• 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 planetary gear (1) for a wind turbine, comprising a sun gear (3), a ring gear (13), a planet carrier (9) with a plurality of bearing seats (12), a plurality Planetenradachsen (8), a plurality of radial plain bearings (23) designed as a bearing bush (24), in particular as a multi-layer sliding bearing, for supporting the Planetenradachsen (8) in the planet carrier (9), a plurality of planetary gears (5) which are each supported by the Planetenradachsen (8) in the planet carrier (9). The planet carrier (9) has in the region of the bearing seats (12) each have a parting plane (17), wherein a first half-shell (18) of the respective bearing seat (12) by the planet carrier (9) and a second half-shell (19) of the respective bearing seat (12) by a respective bearing cap (20) is formed and wherein the bearing bush (24) of the radial sliding bearing (23) through the bearing cap (20) in the bearing seat (12) is clamped.
    公开号:AT516029A4
    申请号:T50743/2014
    申请日:2014-10-16
    公开日:2016-02-15
    发明作者:
    申请人:Miba Gleitlager Gmbh；
    IPC主号:
    专利说明:

    The invention relates to a planetary gear, as well as a equipped with the planetary gear wind turbine.
    A generic planetary gear is known for example from WO2013 / 106878A1 the same applicant. Here, between a planetary axis and the planet carrier at least one sliding bearing is arranged, wherein the planetary gear is rotatably connected to the planetary axis.
    The present invention has for its object to provide an improved Plane¬tengetriebe, which can be easily assembled and / or maintained.
    This object of the invention is achieved by the planetary gear described in this document or the wind turbine equipped therewith.
    According to the invention, a planetary gear for a wind turbine is provided, which comprises the following components: a sun gear; a ring gear; a Planeten¬ carrier with a first bearing receiving portion and a second bearing receiving portion, in which bearing receiving portions each have a plurality Lagerungs¬ are formed; several planetary gear axes; a plurality of radial plain bearings for supporting the Planetenradachsen in the planet carrier, wherein each of Planetenrad¬achsen are each mounted in one of the bearing seats of the first and in one of the bearing seat of the second bearing receiving portion; a plurality of planet gears which are respectively supported by the Planetenradachsen in the planet carrier, where the planetary gears mesh with both the sun gear and with the ring gear. The planet carrier has in the region of the bearing seats one each
    Parting plane, wherein a first half-shell of one of the bearing seats is formed by the Pla¬netenträger and a second half-shell of the bearing seats by a respective bearing cover.
    An advantage of this design is that when assembling the planetary gear, the planetary gear including the planetary gear can be easily inserted into the space provided for this purpose bearing of the planet carrier and subsequently be fastened by the bearing cap. Thereby, the Planetenwellenradachse can be taken out in the radial direction of the planet carrier, which leads to easier handling especially in large planetary gears, as for manipulating the Planetenradachse a lifting tool, such as a crane can be used. These advantages are also present in the maintenance of Plane¬tengetriebes, as well as the disassembly of the transmission for maintenance purposes is simplified.
    Further, it may be desirable for one of the bearing caps to be configured to extend beyond one of the bearing seats of the first bearing receiving portion and the respective associated bearing seat of the second bearing receiving portion. The advantage here is that a Planetenradachse, bzw.ein planetary gear can be attached to the planet carrier with only one bearing cap. The bearing dowel can thus have a high stability. Furthermore, the bearing cap can thereby easily and quickly attached to the planet carrier, bezie¬hart be solved by this again. By using as few components as possible, the clarity in Zusammenbaubziehungsweise during maintenance of the planetary gear is also increased.
    Furthermore, it can be provided that one of the bearing caps has a recess through which one of the planet gears at least partially protrudes.
    The advantage here is that the bearing cap can be designed so that it covers the interior of the planet carrier, with only one standing with the Hohl¬rad engaged portion of the planet gear from the Planetenenträgerbeziehungsweise the bearing cap protrudes. As a result, it can be achieved that the planet carrier forms a compact unit with the bearing cap, which can absorb the occurring bearing forces well.
    In addition, it may be provided that one of the radial sliding bearings is designed as a bearing bush, in particular as a multi-layer sliding bearing. The advantage here is that multi-layer bearings can have a structure in order to achieve a good Lage¬rung the planetary gear can.
    In a further development it can be provided that the bearing bush is firmly received in one of the bearing seats and an inner circumferential surface of the bearing bush is formed for receiving a relative movement between the bearing bush and one of the Planeten¬radachsen. The advantage here is that thereby the Lagerbüchsefest is included in the planet carrier. The relative movement between Plane¬tenradachse and planet carrier is transmitted to the inner circumferential surface of the bearing bush. Thus, it can be achieved that the forces transmitted by the planetary gear act as far as possible on a certain circumferential area of the bearing bush.
    Alternatively, it may be provided that one of the radial sliding bearing is formed as a split sliding bearing half shell. The advantage here is that the maintenance or assembly of the Planetengeriebesgut can be performed in a divided Gleitlagerhalbschale. In addition, for example, different materials can be used for the two plain bearing half shells, which makes it possible to use materials with particularly good sliding or strength properties to cover local stress peaks.
    According to a development, it is possible for one of the planetary gear axles to be formed in one piece with one of the planetary gears. This makes it possible spielsweise for series production to achieve the smallest possible number of Einzelbau¬ parts in the planetary gear. Furthermore, this can improve the quality of the transmission, since the concentricity of the planetary gear can be improved relative to the bearing points on the planetary gear axle.
    Furthermore, it may be expedient that one of the bearing caps is connected by a plurality of Ver¬ binding elements with the planet carrier. The advantage here is that the forces occurring on the bearing cap can thus be introduced evenly into the Planeten¬ carrier, whereby it comes as possible to no deformation due to the stress in the bearing cap. Such connection elements can be, for example, screws for producing a screw connection.
    In addition, it can be provided that Axialgleitlager between the Stirnflä¬chen one of the planet gears and the planet carrier are arranged. Of advantage in this case is that thus introduced in a planetary gear axial forces can be transmitted to the planet carrier and recorded by this.
    For a better understanding of the invention, this will be explained in more detail with reference to the following figures.
    In each case, in a highly simplified, schematic representation:
    Fig. 1 shows a planetary gear in a sectional view according to a cross section along a center line;
    Fig. 2 shows a further embodiment of a planetary gear with a partial section;
    Fig. 3 is a planetary gear which is cut as a half-section along the section line III -III in Fig. 2.
    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 designations, wherein the disclosures contained in the entire description apply mutatis mutandis to the same parts with the same reference numerals. same component names can be transferred. Also, the location information chosen in the description, such as up, down, laterally, etc. related to the directly described and illustrated figure and these conditions are to be transferred in a change in position mutatis mutandis to the new situation.
    1 shows a planetary gear 1 in a sectional view along a cross-section along a center line 2. The view according to FIG. 1 is used in general
    Explanation of the structure of the planetary gear and the representation of the parts installed in a planetary gearbox.
    As is known, wind turbines comprise a tower at the upper end of which a nacelle is arranged, in which the rotor is mounted with the rotor blades. This rotor is via the planetary gear 1 with a generator, which is also located in the nacelle, operatively connected, via the planetary gear 1 low speed of the rotor is translated into a higher speed of the generator rotor. Since such versions of wind turbines belong to the state of the art, reference should be made at this point to the relevant literature.
    The planetary gear 1 has a sun gear 3 which is motion-coupled to a shaft 4 leading to the generator rotor. The sun gear 3 is surrounded by a plurality of planetary gears 5, for example two, preferably three or four. Both the sun gear 3 and the planetary gears 5 have external spurs 6, 7 in meshing engagement with each other, these spur gears 6, 7 in FIG are shown schematically.
    The planetary gears 5 are mounted by means of a planetary gear 8 in the planet carrier 9, wherein in the planet carrier 9, a first bearing receiving portion 10 and a second bearing receiving portion 11 are provided, in each of which Lagersit¬ze 12 are formed for receiving the Planetenradachse 8.
    The planetary gears 5 surrounding a ring gear 13 is arranged, which has a In¬nenverzahnung 14, which is in meshing engagement with the spur gear 7 of the planet gears 5. The ring gear 13 is motion coupled to a rotor shaft 15 of the rotor of the wind turbine. The spur gears 6, 7 and the internal gear 14 may be designed as a straight toothing, as helical gearing or as a double helical gearing.
    Since such planetary gears 1 are also already known in principle from the prior art, for example from the above-cited prior art document, further discussion at this point is unnecessary.
    It should be noted that, hereinafter, with respect to the planetary gear 5, the singular is used. It goes without saying, however, that in the preferred embodiment, all planet gears 5 are designed according to the invention.
    FIGS. 2 and 3 show a further embodiment of the planetary gear 1, which may be independent of itself, wherein the same reference numerals or component designations are used again for identical parts as in the preceding FIG. To avoid unnecessary repetition, reference is made to the detailed description in the preceding Fig. 1.
    Fig. 2 shows a further embodiment of the planetary gear 1 in a Sei¬tenansicht similar to Fig. 1, wherein the planet carrier 9 is partially cutaway shown to bezieziehungsweise the structure of the planet carrier 9 to represent the storage of the planetary gear 8 on the planet carrier.
    Fig. 3 shows the planetary gear 1 in a front view, wherein the left half of the planetary gear 1 is shown uncut. The right half of the planetary gear 1 is shown in a section along the section line III-III of FIG.
    The further construction of the planetary gear 1 will be described with reference to a Zusammenschauaus Figures 2 and 3.
    As can be seen from Fig. 2 it can be provided that the Planetenradachse 8 coupled to the planetary gear 5 and is stored bilaterally in the planet carrier 9. The connection between planetary gear shaft 8 and planetary gear 5 can be realized, for example, by a press fit, by welding, and the like.
    Alternatively, it can be provided that the planetary gear 5 and the Planetenwellenradachse 8 are integrally formed and, for example, from a casting are, which has been reworked in the outer contour, or in which the teeth were formed by mechanical machining.
    2, it is provided that the Pla¬netenträger 9 in the region of the center line 16 of the Planetenradachse 8 has a Trenn¬ebene 17, through which both the bearing seat 12 of the first bearing receiving portion 10 and the bearing seat 12 of the second Lageraufnahmeabschnitt 11 is divided centrally. A first half-shell 18 of the bearing seat 12 is formed by the planetary carrier 9 and a second half-shell 19 of the bearing seat 12 by a bearing cap 20. The bearing cap 20 is ausgebil¬det such that it forms the bearing seats 12 together with the planet carrier 9. The bearing cap 20 is preferably connected to the planet carrier 9 by means of a connecting element 21, such as a screw connection.
    Furthermore, it can be provided that the bearing cap 20 has a recess 22bzw. has a breakthrough. As can be seen particularly well in Fig. 2, the recess 22 is provided to the Stinverzahnung 7 of the planetary gear 5 with the internal teeth 14 of the ring gear 13 can bring into engagement.
    In a further, not shown, embodiment variant can also be provided that the bearing seat 12 of the first bearing receiving portion 10 and the bearing seat 12 of the second bearing receiving portion 11 each have their own bearing cap 20.
    Furthermore, it can be seen from FIGS. 2 and 3 that a radial sliding bearing 23 can be provided, which is introduced into the bearing seat 12. The radial sliding bearing 23 can in this case be designed in particular as a bearing bush 24. Hereby, it can be provided that the bearing bush 24 is received in the bearing seat 12 by means of clamping, wherein the clamping is produced by the bearing cap 20, which forms the bearing seat 12 together with the planetary carrier 9. Furthermore, it can be provided that the bearing bush 24 relative to Bearing seat 12stillsteht and that the Planetenradachse 8 rotates relative to the bearing bush 24, wherein an inner circumferential surface 26 of the bearing bush 24 is formed as a sliding surface and can accommodate the relative movement between the bearing bush 24 and Planetenradachse 8.
    It can be provided that the bearing bushes 24 are produced in a centrifugal casting process, so that its uniform and smooth inner circumferential surface 26 have.
    Alternatively, it can also be provided that the bearing bushes 24 are designed as rolled bushings and have a butt joint 25. In this case, the bearing bush 24 is preferably positioned in the bearing seat 12 in such a way that the butt joint 25 does not lie in an area with high force acting on the bearing bushing 24. Particularly in the case of a design in which the bearing bush 24 is firmly seated in the bearing seat 12, this will only be locally effective a radial force loaded by the Planetenrad¬achse 8, whereby in the region of the butt joint 25 no or only small La¬gerkräfte be added.
    Furthermore, it can be provided that in the planet carrier 9 or in La¬gerdeckel 20 a recess is formed, in which the Radialgleitlager 23 can be inserted so that it is not axially against the bearing seat 12 slidably received in this.
    In addition, it can be provided that in the planet carrier 9, a cover seat 27ausgebildet, which corresponds to the bearing cap 20 so that the La¬gerdeckel 20 is centered on the planet carrier 9 and thus the bearing seat 12 has a smoothest possible inner surface for receiving the radial sliding bearing 23.
    Alternatively, it is also conceivable that dowel pins are provided, which provide for a precise positioning of the bearing cap 20 relative to the planet carrier 9.
    In another variant can also be provided that the Radialgleitlager23 is formed as a split plain bearing half shell 28, wherein each two of the Gleitlagerhalbschalen 28 together form the radial sliding bearing 23. Hereby it can be provided that the two plain bearing half shells 28, which form the radial plain bearing 23, have two different material compositions. Furthermore, it is also conceivable that the radial sliding bearing 23 is formed by several segments. In an embodiment of the radial sliding bearing 23 by
    Plain bearing half-shells 28 or by a plurality of segments can be provided so that the individual plain bearing half-shells 28 are positioned so that an orifice joint 25 in which two plain bearing shells 28 contact each other, also arranged in a region of low load, or is aligned. In other words, the dividing plane of the plain bearing half-shells 28 does not have to coincide with the parting plane 17.
    The radial sliding bearings 23 are preferably designed as multi-layer sliding bearings. A multilayer plain bearing comprises at least one backing layer and at least one slip layer applied to the backing layer. The sliding layer forms a running surface for the planet carrier 9 or the planet wheel axle 8.
    In addition to this two-layered embodiment of the multilayer plain bearing, there is also the possibility that intermediate layers are arranged between the sliding layer and the supporting layer, for example a bearing metal layer and / or at least one bonding layer and / or one diffusion barrier layer.
    Examples of bearing metal layers are: aluminum-based bearing metals, copper-based bearing metals, tin-based bearing metals, etc.
    It is also possible to use bearing metals other than the bearing metals based on nickel, silver, iron or chromium alloys.
    2, it can be provided that between the planetary gear 5 and the first bearing receiving portion 10, as well as between the planetary gear 5 and the second bearing receiving portion 11, a respective Axialgleit¬ 29 is arranged. The Axialgleitlager 29 has the purpose that a Stirnflä¬che 30 of the planetary gear 5 does not start on the planet carrier 9 and the bearing cap 20.
    As can further be seen, it can be provided that the axial sliding bearing 29 are accommodated in a corresponding receptacle 31 on the bearing cover 20 or on the planet carrier 9. The Axialgleitlager 29 may in this case also be formed in the form of segments, so that they are attached, for example, only on the bearing cap 20 or only on the planet carrier 9. It can be provided that the Axialgleitlager 29 is so connected to the bearing cap 20 or the Planetenträger9 that it is supported by these and a relative movement zwi¬schen Axialgleitlager 29 and planet gear 5 takes place.
    Furthermore, it can be provided that, as indicated in Fig. 3, the ring gear 13 has a Hohlradsegment 32 which is removable. As a result, a planetary gearwheel 5 together with the planetary gearwheel axis 8 can be removed from the planet carrier 9 without having to disassemble the entire planetary gearbox 1. The ring gear segment 32, which likewise has the internal toothing 14, can be coupled by a screw connection to the remainder of the ring gear 13. The ring gear segment 32 may be of a small size so that a planetary gear 5 together with the planetary gear shaft 8 will pass through the resulting opening. In an alternative variant, it is also conceivable that the Hohl¬radsegment 32 forms a half-shell of the ring gear 13.
    The exemplary embodiments show possible design variants of the planetary drive 1, wherein it should be noted at this point that the invention is not limited to the specific embodiments of the same, but also various combinations of the individual embodiments are possible with each other and this possibility of variation due to Teaching technical acting by objective invention in the skill of those working in this technical field is the expert.
    Furthermore, individual features or combinations of features from the different embodiments shown and described can also represent solutions that are inventive, inventive or inventive.
    The problem underlying the independent inventive solutions can be taken from the description. All statements on ranges of values in the description given herein are to be understood as including any and all subsections thereof, for example, the indication 1 to 10 should be understood as encompassing all subranges, starting from the lower bound 1 and the upper bound 10, i. all subregions begin with a lower limit of 1 or greater and end at an upper limit of 10 or less, e.g. 1 to 1.7, or 3.2 to 8.1, or 5.5 to 10.
    Above all, the individual embodiments shown in FIGS. 1, 2, 3 can form the subject of independent solutions according to the invention. The related objects and solutions according to the invention can be found in the detailed descriptions of these figures.
    For the sake of order, it should finally be pointed out that in order to better understand the structure of the planetary gear 1, this or its constituent parts have been shown partly unevenly and / or enlarged and / or reduced in size.
    LIST OF REFERENCES 1 Planetary gear 29 Axial sliding bearing 2 Center line Planetary gear 30 End face 3 Sun gear 31 Receiving axial sliding bearing 4 Shaft 32 Ring gear segment 5 Planetary gear 6 Spur gear Sun gear 7 Spur gear Planetary gear 8 Planetary gear 9 Planet carrier 10 First bearing receiving section 11 Second bearing receiving section 12 Bearing seat 13 Ring gear 14 Internal gear 15 Rotor shaft 16 Centerline planetary gear axis 17 Parting plane 18 first half shell 19 second half shell 20 Bearing cover 21 connecting element 22 recess 23 Radial sliding bearing 24 bearing bush 25 butt joint 26 inner lateral surface 27 cover seat 28 plain bearing half shell
    权利要求:
    Claims (10)
    [1]
    A planetary gear (1) for a wind turbine, comprising: a sun gear (3); a ring gear (13); a planetary carrier (9) having a first bearing receiving portion (10) and a second bearing receiving portion (11), in which bearing receiving portions (10, 11) are each formed a plurality of bearing seats (12); a plurality of planetary gear shafts (8); a plurality of radial plain bearings (23) for supporting the Planetenradachsen (8) in the Plane¬tenträger (9), each of the Planetenradachsen (8) in each of the Lagersit¬ze (12) of the first bearing receiving portion (10) and in one of the bearing seats (12 a plurality of planetary gears (5) each supported by the planetary gear axles (8) in the planetary carrier (9), the planetary gears (5) being connected to both the sun gear (3) and the ring gear (13) of the second bearing receiving portion (11); ), characterized in that the planet carrier (9) in the region of the bearing seats (12) each having a parting plane (17), wherein a first half-shell (18) of the bearing seats (12) by the planet carrier (9) and a second Half shell (19) of the bearing seats (12) by a respective bearing cap (20) is formed.
    [2]
    2. Planetary gear according to claim 1, characterized in that ei¬ner the bearing cap (20) is designed such that it extends over one of Lager¬sitze (12) of the first bearing receiving portion (10) and the respective bearing seat (12) of the second Bearing receiving portion (11) extends.
    [3]
    3. planetary gear according to claim 1 or 2, characterized in that one of the bearing cap (20) has a recess (22) through whicheineines the planet wheels (5) at least partially protrudes.
    [4]
    4. Planetary gear according to one of the preceding claims, characterized in that one of the radial sliding bearing (23) is designed as a bearing bush (24), in particular as a multi-layer sliding bearing.
    [5]
    5. Planetary gear according to claim 4, characterized in that the bearing bush (24) is firmly received in one of the bearing seats (12) and an In¬nenmantelfläche (26) of the bearing bush (24) for receiving a relative movement between the bearing bush (24) and one of Planetenradachsen (8) is formed.
    [6]
    6. Planetary gear according to one of claims 1 to 4, characterized gekenn¬zeichnet that one of the radial sliding bearing (23) is designed as a split plain bearing half-shell (28).
    [7]
    7. Planetary gear according to one of the preceding claims, characterized in that one of the Planetenradachsen (8) is formed integrally with one of the Pla¬netenräder (5).
    [8]
    8. Planetary gear according to one of the preceding claims, characterized in that one of the bearing cap (20) is connected by a plurality of Verbindungsele¬mente (21) with the planet carrier (9).
    [9]
    9. Planetary gear according to one of the preceding claims, characterized in that in each case a Axialgleitlager (29) between the end faces (30) of the planetary gears (5) and the planet carrier (9) are arranged.
    [10]
    10. A wind turbine with a rotor and a generator, wherein between the rotor and the generator, a planetary gear (1) is arranged, which is inWirkverbindung with the rotor and the generator, characterized gekennzeichnet that the planetary gear (1) according to one of claims 1 to 9 is formed.
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    同族专利:
    公开号 | 公开日
    DK3207288T3|2019-06-11|
    EP3207288A1|2017-08-23|
    KR20170070182A|2017-06-21|
    CN106715972B|2019-06-07|
    CN106715972A|2017-05-24|
    US10288164B2|2019-05-14|
    US20170219088A1|2017-08-03|
    ES2730078T3|2019-11-08|
    AT516029B1|2016-02-15|
    WO2016058018A1|2016-04-21|
    EP3207288B1|2019-03-13|
    引用文献:
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    法律状态:
    2016-07-15| PC| Change of the owner|Owner name: MIBA GLEITLAGER AUSTRIA GMBH, AT Effective date: 20160601 |
    优先权:
    申请号 | 申请日 | 专利标题
    ATA50743/2014A|AT516029B1|2014-10-16|2014-10-16|Planetary gear for a wind turbine|ATA50743/2014A| AT516029B1|2014-10-16|2014-10-16|Planetary gear for a wind turbine|
    DK15801978.6T| DK3207288T3|2014-10-16|2015-10-14|Planet gear to a wind turbine|
    US15/518,552| US10288164B2|2014-10-16|2015-10-14|Planetary gear train for a wind turbine|
    PCT/AT2015/050255| WO2016058018A1|2014-10-16|2015-10-14|Planetary gear train for a wind turbine|
    EP15801978.6A| EP3207288B1|2014-10-16|2015-10-14|Planetary gear train for a wind turbine|
    ES15801978T| ES2730078T3|2014-10-16|2015-10-14|Planetary gear for a wind turbine|
    CN201580050993.6A| CN106715972B|2014-10-16|2015-10-14|Planetary gear transmission mechanism for wind power plant|
    KR1020177013101A| KR20170070182A|2014-10-16|2015-10-14|Planetary gear train for a wind turbine|
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