that a correspondingly designed wind turbine transmission is used.
    The advantage here is that can be significantly improved by the physical strength of the plain bearing bush by a simple design measure. So there are no further measures for this, such as the bonding or welding of the plain bearing bush with the gear required. In addition, a better centering of the gear is achieved with the conical interference fit, whereby a more uniform running of the gear can be obtained. It can be achieved with this embodiment of the plain bearing bush that even in the worst case that the plain bearing bushing begins to rotate due to cyclic loads and resulting deformations, by acting in the axial direction forces a provision of the plain bearing bush. Thus, the axial migration can be better prevented. By the contact surface for the plain bearing bush resulting axial forces are supported from the conical bearing seat, whereby the prevention of Auswandems the plain bearing bush is supported.
    Preferably, the ratio of large diameter to small diameter of the plain bearing bush (D / d) is at most 1.2, wherein according to a further embodiment, this ratio D / d is preferably selected from a range of 1.0001 to 1.02 in order to prevent the To limit the axial force acting on the contact surface.
    The Aniagefläche is preferably formed by the gear itself, as this assembly of this assembly can be simplified. For this purpose, it may be provided that the contact surface is formed by a radial projection of the gear, since this is easy to produce.
    According to a further embodiment it can be provided that two plain bearing bushes between the gear and the axis for supporting the gear 3/23 N2012 / 31800 3 are arranged, wherein the two plain bearing bushes are arranged such that the two second end faces with the larger diameter D to each other to assign. There are thus the above-mentioned effects further improved because the axial migration of the plain bearing bushings can be better prevented by the two counter-mounted plain bearing bushes.
    The contact surfaces for the plain bearing bushes can be formed in this embodiment by an annular web, which is formed on the gear radially inwardly toward the axis extending. Preferably, this ring land is arranged on the gear viewed in the axial direction in the middle. The annular web has the additional advantage that, if necessary, a lubricant can be supplied to the bearings through this.
    But it can also be provided that the contact surface is formed in each case by a sliding bearing by the respective other sliding bearing, so that in this regard no further measures are to be taken on the gear.
    The plain bearing bush (s) may be formed as a multi-layer sliding bearing. In addition to the well-known effect that thus the tribological properties of the plain bearing can be tailored to the particular requirements, it is thus also achieved that higher frictional forces are provided by an appropriate combination of materials with the gear, whereby the holding force of the interference fit can be increased can.
    It can be provided that the multilayer plain bearing in the region of the axis has, as known, a sliding layer, wherein according to a further embodiment, the sliding layer over the length of the plain bearing bush in the axial direction has a uniform layer thickness.
    The sliding layer can be formed into the region of the end face with the diameter D and / or into the region of the end face with the diameter d. It is thus provided in the case of rotation of the plain bearing bush (s) also in the radial direction, a corresponding sliding surface, i. an Axialla- 4/23 N2012 / 31800 4 ger, which in this case, the plain bearing bush (s) can be better protected against damage or can.
    In addition to the interference fit, the plain bearing bush or the plain bearing bushes can additionally be positively connected to the toothed wheel, as a result of which the local stability of the plain bearing bushing (s) can be further improved.
    However, it can also be provided that a surface of the plain bearing bush (s) bearing against the toothed wheel has a surface roughness. Due to the surface roughening holding force of the press fit can be further increased, whereby also the local strength of the plain bearing bush can be further improved.
    In the embodiment of the gear with the above-mentioned ring land this may be formed spaced to form an intermediate space to the axis. It can thus be created a simple way to supply lubricant.
    But it is also possible that in the intermediate space a connecting line opens, which connects the intermediate space with the ambient atmosphere, whereby in terms of lubricant distribution, the throttling effect of the bearings can be reduced.
    For a better understanding of the invention, this will be explained in more detail with reference to the following figures.
    Each shows in a highly schematically simplified representation:
    Figure 1 shows a detail of a wind turbine gear cut in side view.
    Fig. 2 shows a detail of a variant of the wind turbine transmission cut in side view;
    3 shows a detail of a further embodiment variant of the wind turbine gearbox in side view; 5/23 N2012 / 31800 5
    Fig. 4 shows a detail of another embodiment of the wind turbine gearbox cut in side view.
    By way of introduction, it should be noted that in the differently described embodiments, the same parts are provided with the same reference numerals or the same component names, wherein the disclosures contained in the entire description can be mutatis mutandis to the same parts with the same reference numerals or component names. Also, the location information chosen in the description, such as top, bottom, side, etc. related to the immediately described and illustrated figure and are to be transferred to the new situation mutatis mutandis when a change in position.
    As is known, wind turbines comprise a tower at whose upper end a nacelle is arranged, in which the rotor is mounted with the rotor blades. This rotor is via a wind turbine gearbox with a generator, which is also located in the nacelle, operatively connected, wherein the low speed of the rotor is translated into a higher rotational speed of the generator rotor via the wind turbine gearbox. Since such embodiments of wind turbines belong to the prior art, reference should be made at this point to the relevant literature.
    In Fig. 1, a detail of a first embodiment of a wind turbine gearbox 1 according to the invention is shown. This has at least one gear 2. This gear 2 is arranged in the wind turbine gear 1 in meshing engagement between a second and a third gear (both not shown). For this purpose, the at least one gear 2 has an outer end toothing 3.
    In the embodiment of the wind turbine transmission 1 as a planetary gear, in particular as the main gear of a wind turbine, the second gear is designed as a sun gear with a spur gear, which is rotatably connected to a shaft leading to the generator rotor. The sun gear is usually surrounded by a plurality of gears 2, the planetary gears, for example two, preferably three or four. 6/23 N2012 / 31800 6
    The third gear is designed as a ring gear, which surrounds the at least one gear 2 and the gears 2 in the radial direction and which also has at least partially on an inner surface a toothing, in meshing engagement with the outer end teeth 3 of the gear 2 and Gears 2 is. The ring gear is rotatably connected to a rotor shaft of the rotor of the wind turbine or rotatably connected to the housing of the wind turbine gearbox 1.
    The teeth of the gears 2 in the wind turbine transmission 1 can be designed as a straight toothing or in particular as helical toothing.
    The at least one gearwheel 2 (only one gearwheel 2 will be described below, these embodiments also being transferable to all or several of these gearwheels 2 of the wind turbine gearbox 1) is provided via a plain bearing in the form of a plain bearing bush 4, in particular a multilayer plain bearing, on an axis 5, so for example a planetary pin (the so-called planetary axis) stored. This axis 5 can either be integrally formed with at least part of a gear carrier 6, in particular a planet carrier, or it is used as a separate component in a bore of the gear carrier 6.
    It should be noted that not only single-stage versions of such wind turbine transmissions 1 in the invention are possible, but also multi-stage, for example, two or three stages, including in at least one gear 2, in particular a planetary gear, more spur gears can be integrated. In addition, parallel transmissions, as described for example in EP 2 284 420 B1, can also be represented within the scope of the invention. Reference is therefore made to this document, which belongs to this description to representational description. Accordingly, the wind turbine transmission 1 may have a simple planetary gear and a parallel two- or multi-stage planetary gear or generally more planetary gear.
    Furthermore, it should be noted again that, although preferred, the invention is not only used in planetary gear units of wind turbines, but can generally be used in transmissions for wind turbines, in particular 7/23 N2012 / 31800 7 to translate the slow speed of the rotor of a wind turbine in a higher speed.
    The plain bearing bush 4 is rotatably connected via a press fit with the gear 2. The press fit is conical. For this purpose, the plain bearing book 4 is frusto-conical and has along a longitudinal central axis 7 opposite end surfaces 8, 9. The first end face 8 has an outer diameter d 1D and the second end face 9 has an outer diameter D 11, wherein the first diameter d 10 is smaller than the second diameter D 11.
    The absolute size of the diameter d 10 and D 11 depends on the respective gearbox size. However, the ratio D / d is preferably at most 1.2, in particular at most 1.1. In particular, the ratio D / d is selected from a range of 1.0001 to 1.02, preferably from a range of 1.0001 to 1.008.
    In particular, the diametric cone expansion can be between 0.01% and 0.6%, for example 0.1%, of the outer diameter D 11.
    The plain bearing bushing 4 may be formed in one layer and in this case consists of a sliding material, that is to say a material which has a reduced friction in relation to the material of the axle 5. For this purpose, this sliding material can be selected from the materials mentioned below for a sliding layer.
    The plain bearing bush 4 according to the invention can already be produced in the appropriate form, for example from a corresponding sheet metal blank. But it is also possible to form this by widening with a corresponding tool from a cylindrical plain bearing bush. For example, this widening can take place simultaneously with the press-fitting of the sliding bearing bush 4 into the gearwheel 2 to form the press fit.
    In Figs. 2, 3 and 4 are sections of further and possibly independent embodiments of the wind turbine transmission 1 is shown, wherein 8/23 N2012 / 31800 8 again the same reference numerals or component names are used as in the previous Fig. 1. To avoid unnecessary repetition, reference is made to the detailed description of FIG.
    2, the gear 2 in the region of the second (large) diameter D 11 of the end face 9 of the plain bearing bush 4 on a radial projection 12, which is preferably formed annularly. The radial projection 12 serves as axial securing of the plain bearing bush 4, so that it rests with the end face 9 on the radial projection 12 at least temporarily, so this forms a contact surface 13 for the plain bearing bush 4 in the axial direction. For this purpose, the radial projection 12 protrudes radially inwards, so that an overlap - viewed in the axial direction - with the plain bearing bush is present.
    The radial projection 12 may extend continuously over the entire circumference of the plain bearing bushing 4. But it is also possible that only a single radial projection 12 or more radial projections 12 are arranged distributed over the inner circumference of the gear 2, which extend only a portion of 360 ° of the circumference.
    Further, it is possible that the radial projection 12 extends to the axis 5 and spaced from this.
    The radial projection 12 is preferably formed integrally with the gear 2. But it is also possible that this is formed by a separate component which is connected to the gear 2.
    According to a variant embodiment, the radial projection 12 may be arranged instead of the gear 2 on the axis 5 (see FIG. 1), for example as a ring land.
    This radial projection 12 for receiving axial forces also in the embodiment of FIG. 1 available. 9/23 N2012 / 31800 9
    From Fig. 2 it is further seen that viewed in the radial direction, the plain bearing bushing 4 need not necessarily be arranged in alignment with the gear 2, as shown in Fig. 1, but also an offset in the axial direction arrangement is possible, in which case the plain bearing bush 4 preferably protrudes in the axial direction over the gear 2 in the region of the first diameter d 10.
    Dashed line in Fig. 2, the embodiment of the plain bearing bush 4 is shown as a multi-layer sliding bearing.
    The multilayer sliding bearing consists at least of a support layer 14, which consists for example of a steel, and a sliding layer 15, which is applied radially inwardly on the support layer 14. The sliding layer 15 forms a running surface 16 for the axis 5 (see FIG. 1).
    In addition to this two-layered embodiment of the multilayer plain bearing, there is also the possibility within the scope of the invention that intermediate layers are arranged between the sliding layer 15 and the support layer 14, for example a bearing metal layer and / or at least one bonding layer and / or one diffusion barrier layer.
    Examples of materials for the individual layers of the multilayer plain bearing are known from AT 509 624 B1, to which reference is made in this regard and which belongs to this scope to the description of the present invention.
    But there are also single-layer variants of the plain bearing bush 4 possible. For example, this may consist of a copper alloy, in particular bronze or brass.
    The sliding layer 15 or all layers of the multilayer plain bearing bush can also have a frusto-conical shape. On the other hand, it is possible, as shown in Fig. 2, that the sliding layer 15 over the length of the plain bearing bush 4 in the axial direction has a uniform layer thickness. 10/23 N2012 / 31800 10
    According to a further embodiment variant of the plain bearing bush 4, it can be provided that the sliding layer 15 is formed up to the area of the end face with the diameter D, as shown by dashed lines in FIG. 2. The sliding layer 15 thus has not only an extension in the longitudinal direction of the plain bearing bush 4 but also in the radial direction. In principle, the sliding layer 15 can be applied separately to the end face 9 of the plain bearing bush 4.
    Of course, there is also the possibility that such a sliding layer is also applied to the end face 8 of the plain bearing bush 4, so that therefore the support layer 14 is coated on both sides on the end faces 8, 9 at least partially.
    In the axial course, in each case adjacent to the end face 8 and / or the end face 9 of the slide bearing bushing 4, a thrust washer between the slide bearing bush 4 and the gear carrier 6 (see FIG. 1) can be further provided. In this case, the sliding layer 15 of the plain bearing bush 4 can be pulled up into the end face to the thrust washers.
    The plain bearing bush 4 can therefore fulfill an axial bearing function in addition to the radial bearing function.
    In the embodiment of the wind turbine transmission 1 of FIG. 3, instead of the radial projection 12 of FIG. 2, a particular disc-shaped component 17 is arranged, which can be connected to either the gear 2 or the axis 5 (see Fig. 1) and the Contact surface 13 for the plain bearing bush 4 forms.
    Furthermore, it is shown by dashed lines in FIG. 3 that the plain bearing bush 4 can additionally or alternatively also be connected to the gearwheel 2 via at least one interlocking element 18. This form-fit element 19 can be, for example, a longitudinal web arranged on the outer surface of the plain bearing bush 5, which faces the toothed wheel 2, which is inserted into a corresponding longitudinal groove of the toothed wheel 2. The longitudinal bar can be at least one 11/23 N2012 / 31800 11
    Part of the region or over the entire length between the two end faces 8, 9 of the plain bearing bush 4 extend.
    It is also possible for more than one longitudinal web to be arranged on the outer surface of the sliding bearing bush 4, for example two, three, four, etc., in which case they are preferably distributed symmetrically over the circumference of the plain bearing bush 4.
    However, the form-locking element 18 may also have another suitable shape.
    In the lower part of the plain bearing bushing 4 in Fig. 3 is a variant of the positive connection of the plain bearing bush 4 with the sliding bearing bush 4 receiving bore in the gear 2 is shown by dashed lines, the representation is disproportionate for better identification. In this embodiment, which can be provided alternatively or in addition to the positive-locking element 18, has a voltage applied to the gear 2 surface 19 of the plain bearing bush 4, i. the lateral surface at least partially, in particular in its entirety, a surface roughness on. The surface roughening can be produced by appropriate abrasive removal of material, for example by sandblasting or by erosion. In particular, the surface 19 may have an arithmetic mean roughness Ra according to DIN EN ISO 4287, which is selected from a range with a lower limit of 1 pm and an upper limit of 20 pm, in particular selected from a range with a lower limit of 4 pm and an upper limit of 10 pm. Furthermore, this surface 19 may have a maximum roughness profile height Rz according to DIN EN ISO 4287, which is selected from a range with a lower limit of 2 pm and an upper limit of 100 pm, in particular selected from a range with a lower limit of 20 pm and an upper limit of 70 pm.
    In Fig. 4 a section of a further embodiment of the wind turbine transmission 1 is shown in side view cut. Shown again is the gear 2, which is mounted on the axis 5 via two plain bearing bushes 4, 20 12/23 N2012 / 31800 12, including the plain bearing bushes between the axis 5 and the gear 2 are arranged.
    The plain bearing bushes 4, 20 in turn have a conical shape and arranged in conical seats in the gear 2, whereby the conical press fit is formed. In this case, the arrangement takes place such that the end faces 9 with the respective larger diameter 11 of the two plain bearing bushes 4, 20 assign each other. In other words, the plain bearing bushes 4, 20 are arranged in the gear 2 with in the axial direction outwardly tapering cross-section. As a result, the two plain bearing bushes 4, 20 are arranged opposite in the gear 2.
    Between the two plain bearing bushes 4, 20, a gap 21 is formed, into which an annular web 22 of the gear 2 protrudes. The annular web 22 forms the contact surfaces 13 for the end faces 9 of the two plain bearing bushes 4, 20th
    According to a preferred embodiment, the annular web 22 does not extend in the radial direction to the axis 5, so that it is arranged spaced apart from the surface of the axis 5 with the formation of a gap 23. This intermediate space 23 can be used to supply a lubricant, in particular lubricating oil, for which purpose a supply line 24 for the lubricant opens into this intermediate space 23. Preferably, the feed line 24 is guided by the axis 5, but may also be guided by the gear 2.
    Alternatively or additionally, there is the possibility that the lubricant is supplied directly to the running surfaces 16, as shown in Fig. 4 by dashed lines.
    The gap 24 may also be connected to a connection line 25 with the ambient atmosphere. Preferably, the connecting line 25 is guided by the axis 5 (as shown in Fig. 4 by dashed lines), but may also be guided by the gear 2. It can thus be reduced, the throttle effect of the bearings. 13/23 N2012 / 31800 13
    According to a specific embodiment variant of the wind turbine transmission 1 according to FIG. 4, it can be provided that the annular web 22 is dispensed with and the two plain bearing bushes 4, 20 are arranged so that they abut one another with their end faces 9. Thus, in each case one of the two plain bearing bushes 4, 20 forms the contact surface 13 for the other plain bearing bush 4, 20.
    With regard to the further possible embodiments of the wind turbine transmission 1 of this embodiment, in particular with regard to the plain bearing bushes 4, 20, reference is made to the above statements.
    To form the conical interference fit cylindrical bushings 4, 20 can be used in all embodiments of the invention. These are introduced into the corresponding receptacles in the gear 2 and then widened to a conical shape with a corresponding tool.
    For the sake of order, it should finally be pointed out that for better understanding of the construction of wind turbine transmission 1, this or its components have been shown partly unevenly and / or enlarged and / or reduced in size. 14/23 N2012 / 31800
    LIST OF REFERENCE NUMBERS
    Wind Turbine Gearbox
    gear
    External spur gearing
    plain bearing bush
    axis
    Gear carrier longitudinal center axis
    face
    face
    diameter
    diameter
    radial projection
    contact surface
    backing
    Overlay
    tread
    module
    Form final element
    surface
    plain bearing bush
    gap
    ring land
    gap
    feed
    Connecting cable 15/23 N2012 / 31800
    权利要求:
    Claims (18)
    [1]
    1 wind turbine gearbox (1) having an axis (5) and a gear (2), wherein between the axis (5) and the gear (2) at least one plain bearing bush (4, 20) is arranged, characterized in that the at least one plain bearing bush (4, 20) is connected to the toothed wheel (2) via a conical press fit, wherein the at least one plain bearing bush (4, 20) has a first end face (8) and one of these along a longitudinal central axis (7) through the at least one Plain bearing bush (4, 20) second end face (9), and wherein the first end face (8) has a diameter d (10) and the second end face (9) has a diameter D (11), wherein the diameter D (11) larger is as the diameter d (10) and wherein subsequently to the end face (9) with the diameter D (11) a bearing surface (13) for the at least one plain bearing bush (4, 20) is formed.
    [2]
    2. wind turbine transmission (1) according to claim 1, characterized in that the ratio of D (11) / d (10) is at most 1.2.
    [3]
    3. wind turbine transmission (!) According to claim 2, characterized in that the ratio D (11) / d (10) is selected from a range of 1.0001 to 1.02.
    [4]
    4. wind turbine transmission (1) according to one of claims 1 to 4, characterized in that the bearing surface (13) by the gear (2) is formed.
    [5]
    5. wind turbine transmission (1) according to claim 4, characterized in that the contact surface by a radial projection (12) of the gear (2) is formed. 16/23 N2012 / 31800 2
    [6]
    6. wind turbine transmission (1) according to one of claims 1 to 5, characterized in that two plain bearing bushes (4, 20) between the gear (2) and the axis (5) for supporting the gear (2) are arranged, wherein the two Plain bearing bushes (4, 20) are arranged such that the two second end faces (9) with the larger diameter D (11) assign each other.
    [7]
    7. wind turbine transmission (1) according to claim 6, characterized in that the Anlagefläehen (13) by an annular web (22) are formed, which is formed on the gear (2) radially inwardly in the direction of the axis (5) extending ,
    [8]
    8. wind turbine transmission (1) according to claim 6, characterized in that the abutment surface (13) for a respective sliding bearing (4, 20) by the respective other sliding bearing (20, 4) is formed.,.
    [9]
    9. wind turbine transmission (1) according to one of claims 1 to 8, characterized in that the plain bearing bush (s) (4, 20) is designed as a multi-layer sliding bearing.
    [10]
    10. wind turbine transmission (1) according to claim 9, characterized in that the multi-layer sliding bearing in the region of the axis (5) has a sliding layer (15).
    [11]
    11. wind turbine transmission (1) according to claim 10, characterized in that the sliding layer (15) over the length of the plain bearing bush (4) in the axial direction has a uniform layer thickness.
    [12]
    12. wind turbine transmission (1) according to claim 10 or 11, characterized in that the sliding layer (15) into the region of the end face (9) with 17/23 N2012 / 31800 3 the larger diameter D (11) and / or up in the region of the end face (8) with the diameter d (10) is formed.
    [13]
    13. wind turbine transmission (1) according to one of claims 1 to 12, characterized in that the plain bearing bushing (s) (4, 20) is additionally positively connected to the gear (2).
    [14]
    14. wind turbine transmission (1) according to one of claims 1 to 13, characterized in that on the gear (2) abutting surface (19) of the plain bearing bush (s) (4, 20) has a surface roughness.
    [15]
    15. wind turbine transmission (1) according to one of claims 7 to 14, characterized in that the annular web (22) to form a gap (23) spaced from the axis (5) is formed.
    [16]
    16. wind turbine transmission (1) according to claim 15, characterized in that in the intermediate space (23), a connecting line (25) opens, which connects the intermediate space (23) with the ambient atmosphere.
    [17]
    17. Wind turbine with a wind turbine gearbox (1), characterized in that the wind turbine gearbox (1) is designed according to one of the preceding claims.
    [18]
    18/23 N2012 / 31800
    类似技术:
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    同族专利:
    公开号 | 公开日
    US10294926B2|2019-05-21|
    DK2951467T3|2017-09-04|
    CN104956126A|2015-09-30|
    CN104956126B|2018-07-20|
    KR20150110808A|2015-10-02|
    EP2951467A1|2015-12-09|
    WO2014117197A1|2014-08-07|
    AT513516A4|2014-05-15|
    US20150369352A1|2015-12-24|
    AT513516B1|2014-05-15|
    ES2637511T3|2017-10-13|
    KR102184103B1|2020-11-30|
    EP2951467B1|2017-05-17|
    引用文献:
    公开号 | 申请日 | 公开日 | 申请人 | 专利标题
    JPS4827143A|1971-08-12|1973-04-10|
    DE3318967A1|1982-05-25|1984-02-02|Hydro-Pneumatic AB, 523 01 Ulricehamn|Mounting comprising a sliding-contact or rolling-contact bearing bush|
    US4939827A|1987-10-20|1990-07-10|Diado Metal Company Ltd.|Method of manufacturing a bearing device including a housing with a flange at one end thereof and a bearing bush press-fitted thereinto|
    US20110176907A1|2010-01-19|2011-07-21|Chris Groves|Multi-piece turbocharger bearing|
    AT509624B1|2010-04-14|2012-04-15|Miba Gleitlager Gmbh|WIND TURBINE|
    US2318114A|1940-10-26|1943-05-04|Westinghouse Electric & Mfg Co|Thrust bearing|
    FR1046851A|1951-09-22|1953-12-09|Improvements to quick-clamping and centering chucks|
    FR1110347A|1954-07-22|1956-02-10|Inst Francais Du Petrole|Devices for the lubrication of gears|
    DE1216654B|1961-05-25|1966-05-12|Hurth Masch Zahnrad Carl|Centering clamping device|
    DE1425132A1|1962-09-07|1968-12-12|Stal Laval Turbin Ab|Device on a thrust bearing|
    DE1985822U|1965-11-13|1968-05-22|Rheinstahl Huettenwerke Ag|DEVICE FOR SUPPLYING SLIDING BEARINGS OF PLANETARY WHEELS BEARING IN THE PLANETARY WHEEL CARRIER OF A PLANETARY GEAR WITH OIL.|
    DE1650681B2|1967-09-19|1972-12-21|Eisenwerk Wulfel, 3000 Hannover Wulfel|LUBRICATION DEVICE FOR THE BEARINGS OF THE PLANETARY WHEELS IN PLANETARY GEARS WITH REVOLVING PLANETARY WHEEL BEARING|
    US3837068A|1971-06-14|1974-09-24|Federal Mogul Corp|Method of making a composite high-strength sleeve|
    US3736705A|1971-06-24|1973-06-05|Bendix Corp|Thrust bearing arrangement for a deadshaft mounted grinder wheelhead|
    NO129163B|1971-07-15|1974-03-04|N Tharaldsen|
    JPS4896382U|1972-02-21|1973-11-15|
    FR2211071A5|1972-11-17|1974-07-12|Vandervell Products Ltd|
    US3821908A|1972-12-12|1974-07-02|Allis Chalmers|Retainer for planet pinion shaft|
    US4083612A|1976-10-15|1978-04-11|Smith International, Inc.|Non-rotating stabilizer for earth boring and bearing therefor|
    US4271928A|1978-07-11|1981-06-09|Rolls-Royce Limited|Lubricant supply device|
    JPS5849017U|1981-09-30|1983-04-02|
    JPS58166122A|1982-03-26|1983-10-01|Hitachi Ltd|Journal bearing|
    US4771654A|1983-09-17|1988-09-20|Kinichi Shinjo|Gear system|
    JPS6175520U|1984-10-24|1986-05-21|
    JPH0214565B2|1985-04-19|1990-04-09|Ube Industries|
    JPS62151426A|1985-12-26|1987-07-06|Shin Kobe Electric Mach Co Ltd|Production of prepreg|
    JPS62151426U|1986-03-19|1987-09-25|
    JP2616922B2|1987-05-22|1997-06-04|株式会社日立製作所|Screw compressor|
    US5102379A|1991-03-25|1992-04-07|United Technologies Corporation|Journal bearing arrangement|
    DE4336915C2|1993-10-28|1996-09-12|Renk Ag|Slide bearing combination|
    US5743658A|1995-12-15|1998-04-28|Renk Aktiengesellschaft|Lubricated journal bearing|
    KR19980066271A|1997-01-22|1998-10-15|김광호|Conical bearing device applied to motor|
    GB9818097D0|1998-08-19|1998-10-14|Corac Group Plc|Improvements in and relating to bearing assemblies|
    JP2000320649A|1999-05-11|2000-11-24|Honda Motor Co Ltd|Gear with bearing|
    US6755570B1|1999-06-11|2004-06-29|Seagate Technology Llc|Single piece hub with integral upper and lower female cones and method for making the same|
    US6695480B1|1999-07-13|2004-02-24|A.W. Chesterton Co.|Opposed flow seal/bearing assembly|
    US6663289B1|1999-11-29|2003-12-16|Pablo Javier Iljin|Bearing with multi-layered spacers|
    DE19960157A1|1999-12-14|2001-06-21|Schaeffler Waelzlager Ohg|Lubricant supply for a planetary gear|
    US6929402B1|2002-04-11|2005-08-16|Morgan Construction Company|Journal bearing and thrust pad assembly|
    US7090401B2|2003-01-21|2006-08-15|Seagate Technology Llc|Grooving pattern for grooved fluid bearing|
    US7540664B2|2003-01-21|2009-06-02|Seagate Technology Llc|Grooves on both the moving and the stationary mating fluid dynamic bearing surfaces for performance enhancement|
    JP4380699B2|2006-12-28|2009-12-09|トヨタ自動車株式会社|Planetary gear device and automatic transmission|
    US20080268997A1|2007-04-24|2008-10-30|Gooden James T|Lubrication path in a planetary gear unit for a transmission|
    AT456748T|2007-10-29|2010-02-15|Grundfos Management As|PUMP UNIT|
    DE102008000900A1|2008-04-01|2009-10-08|Zf Friedrichshafen Ag|planetary gear|
    DE102009010001A1|2009-02-23|2010-09-02|Ims Gear Gmbh|Planetary gear with an axial groove bearing pin|
    DE102010000809B4|2009-07-13|2014-10-30|manroland sheetfed GmbH|Compact axial-radial bearing|
    CN101956676A|2009-07-14|2011-01-26|郭溪泉|Static-dynamic pressure self-alignment type spindle oil film bearing of wind driven generator|
    SI2284420T1|2009-08-10|2012-08-31|Zf Wind Power Antwerpen Nv|Parallel gear unit for a gearbox for a wind turbine|
    JP5249902B2|2009-10-16|2013-07-31|三菱重工業株式会社|Planetary bearing structure|
    DE102009049769A1|2009-10-16|2011-04-21|Suzlon Energy Gmbh|Bearing arrangement for a wind turbine|
    US20110140448A1|2009-12-15|2011-06-16|Mitsubishi Heavy Industries, Ltd.|Wind-turbine-generator-system transmission and wind turbine generator|
    JP5345048B2|2009-12-15|2013-11-20|三菱重工業株式会社|Wind power transmission and wind power generator|
    WO2011095349A1|2010-02-05|2011-08-11|Aktiebolaget Skf|Hybrid wind turbine blade bearing|
    JP2011208701A|2010-03-29|2011-10-20|Nippon Densan Corp|Spindle motor and disk driving device|
    DK2383480T3|2010-04-30|2013-01-21|Winergy Ag|Planetary gear for a wind turbine|
    CN201802752U|2010-08-26|2011-04-20|大连三环复合材料技术开发有限公司|Three-way combined self-lubricating sliding spindle bearing of wind turbine|
    KR20120054559A|2010-08-31|2012-05-30|다이도 메탈 고교 가부시키가이샤|Planetary gear train, bearing structure, wind turbine generator, and manufacture method of planetary gear|
    JP5511968B2|2010-08-31|2014-06-04|三菱重工業株式会社|Planetary gear mechanism, wind power generator, and carrier manufacturing method for planetary gear mechanism|
    US8500333B2|2011-05-24|2013-08-06|Siemens Industry, Inc.|Self aligning oil film bearing|
    EP2662598A1|2012-05-08|2013-11-13|ZF Wind Power Antwerpen NV|Planetary gear stage with plain bearings as planet bearings|DE102014010585A1|2014-07-17|2016-01-21|Diehl Metall Stiftung & Co. Kg|Brass component and use of the component|
    ES2765403T3|2015-05-07|2020-06-09|Flender Gmbh|Planetary transmission mechanism|
    AT517719B1|2015-09-15|2017-04-15|Miba Gleitlager Austria Gmbh|Planetary gear for a wind turbine|
    CN107299966B|2016-04-15|2019-09-24|南京高速齿轮制造有限公司|A kind of planetary transmission|
    DE102017114584A1|2017-06-29|2019-01-03|Wobben Properties Gmbh|Wind turbine rotary joint, and wind turbine with selbiger|
    DE102017222901A1|2017-12-15|2019-06-19|Zf Friedrichshafen Ag|Planetary gear stage with a sliding bearing arrangement, in particular for a Planetenradlagerung in a wind turbine gearbox|
    AT521071B1|2018-03-23|2019-12-15|Miba Gleitlager Austria Gmbh|Wind turbine transmission and method for producing a wind turbine transmission|
    DE102018214083A1|2018-08-21|2020-02-27|Zf Friedrichshafen Ag|Planetary gear for a wind turbine|
    CN111547216A|2020-04-09|2020-08-18|武汉船用机械有限责任公司|Nacelle propeller and method for mounting stator of propulsion motor thereof|
    DE102020112765A1|2020-05-12|2021-11-18|Miba Gleitlager Austria Gmbh|Main rotor bearing of a nacelle for a wind turbine|
    DE102020116588A1|2020-06-24|2021-12-30|Schaeffler Technologies AG & Co. KG|Angular contact sliding bearing|
    法律状态:
    2016-01-15| PC| Change of the owner|Owner name: MIBA GLEITLAGER AUSTRIA GMBH, AT Effective date: 20151116 |
    2021-09-15| MM01| Lapse because of not paying annual fees|Effective date: 20210130 |
    优先权:
    申请号 | 申请日 | 专利标题
    ATA50067/2013A|AT513516B1|2013-01-30|2013-01-30|Wind Turbine Gearbox|ATA50067/2013A| AT513516B1|2013-01-30|2013-01-30|Wind Turbine Gearbox|
    EP14711908.5A| EP2951467B1|2013-01-30|2014-01-27|Wind power plant gear mechanism|
    US14/762,541| US10294926B2|2013-01-30|2014-01-27|Wind power plant gear mechanism|
    DK14711908.5T| DK2951467T3|2013-01-30|2014-01-27|WIND TURBINE GEAR MECHANISM|
    PCT/AT2014/050030| WO2014117197A1|2013-01-30|2014-01-27|Wind power plant gear mechanism|
    KR1020157023546A| KR102184103B1|2013-01-30|2014-01-27|Wind power plant gear mechanism|
    ES14711908.5T| ES2637511T3|2013-01-30|2014-01-27|Wind power installation gear|
    CN201480006115.XA| CN104956126B|2013-01-30|2014-01-27|wind power installation transmission mechanism|
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