• 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 gearbox (1) for a wind power plant, comprising a sun gear (3), a ring gear (17), a planet carrier (9) with a first bolt receiving element (10), which has at least one first bolt seat (12), at least one Planetenradbolzen (8) and at least one planetary gear (5). The bearing assembly (19) has a first Planetenradaufnahmebuchse (20) and a second Planetenradaufnahmebuchse (21), which Planetenradauf- receiving bushes (20, 21) are rotationally rigidly coupled to the planetary gear (5) and between which Planetenradaufnahmebuchsen (20, 21) an axial bearing gap (25) is formed. The bearing arrangement (19) has at least one bearing sleeve (28), which is received in a torsionally rigid manner on the planet wheel pin (8) and on which an axial positioning flange (29) is formed, which is received in the axial bearing gap (25) between the planetary gear receiving bushes (20) and thereby an axial positional fixation, in particular an axial bearing, of the planetary wheel (5) on the planetary gear pin (8) is realized.
    公开号:AT517719A4
    申请号:T50789/2015
    申请日:2015-09-15
    公开日:2017-04-15
    发明作者:
    申请人:Miba Gleitlager Austria Gmbh；
    IPC主号:
    专利说明:

    The invention relates to a planetary gear, as well as equipped with the planetary gear wind turbine.
    A generic planetary gear is known for example from WO2013 / 106878A1 the same applicant. In this document, a sliding bearing is arranged between a planetary axis and the planet carrier, wherein the planetary gear is rotatably connected to the planetary axis. For axial mounting of the planet gear two thrust washers are provided, which are arranged on either side of the planet gear between planet and planet carrier.
    The present invention has for its object to provide a planetary gear with an improved storage of the planetary gear.
    This object of the invention is achieved by the planetary gear according to claim 1.
    According to the invention, a planetary gear is designed for a wind turbine. The planetary gear comprises a sun gear, a ring gear, a planetary carrier with a first bolt receiving element, which has at least a first bolt seat and, at least one planet gear bolt, which is received drehrehstarr in the first bolt seat; at least one planetary gear, which is rotatably received on the Planetenradbolzen means of a bearing assembly relative to the Planetenradbolzen, wherein the planetary gear is engaged with both the sun gear and the ring gear. The bearing assembly comprises a first Planetenradaufnahmebuchse and a second Planetenradaufnahmebuchse, which Planetenradaufnahmebuchsen are rotationally rigidly coupled to the planet and between which Planetenradaufnahmekuchsen an axial bearing gap is formed. The bearing assembly has at least one bearing sleeve, which is received drehrehfest on Planetenradbolzen and on which a Axialpositionierflansch is formed, which is received in Axiallagerspalt between the Planetenradaufnahmebuchsen and thereby axial positional fixation, in particular a thrust bearing, the planetary gear is realized on Planetenradbolzen.
    The inventive construction of the planetary gear has the advantage that the axial bearing of the planetary gear is arranged to save space in the planetary gear and that such a planetary gear, in particular planetary gear, can be easily maintained. Moreover, it is also conceivable that in an existing planetary gear originally intended rolling bearing can be replaced by a slide bearing constructed in this way.
    Furthermore, it may be appropriate that the bearing assembly comprises a first radial plain bearing bush which is rotationally accommodated in the first Planetenradaufnahmebuchse and a second Radialgleitlagerbuchse which is received rotationally fixed in the second Planetenradaufnahmebuchse, wherein the first and the second Radialgleitlagerbuchse at a contact surface with the bearing sleeve Have sliding surface for relative movement. Such a plain bearing bush can easily be replaced in case of wear or such plain bearing bushes can be made so that they are adapted to the requirements of the respective planetary gear.
    Furthermore, it can be provided that the bearing arrangement comprises a first axial sliding bearing disc, which is arranged between the first Planetenradaufnahmekuchse and Axialpositionierflansch the bearing sleeve and that the bearing assembly comprises a second Axialgleitlagerscheibe, which is arranged between the second Planetenradaufnahmekuchse and Axialpositionierflansch the bearing sleeve. The arrangement of axial plain bearing disks, the ease of movement of the planetary gear can be increased or can be achieved that in the bearing assembly and axial forces, for example by a helical toothing in the planetary gear, can be transmitted.
    In addition, it can be provided that the first Axialgleitlagerscheibe is fastened by means of a fastening means to the first Planetenradaufnahmebuchse and that the second Axialgleitlagerscheibe is fastened by means of a fastening means on the second Planetenradaufnahmekuchse. The advantage here is that the Axialgleitlagerscheiben can be recorded fixed in position within the bearing assembly and thus the sliding surfaces of the Axialgleitlagerscheiben can be accurately predetermined.
    Furthermore, it can be provided that the planet carrier has a second bolt receiving element, on which at least a second bolt seat is formed, wherein the planetary gear is arranged on Planetenradbolzen between the first bolt seat and the second bolt seat. The advantage here is that thereby a two-sided storage of the planetary gear bolt can be achieved. This leads to an increased rigidity of the overall system and thus to a reduction of the vibrations during operation of the planetary gear.
    Also advantageous is an embodiment, according to which it can be provided that the bearing sleeve comprises a first bearing sleeve part and a second bearing sleeve part, wherein on one of the two Lagerlaufhülsenteile frontally the Axialpositionierflansch is formed and the two Lagerlaufhülsenteile are positioned relative to each other, that the Axialpositionierflansch inside between the two bearing sleeve parts is arranged. The advantage here is that the bearing sleeve by the split design can be easily and inexpensively manufactured and beyond the installation of the bearing sleeve is facilitated.
    According to a development, it is possible that at least one of the Planetenradaufnahmebuchsen has a frontally arranged gradation, which forms the Axiallagerspalt, the two Planetenradaufnahmebuchsen touching each other frontally. The advantage here is that thereby the axial extent of the thrust bearing gap can be precisely defined. Thus, an axial bearing clearance can be determined.
    Furthermore, it may be expedient that at least one lubricant supply line is formed in the planetary pin, which is guided in the region of the bearing sleeves of the Planetenradbolzen and that in Planetenradbolzen further at least one lubricant discharge is formed, which opens in the region of the Axialpositionierflansches in the Planetenradbolzen. The advantage here is that the axial bearing and the radial bearing can be specifically lubricated by means of external lubricant supply by the lubricant supply and the lubricant discharge.
    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 is a perspective view of an embodiment planet carrier for a planetary gear;
    FIG. 2 is a sectional view of the planet carrier according to the section line II-II of FIG. 3; FIG.
    3 shows a sectional view of the planet carrier according to the section line III-III according to FIG. 2;
    4 is a sectional view of the planet carrier according to the section line IV-IV of Fig. 3.
    5 is a sectional view of a planet carrier with cantilevered planet pins.
    Fig. 6 is a sectional view of a planet carrier with integrated planet pins.
    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, 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 these position information in a change in position mutatis mutandis to transfer to the new location.
    Fig. 1 shows a perspective view of the interior of a planetary gear 1 for a wind turbine. Fig. 2 shows a half section of the planetary gear 1, wherein for reasons of clarity, only one above a central axis 2 lying portion of the planetary gear 1 is shown.
    The following description of the structure of the planetary gear 1 is based on a synopsis of Figures 1 and 2.
    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 the planetary gear 1 with a generator, which is also located in the nacelle, operatively connected, via the planetary gear 1, the low speed of the rotor is translated into a higher rotational speed of the generator rotor. Since such embodiments of wind turbines belong to the prior art, reference should be made at this point to the relevant literature.
    The planetary gear 1 has a sun gear 3, which is coupled to a shaft 4, which leads to the generator rotor. The sun gear 3 is surrounded by a plurality of planet wheels 5, for example two, preferably three or four. Both the sun gear 3 and the planet gears 5 have external serrations 6, 7, which are in meshing engagement with each other, these spur gears 6, 7 are shown schematically in Fig. 2.
    The planetary gears 5 are mounted by means of planetary pin 8 in a planet carrier 9, wherein in the planet carrier 9, a first pin receiving element 10 and a second pin receiving element 11 are provided. In the bolt receiving elements 10, 11, a first pin seat 12 and a second pin seat 13 are formed in which the Planetenradbolzen 8 is received. The Planetenradbolzen 8 can be secured by additional security measures, such as fasteners in the planet carrier 9.
    The planet carrier 9, in particular the bolt receiving elements 10, 11 may be integrally formed from a cast workpiece.
    In an alternative variant, it is also conceivable that the second bolt receiving element 11 is fastened by means of a fastening means on the first bolt receiving element 10 and the two bolt receiving elements 10, 11 are thus dismantled. Furthermore, guide pins can be provided, by means of which the position of the second pin receiving element 11 is fixed relative to the first pin receiving element 10.
    As can be seen particularly well in FIG. 2, it can be provided that the first pin seat 12 is designed in the form of a blind hole and that the second pin seat 13 is designed in the form of a through hole. Thus, the Planetenradbolzen 8 can be inserted from the side of the second pin seat 13 in the two pin receiving elements 10, 11.
    Furthermore, it can be seen that the planetary gear 5 is received approximately in the middle between the two pin receiving elements 10, 11, wherein both between a first end face 14 of the planetary gear 5 and the first pin receiving element 10 and between a second end face 15 of the planetary gear 5 and the second pin receiving element 11 an axial clearance 16 is formed, so that the planetary gear 5 can run freely in the planet carrier 9.
    On the outer side of the planet gears 5, a Flohlrad 17 is arranged, which has an internal toothing 18 which is in meshing engagement with the spur gear teeth 7 of the planet gears 5. The Flohlrad 17 is coupled for movement with a rotor shaft of the rotor of the wind turbine.
    The serrations 6, 7 and the internal teeth 18 may be designed for example as a straight toothing, as a helical toothing or as a double helical toothing.
    Since such planetary gear 1 in principle also already known from the prior art, for example, from the above cited
    Document on the state of the art, there is no need for further discussion at this point.
    It should be noted that in the following with respect to the planetary gear 5, the singular is used. It goes without saying, however, that a plurality of planet wheels 5 can be designed according to the invention.
    The planetary gear 5 is mounted by means of a bearing assembly 19 on Planetenradbolzen 8 and thereby rotatable relative to the Planetenradbolzen 8. In addition, can be achieved by the bearing assembly 19, that the axial clearance 16 between the planetary gear 5 and the pin receiving elements 10, 11 is maintained upright in operation and thereby the planetary gear 5 is free to rotate.
    The bearing assembly 19 includes a first Planetenradaufnahmebuchse 20 and a second Planetenradaufnahmebuchse 21, which are received drehrehstarr in the planetary gear 5. This can be achieved, for example, in that the planetary gear receiving bushes 20, 21 are inserted into an inner cylindrical surface 22 of the planetary gear 5. The inner cylindrical surface 22 of the planetary gear 5 may also have gradations, which serve as a stop. In order to accommodate the Planetenradaufnahmebuchsen 20, 21 in the planetary gear 5 drehrehstarr, for example, be provided that they are received by a press fit in the planetary gear 5. Additionally or alternatively, it may be provided that the Planetenradaufnahmebuchsen 20, 21 are secured in the planetary gear 5 by means of a fastening means, such as a worm screw. In a further variant it can be provided that the Planetenradaufnahmebuchsen 20, 21 are secured in the planetary gear 5 by means of a material connection, such as an adhesive bond or a welded joint.
    Furthermore, it can be provided that at least one of the two Planetenradaufnahmebuchsen 20, 21 on a front side 23 has a gradation 24 through which an axial bearing gap 25 is formed. The Planetenradaufnahmebuchsen 20, 21 are preferably formed in the form of a hollow cylinder, wherein the gradation 24 in the inner cylindrical surface of the Planetenradaufnahmebuchse 20, 21 is formed. In particular, it can be provided that end faces 23 of the Planetenradaufnahmebuchsen 20, 21 abut each other in the assembled state.
    In another embodiment, not shown, it can be provided that centrally of the cylindrical surface 22 of the planetary gear 5, a projection is arranged, on which the Planetenradaufnahmebuchsen 20, 21 abut, whereby the Axiallagerspalt 25 is formed.
    In yet another embodiment, it can be provided that one of the two Planetenradaufnahmebuchsen 20, 21 is integrally connected to the planetary gear 5, or that one of the two Planetenradaufnahmebuchsen 20, 21 is integrally formed with the planetary gear 5.
    Furthermore, it can be provided that on the inner lateral surface of the first Planetenradaufnahmebuchse 20, a first Radialgleitlagerbuchse 26 is received and that on the inner lateral surface of the second Planetenradaufnahmebuchse 21, a second Radialgleitlagerbuchse 27 is arranged. The two radial plain bearing bushes 26, 27 are preferably received in the Planetenradaufnahmebuchsen 20, 21 by means of a press connection. As a result, the radial plain bearing bushes 26, 27 are preferably received rotationally rigidly in the Planetenradaufnahmebuchsen 20, 21. In particular, it can be provided that in the Planetenradaufnahmebuchsen 20, 21, a lug is formed, in which the radial plain bearing bushes 26, 27 are added. Thereby, the axial position of the radial plain bearing bushes 26, 27 are determined.
    Furthermore, a bearing sleeve 28 is provided, which is preferably fastened by means of a press connection to the Planetenradbolzen 8. The bearing sleeve 28 may also be additionally secured in the seat on the Planetenradbolzen 8. The bearing sleeve 28 has an Axialpositionierflansch 29, which is received in the thrust bearing 25. By Axialpositionierflansch 29 and the thrust bearing 25, the planetary gear 5 can be secured in its axial position.
    As can be seen from FIG. 2, it can be provided that the first and the second radial plain bearing bushes 26, 27 have a sliding surface 30 by means of which they rest on the bearing sleeve 28 and whereby the plain bearing of the planetary gear 5 is formed.
    In another embodiment, not shown, it may also be provided that the sliding surface 30 is not arranged on the inner cylindrical surface of the radial plain bearing bushes 26, 27, but that it is arranged on the outer cylindrical surface of the radial plain bearing bushes 26, 27. In such a variant embodiment, the radial plain bearing bush 26, 27 is rotationally rigidly pressed against the bearing sleeve 28 and finds the relative movement between the radial plain bearing bushing 26, 27 and the Planetenradaufnahmebuchsen 20, 21 instead.
    Furthermore, it can be provided that between the Axialpositionierflansch 29 and the first Planetenradaufnahmebuchse 20 a first Axialgleitlagerscheibe 31 is arranged and that analogously thereto between Axialpositionierflansch 29 and the second Planetenradaufnahmebuchse 21, a second Axialgleitlagerscheibe 32 is arranged.
    In a first variant it can be provided that the Axialgleitlagerscheiben 31,32 are arranged by means of a fastening means 33 on the first and or second Planetenradaufnahmebuchse 20, 21. The relative movement thus takes place between Axialgleitlagerscheiben 31,32 and the Axialpositionierflansch 29. Such a fastening means may be, for example, an Allen or a countersunk screw.
    Alternatively, it can be provided that, instead of the fastening means 33, an adhesive connection is used for fastening the axial sliding bearing disks 31, 32 to the planetary gear receiving bushing 20, 21.
    In another embodiment, not shown, it can be provided that by means of a fastening means 33 or an adhesive joint, the Axialgleitlagerscheiben 31,32 are attached to the Axialpositionierflansch 29 and that a relative movement between the Axialgleitlagerscheiben 31,32 and the Pla-netenradaufnahmebuchsen 20, 21 takes place.
    In yet another embodiment, it may be provided that the Axialgleitlagerscheiben 31,32 is fixed either by the outboard or by the inner peripheral surface radially within the Axiallagerspaltes 25 and the Axialgleitlagerscheibe 31, 32 thus loose in Axiallagerspalt 25 can be inserted.
    As shown in FIG. 2, it can be provided that the bearing sleeve 28 is formed by a first bearing sleeve part 34 and a second bearing sleeve part 35. Such an embodiment of the bearing sleeve 28 has the advantage that the individual bearing sleeve parts 34, 35 are easy to manufacture and can be installed separately from each other. In such a split configuration, the axial positioning flange 29 is formed on one of the bearing sleeve parts 34, 35. The two bearing sleeve parts 34, 35 are positioned in the installed state to each other, that the Axialpositionierflansch 29 is arranged approximately in the middle of the two bearing sleeve parts 34, 35.
    In a further embodiment, not shown, it can be provided that the bearing sleeve 28 has a similar shape as the bearing sleeve parts 34, 35 shown in Fig. 2 in the assembled state, but is integrally formed.
    Furthermore, it can be provided that in the Planetenradbolzen 8 a lubricant supply line 36 is formed, by means of which lubricant, such as oil, to the sliding surfaces 30 of the two plain bearing bushes 26, 27 can be supplied. In particular, it can be provided that the bearing sleeve 28 has at least one bore, which is congruent with the mouth opening in the peripheral region of the planetary gear 8 and thus the lubricant can be passed directly to the sliding surface 30. Furthermore, it can be provided that distributed over the circumference, a plurality of holes or mouths of the lubricant supply line 36 are provided so that the radial plain bearing bushes 26, 27 can be supplied at several points with a lubricant.
    In order to ensure that the holes in the bearing sleeve 28 are congruent with the mouths of the lubricant supply line 36 in the Planetenradbolzen 8, it can be provided that between bearing sleeve 28 and Planetenradbolzen 8 is formed a feather key or other positive connection to prevent rotation.
    Furthermore, a lubricant discharge 37 can be provided, by means of which the lubricant pressed into the axial bearing gap 25 can be removed from the axial bearing gap 25.
    Fig. 3 shows a sectional view of the planet carrier according to the section line MINI of Fig. 2, wherein again for the same parts the same reference numerals or component designations as in the preceding Figures 1 and 2 are used. In order to avoid unnecessary repetition, reference is made to the detailed description in the preceding Figures 1 and 2 or reference.
    Fig. 4 shows a sectional view of the planet carrier according to the section line IV-IV of FIG. 3, wherein in turn the same reference numerals or component names are used as in the previous figures 1 to 3 for the same parts. To avoid unnecessary repetition, reference is made to the detailed description in the preceding figures 1 to 3 or reference.
    As can be seen particularly well from a synopsis of Figs. 3 and 4, the lubricant discharge 37 is pulled in the region of the Axialpositionierflansches 29 in preferably a plurality of orifices to the outside. In particular, it may be provided that the bearing sleeve 28 in the region of the Axialpositionierflansches 29 has radial bores, which are congruent with the lubricant discharge 37 of the Planetenradbolzens and thus the lubricant can be removed from the Axiallagerspalt 25. The described arrangement of the lubricant supply line 36 and the lubricant discharge 37 can ensure that both the radial plain bearing bushes 26, 27 and the axial plain bearing disks 31, 32 are supplied with sufficient lubricant.
    2, the possible installation of such a planetary gear 5 formed in the planet carrier 9 will now be described.
    In a first method step, the first Planetenradaufnahmebuchse 20 is pressed into the planetary gear 5 and secured as needed. In a further method step, the first radial plain bearing bush 26 is now pressed into the first planetary gear receiving bushing 20. Alternatively, it is also conceivable that the first Radialgleitlagerbuchse 26 is pressed before the onset of the first Planetenradaufnahmebuchse 20 in the planetary gear 5 with the first Planetenradaufnahmekuchse 20.
    In a further method step, the first axial sliding bearing disk 31 is now inserted into the axial bearing gap 25. Now, the bearing sleeve 28 can be inserted into the first radial plain bearing bush 26 such that the Axialpositionierflansch 29 is received in the thrust bearing 25.
    In a further method step, the second radial plain bearing bushing 27 can be pressed into the second Planetenradaufnahmebuchse 21 and the second Axialgleitlagerscheibe 32 are positioned at this.
    In a further method step, the second Planetenradaufnahmekuchse 21 can now be pressed into the planetary gear 5 and, if necessary, be secured in this. As a result, the planetary gear 5 with the Planetenradaufnahmebuchsen 20, 21 of the bearing sleeve 28 and arranged between the individual parts Radialgleitlagerbuchsen 26, 27 and Axialgleitlagerscheiben 31,32 a unit.
    In a further method step, this unit can now be used in the planet carrier 9 and the Planetenradbolzen 8, starting from the side of the second pin seat 13 in the two pin seats 12, 13 are inserted and then secured as needed.
    FIG. 5 shows a further embodiment of the planetary gear 1, which is possibly independent of itself, wherein the same reference numerals or component designations are used again for the same parts as in the preceding FIGS. 1 to 4. In order to avoid unnecessary repetition, reference is made to the detailed description in the preceding figures 1 to 4 or reference.
    In the embodiment according to FIG. 5, only the first bolt receiving element 10 is provided for receiving the planetary gear bolt 8. In other words, the Planetenradbolzen 8 is stored flying in the first pin seat 12. Also in this embodiment, the Planetenradbolzen 8 is received torsionally rigid in the first pin seat 12.
    For attachment of the Planetenradbolzens 8 in the first bolt receiving element 10, one or more fasteners 38 may be provided. The fastening elements 38 may be formed, for example in the form of screws. Furthermore, it can be provided that the Planetenradbolzen 8 has a shoulder 39. In particular, it may be provided that the bearing sleeve parts 34, 35 are clamped between the shoulder 39 and the first pin receiving element 10. Such a clamping can be achieved by tightening the fasteners 38.
    FIG. 6 shows a further embodiment of the planetary gear 1, which is possibly independent of itself, wherein the same reference numerals or component designations are used again for the same parts as in the preceding FIGS. 1 to 5. In order to avoid unnecessary repetition, reference is made to the detailed description in the preceding figures 1 to 5 or reference.
    In the further embodiment of FIG. 6 it can be provided that the Planetenradbolzen 8 is formed integrally with the first pin receiving element 10 or one piece. In such an embodiment, the first pin seat 12 is realized by the cohesive material connection.
    In order to be able to fasten the bearing sleeve parts 34, 35 to the planet wheel bolt 8, an axial securing element 40 can be provided by means of which the bearing sleeve parts 34, 35 can be clamped. The Axialsicherungsele element 40 may be formed as shown in the form of a disc, which can be secured by means of a further fastening means 41, such as a screw on the Planetenradbolzen 8.
    In an alternative embodiment, not shown, it may also be provided that the axial securing element 40 is designed in the form of a shaft nut, which is screwed directly onto the planetary gear bolt 8.
    In yet another variant, not shown, it can also be provided that the axial securing element 40 is designed in the form of an axial securing ring, which is fastened directly to the planetary wheel pin 8. Of course, other forms of axial securing elements 40 can be used.
    Analogous to the exemplary embodiments according to FIGS. 1 to 4, a lubricant supply in the planetary gear pin 8 can also be formed in the exemplary embodiments according to FIGS. 5 and 6.
    Furthermore, individual features or combinations of features from the different exemplary embodiments shown and described can also represent independent, inventive or inventive solutions.
    The task underlying the independent inventive solutions can be taken from the description.
    Above all, the individual embodiments shown in FIGS. 1, 2, 3, 4, 5, 6 can form the subject of independent solutions according to the invention. The relevant 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 individual parts, these parts have been shown to be partly un-scaled and / or enlarged and / or reduced in size.
    REFERENCE SIGNS LIST 1 Planetary gear TI second radial plain bearing bush 2 center pinion planetary gear 28 bearing sleeve 3 sun gear 29 Axialpositionierflansch 4 shaft 30 sliding surface 5 planetary 31 first Axialgleitlagerscheibe 6 front teeth sun gear 32 second Axialgleitlagerscheibe 7 spur gear planetary 33 fasteners 8 Planetenradbolzen 34 first Lagerlaufhülsenteil 9 Planetenträger 35 second Lagerlaufhülsenteil 10 first Bolzenaufnahmeele- 36th Schmiermittelzuleitung ment 37 Schmiermittelableitung 11 second Bolzenaufnahmeele- 38 fastener ment 39 shoulder 12 first bolt seat 40 Axialsicherungselement 13 second bolt seat 41 further attachment means 14 first end planetary gear 15 second planetary gear 16 axial clearance 17 ring gear 18 internal teeth 19 Bearing assembly 20 first Planetenradaufnahmebuchse 21 second Planetenradaufnahmekuchse 22 cylindrical surface planetary gear 23 Front side 24 Gradation 25 Axial bearing gap 26 First radial sliding bearing bush
    权利要求:
    Claims (9)
    [1]
    claims
    A planetary gear (1) for a wind turbine, comprising: a sun gear (3); a ring gear (17); a planet carrier (9) having a first bolt receiving element (10), which has at least one first bolt seat (12); at least one Planetenradbolzen (8), which is received drehreharr in the first bolt seat (12); at least one planet gear (5), which is rotatably received on the planet wheel bolt (8) by means of a bearing arrangement (19) relative to the planet gear pin (8), wherein the planet gear (5) with both the sun gear (3) and with the ring gear (17) is engaged, characterized in that the bearing assembly (19) has a first Planetenradaufnahmebuchse (20) and a second Planetenradaufnahmebuchse (21), which Planetenradaufnahmebuchsen (20, 21) are rotationally rigidly coupled to the planetary gear (5) and between which Planetenradaufnahmebuchsen (20 , 21) an axial bearing gap (25) is formed, and that the bearing arrangement (19) has at least one bearing sleeve (28), which is held rotationally rigidly on the planet wheel pin (8) and on which an axial positioning flange (29) is formed, which is arranged in the axial bearing gap (25 ) is received between the Planetenradaufnahmebuchsen (20) and thereby an axial position fixation, in particular a thrust bearing, the planetary gear s (5) on Planetenradbolzen (8) is realized.
    [2]
    2. Planetary gear according to claim 1, characterized in that the bearing assembly (19) further comprises a first Radialgleitlagerbuchse (26) which is rotatably received in the first Planetenradaufnahmebuchse (20) and a second Radialgleitlagerbuchse (27) which in the second Planetenradaufnahmebuchse ( 21) is received rotationally fixed, wherein the first (26) and the second Radialgleitlagerbuchse (27) on a contact surface with the bearing sleeve (28) has a sliding surface (30) for relative movement.
    [3]
    3. planetary gear according to claim 1 or 2, characterized in that the bearing assembly (19) has a first Axialgleitlagerscheibe (31) which between the first Planetenradaufnahmebuchse (20) and Axialpositionierflansch (29) of the bearing sleeve (28) is arranged and that the bearing assembly (19) has a second Axialgleitlagerscheibe (32) which is disposed between the second Planetenradaufnahmekuchse (21) and Axialpositionierflansch (29) of the bearing sleeve (28).
    [4]
    4. Planetary gear according to claim 3, characterized in that the first Axialgleitlagerscheibe (31) by means of a fastening means (33) on the first Planetenradaufnahmebuchse (20) is fixed and that the second Axialgleitlagerscheibe (32) by means of a fastening means (33) on the second Planetenradaufnahmekuchse (21) is attached.
    [5]
    5. Planetary gear according to one of the preceding claims, characterized in that the planet carrier (9) has a second bolt receiving element (11) on which at least a second bolt seat (13) is formed, wherein the planet gear (5) on Planetenradbolzen (8) between first bolt seat (12) and second bolt seat (13) is arranged.
    [6]
    6. Planetary gear according to one of the preceding claims, characterized in that the bearing sleeve (28) comprises a first bearing sleeve part (34) and a second bearing sleeve part (35), wherein on one of the two bearing sleeve parts (34, 35) frontally the Axialpositionierflansch (29) is formed and the two Lagerlaufhülsenteile (34, 35) are positioned to each other so that the Axialpositionierflansch (29) is disposed internally between the two Lagerlaufhülsenteilen (34, 35).
    [7]
    7. Planetary gear according to one of the preceding claims, characterized in that at least one Planetenradaufnahmebuchsen (20, 21) has a frontally arranged gradation (24) which forms the Axiallagerspalt (25), wherein the two Planetenradaufnahmebuchsen (20, 21) each other frontally touch.
    [8]
    8. Planetary gear according to one of the preceding claims, characterized in that in Planetenradbolzen (8) at least one lubricant supply line (36) is formed, which in the region of the bearing sleeves (28) from the Planetenradbolzen (8) is guided and that in Planetenradbolzen (8) Furthermore, at least one lubricant discharge line (37) is formed which opens into the planet wheel pin (8) in the region of the axial positioning flange (29).
    [9]
    9. wind turbine with a planetary gear (1), characterized in that the planetary gear (1) is designed according to one of the preceding claims.
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    同族专利:
    公开号 | 公开日
    AT517719B1|2017-04-15|
    CN108026975A|2018-05-11|
    EP3350464B1|2019-11-27|
    WO2017046194A1|2017-03-23|
    ES2774507T3|2020-07-21|
    EP3350464A1|2018-07-25|
    US10451176B2|2019-10-22|
    CN108026975B|2019-06-21|
    DK3350464T3|2020-03-02|
    US20180299006A1|2018-10-18|
    KR20180054685A|2018-05-24|
    引用文献:
    公开号 | 申请日 | 公开日 | 申请人 | 专利标题
    GB2010415A|1977-11-25|1979-06-27|Gkn Group Services Ltd|Vehicle Bearing|
    WO2009141140A2|2008-05-20|2009-11-26|Urs Giger|Wind power plant, transmission for a wind power plant and flexpin|
    EP2383480A1|2010-04-30|2011-11-02|Winergy AG|Planetary gear for a wind power system|
    WO2013106878A1|2012-01-16|2013-07-25|Miba Gleitlager Gmbh|Wind turbine|
    EP2662598A1|2012-05-08|2013-11-13|ZF Wind Power Antwerpen NV|Planetary gear stage with plain bearings as planet bearings|
    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|
    DE102011087568A1|2011-12-01|2013-06-06|Schaeffler Technologies AG & Co. KG|Bearing pin for planetary gear of spur gear in power train of motor vehicle e.g. truck, has main structure whose first region is provided on both sides of second region of main structure|
    AT512436B1|2012-01-16|2013-10-15|Miba Gleitlager Gmbh|WIND TURBINE|
    DE102012213971A1|2012-08-07|2014-05-22|Zf Friedrichshafen Ag|Planetary gear with ring for absorbing axial forces|
    CN103791039B|2012-10-30|2016-09-14|吴小杰|Bearing grease lubrication wind-powered electricity generation compound-planetary gearbox|
    AT513516B1|2013-01-30|2014-05-15|Miba Gleitlager Gmbh|Wind Turbine Gearbox|
    EP3058245B1|2013-10-15|2020-05-06|FM Energie GmbH & Co. KG|Elastic bushing for a planetary bearing|
    US9797475B2|2014-05-27|2017-10-24|Ge Avio S.R.L.|Epicyclic transmission|EP3480495B1|2017-11-07|2020-04-01|Moventas Gears Oy|A planet wheel assembly for a planetary gear|
    GB201820399D0|2018-12-14|2019-01-30|Rolls Royce Plc|Planet carrier and method of assembling of a planet carrier|
    US11174895B2|2019-04-30|2021-11-16|General Electric Company|Bearing for a wind turbine drivetrain having an elastomer support|
    US11209045B2|2020-02-14|2021-12-28|Pratt & Whitney Canada Corp.|Dual land journal bearings for a compound planetary system|
    CN111648920B|2020-06-23|2022-03-04|湘电风能有限公司|Ultra-compact medium-speed permanent magnet wind generating set|
    法律状态:
    优先权:
    申请号 | 申请日 | 专利标题
    ATA50789/2015A|AT517719B1|2015-09-15|2015-09-15|Planetary gear for a wind turbine|ATA50789/2015A| AT517719B1|2015-09-15|2015-09-15|Planetary gear for a wind turbine|
    US15/758,767| US10451176B2|2015-09-15|2016-09-15|Planetary gearing for a wind turbine having mounted planetary gears|
    PCT/EP2016/071749| WO2017046194A1|2015-09-15|2016-09-15|Planetary gearing for a wind turbine having mounted planetary gears|
    ES16766286T| ES2774507T3|2015-09-15|2016-09-15|Planetary gear for a wind turbine with slidably supported planetary wheels|
    CN201680053454.2A| CN108026975B|2015-09-15|2016-09-15|There is slidably supported planetary gear planetary gear transmission mechanism for wind power plant|
    DK16766286.5T| DK3350464T3|2015-09-15|2016-09-15|Planetary gear for a wind turbine with plain-mounted planetary wheels|
    EP16766286.5A| EP3350464B1|2015-09-15|2016-09-15|Planetary gear train for a wind turbine with slidably mounted planet gears|
    KR1020187010281A| KR20180054685A|2015-09-15|2016-09-15|Planetary gear unit for wind turbine equipped with planetary gears|
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