Wind turbine planet gear shaft and planet gear structure

Abstract

A wind turbine planet gear shaft has a shaft body with an outer surface, a segment of the outer surface being a slide bearing surface configured to form a radial slide bearing with an inner opening of a planet gear. The slide bearing surface has a first portion configured as a non-load-bearing zone and a second portion configured as a load-bearing zone and exactly one axially elongate oil pocket in the slide bearing surface, that oil pocket being located in the non-load-bearing zone. An oil supply channel in the shaft body has a first end in communication with the oil pocket, and first and second oil return channels in the slide bearing surface each have a first end at a longitudinal end of the oil pocket and a second end open to ambient air.

Claims

1. A wind turbine planet gear shaft, comprising: a shaft body having an outer surface, a segment of the shaft body outer surface comprising a slide bearing surface configured to form a radial slide bearing with an inner opening of a planet gear, the slide bearing surface having a first portion configured as a non-load-bearing zone and a second portion configured as a load-bearing zone, exactly one axially elongate oil pocket in the slide bearing surface, the oil pocket being located in the non-load-bearing zone, an oil supply channel in the shaft body having a first end in fluid communication with the oil pocket and a second end, a first oil return channel in the slide bearing surface having a first end at a first longitudinal end of the oil pocket and a second end open to ambient air, and a second oil return channel in the slide bearing surface having a first end at a second longitudinal end of the oil pocket and a second end open to the ambient air.

2. The wind turbine planet gear shaft according to claim 1, wherein the oil supply channel comprises a radial oil feed segment, a radial oil supply segment and an axial oil supply segment fluidly connecting the radial oil feed segment to the radial oil supply segment, wherein an inlet end of the radial oil feed segment is located at an outer radial surface at an end of the shaft body, wherein the axial oil supply segment is located on a central axis of the shaft body, and wherein the radial oil supply segment has an opening inside the oil pocket.

3. The wind turbine planet gear shaft according to claim 2, wherein the oil supply channel further comprises at least one radial auxiliary oil feed segment, wherein a first end of the at least one radial auxiliary oil feed segment is disposed at the first portion of the slide bearing surface, and wherein a second end of the at least one radial auxiliary oil feed segment is in fluid communication with the axial oil supply segment.

4. The wind turbine planet gear shaft according to claim 3, wherein the at least one radial auxiliary oil feed segment is located at a longitudinally central position of the sliding bearing surface.

5. The wind turbine planet gear shaft according to claim 4, wherein the at least one radial auxiliary oil feed segment comprises a first radial auxiliary oil feed segment and a second radial auxiliary oil feed segment, and wherein the first end of the first radial auxiliary oil feed segment is circumferentially spaced from the first end of the second radial auxiliary oil feed segment.

6. The wind turbine planet gear shaft according to claim 3, wherein the first end of the at least one radial auxiliary oil feed segment is conically tapered.

7. The wind turbine planet gear shaft according to claim 2, wherein the axial oil supply segment is a blind bore having a threaded open end open to the ambient air, and wherein the threaded open end is sealed by a threaded plug.

8. The wind turbine planet gear shaft according to claim 1, wherein the segment of the shaft body outer surface comprises a layer of laser-cladding on the outer surface of the shaft body.

9. A wind turbine planet gear assembly, comprising: a planet carrier, a wind turbine planet gear shaft according to claim 1 fixedly mounted to the planet carrier, and the planet gear mounted on the wind turbine planet gear shaft.

10. The wind turbine planet gear assembly according to claim 9, wherein the second end of the oil supply channel is located in a circumferentially extending groove in the outer surface of the shaft body, and wherein the planet carrier includes an oil feed channel in fluid communication with the circumferentially extending groove.

11. The wind turbine planet gear shaft according to claim 1, wherein a radially inner surface of the oil pocket is planar.

12. The wind turbine planet gear shaft according to claim 1, wherein a radially inner surface of the oil pocket is concave.

Description

BRIEF DESCRIPTION OF THE DRAWINGS

[0022] A more detailed description of embodiments of the present invention based is given below, with reference to the drawings.

[0023] FIG. 1 is a schematic perspective view of a structure of a wind turbine planet gear shaft according to an embodiment of the present disclosure.

[0024] FIG. 2 is a schematic perspective view of a structure of a wind turbine planet gear shaft according to another embodiment of the present disclosure.

[0025] FIG. 3 is a schematic view illustrating a distribution of load-bearing forces of a wind turbine planet gear shaft according to the present disclosure.

[0026] FIG. 4 is a left end elevational view of the wind turbine planet gear shaft of FIG. 1.

[0027] FIG. 5 is a sectional view along line A-A in FIG. 4.

[0028] FIG. 6 is a sectional view along line B-B in FIG. 5.

[0029] FIG. 7 is a elevation view of the wind turbine planet gear shaft of FIG. 4 looking in the direction of arrow C.

[0030] FIG. 8 is a elevation view of the wind turbine planet gear shaft of FIG. 4 looking in the direction of arrow D.

[0031] FIG. 9 is a structural schematic view of the wind turbine planet gear shaft of FIG. 6 looking in the direction of arrow E.

[0032] FIG. 10 is an enlarged detail view of region F in FIG. 5.

[0033] FIG. 11 is an enlarged detail view of region G in FIG. 6.

[0034] FIG. 12 is an elevational view, partly in section, of the single oil pocket and the end-to-end-connecting oil feed groove of a wind turbine planet gear shaft according to the present disclosure.

[0035] FIG. 13 is a main sectional view of the wind turbine planet gear structure according to the present disclosure.

DETAILED DESCRIPTION

[0036] The present invention is explained in further detail below in conjunction with the accompanying drawings and specific embodiments, but without limiting the scope of protection of the present invention.

[0037] As shown in FIGS. 1-12, the wind turbine planet gear shaft in this embodiment comprises a shaft body 1, a radial sliding bearing 2, an oil supply component 3 and an oil return component 4. The radial sliding bearing 2 is disposed outside the shaft body 1 and is used to sustain the load of a planet gear 6. The oil supply component 3 comprises an oil supply channel 31 and a single oil pocket 32 which are in communication with each other. Oil enters the single oil pocket 32 through the oil supply channel 31 and provides lubrication for the radial sliding bearing 2. Compared with existing multiple oil pockets, the single oil pocket 32 has an increased load-bearing area, and is better able to bear the load of the planet gear 6.

[0038] As shown in FIG. 3, when the planet gear 6 is running, due to the rotation of the planet gear 6 and the loading action of the outer ring gear and the sun gear on the planet gear 6, the radial sliding bearing 2 will form a pressure oil film, separating the planet gear 6 from the radial sliding bearing 2; at this time, a region where oil film pressure is formed is a load-bearing zone 22 of the radial sliding bearing 2, and a region where oil film pressure is not formed is a non-load-bearing zone 21 of the radial sliding bearing 2. In this embodiment, the single oil pocket 32 is disposed on a surface of the non-load-bearing zone 21 of the radial sliding bearing 2, so that no oil pocket is disposed in the load-bearing zone 22 of the radial sliding bearing 2; this will not alter the internal pressure distribution of the radial sliding bearing 2, further ensuring that the bearing has the maximum load-bearing ability, and thus ensuring the operational reliability and safety of the structure of the wind turbine planet gear 6. Moreover, due to the large oil storage area of the single oil pocket 32, it has a certain degree of oil storage functionality, and there is no need to provide a separate oil storage space inside the shaft body 1; thus, oil storage functionality is ensured, the structure is simple, and processing is convenient.

[0039] At the same time, the oil return component 4 is located on a surface of the radial sliding bearing 2. The oil return component 4 comprises two oil discharge grooves 41, the two oil discharge grooves 41 being respectively disposed at two sides in a length direction of the single oil pocket 32, one end of each oil discharge groove 41 being in communication with the single oil pocket 32 the other end of each oil discharge groove 41 being in communication with external air. In the present disclosure, since the oil return component 4 is disposed on the surface of the radial sliding bearing 2, an oil return region is moved from inside the shaft body 1 to an outer surface of the shaft body 1, thus avoiding problems such as structural complexity and complicated processing associated with an existing oil return component 4 being disposed inside the shaft body 1. Moreover, since the oil discharge groove 41 has separate ends in communication with the single oil pocket 32 and with external air, some of the heated oil in the single oil pocket 32 can be discharged to an external space through the oil discharge groove 41. This increases oil circulation, improves the heat-dissipating and cooling effect of the radial sliding bearing 2, and ensures effective reduction of wear between the wind turbine planet gear shaft and the planet gear 6. While ensuring the cooling effect of the radial sliding bearing 2, the present disclosure further simplifies the structure of the oil return component 4, and is convenient to process.

[0040] Secondly, the configuration of the oil discharge groove 41 increases the gap between the wind turbine planet gear shaft and the planet gear 6, such that impurities and particulates in the lubricating oil can be discharged through the oil discharge groove 41, thus avoiding the problem of being unable to discharge impurities due to too small of a gap between the wind turbine planet gear shaft and the planet gear 6.

[0041] In the present embodiment, circulating oil enters a bearing working face from the oil supply channel 31 and the single oil pocket 32, forming an oil film between the wind turbine planet gear shaft and the planet gear 6, thus preventing damage due to contact wear between the planet gear 6 and the radial sliding bearing 2; the circulating oil is discharged through the oil discharge groove 41 and two ends of the gap between the planet gear 6 and the radial sliding bearing 2, and impurities and particulates, etc. in the lubricating oil are discharged through the oil discharge groove 41.

[0042] As shown in FIG. 11, the single oil pocket 32 is a flat-bottomed rectangular oil pocket, and the oil discharge groove 41 is an arc-shaped oil discharge groove 41. In other embodiments, all structural forms of the single oil pocket 32 that are able to ensure a sufficient oil storage area of the single oil pocket 32 are considered to fall within the scope of protection of the present invention. As shown in FIGS. 2 and 12, the single oil pocket 32 may also be configured as a single oil pocket 32 with an arc-shaped bottom face. All structural forms of the oil discharge groove 41 that are able to ensure discharge of oil and oil impurities should be considered to fall within the scope of protection of the present invention; for example, the oil discharge groove could also be configured as an oil discharge groove that is V-shaped, square or trapezoidal, or in another form. Further, as shown in FIGS. 5 and 7, the oil supply channel 31 comprises a radial main oil feed segment 312, an axial oil supply segment 311 and a radial oil supply segment 314, which are sequentially in communication with each other. An oil feed end of the radial main oil feed segment 312 is located at an outer surface at an end of the shaft body 1, the axial oil supply segment 311 is located on a central axis of the shaft body 1, and the radial oil supply segment 314 is in communication with the single oil pocket 32. This structure is simple and compact, enabling external lubricating oil to be effectively delivered to the position of the radial sliding bearing 2, thus ensuring the lubricating and wear-reducing effect of the radial sliding bearing 2.

[0043] Further, as shown in FIGS. 6 and 9, the oil supply channel 31 further comprises a radial auxiliary oil feed segment 313. One end of the radial auxiliary oil feed segment 313 is disposed on the surface of the non-load-bearing zone 21 of the radial sliding bearing 2, and another end of the radial auxiliary oil feed segment 313 is in communication with the axial oil supply segment 311. The configuration of the radial auxiliary oil feed segment 313 increases the oil feed amount and oil circulation, further improving the cooling and heat-dissipating effect of the radial sliding bearing 2. At the same time, since the radial auxiliary oil feed segment 313 is disposed on the surface of the non-load-bearing zone 21 of the radial sliding bearing 2, the internal pressure distribution of the radial sliding bearing 2 will not be altered, further ensuring the operational reliability and safety of the structure of the wind turbine planet gear 6.

[0044] In this embodiment, the radial auxiliary oil feed segment 313 is located at a central position in a length direction of the radial sliding bearing 2, such that the load-bearing ability of the radial sliding bearing 2 is better; in other embodiments, the radial auxiliary oil feed segment 313 may also deviate from a central position on the radial sliding bearing 2, while ensuring effective bearing of the load of the planet gear 6.

[0045] In this embodiment, there are two radial auxiliary oil feed segments 313, the two radial auxiliary oil feed segments 313 being arranged in a circumferential direction of the shaft body 1; in other embodiments, the number of radial auxiliary oil feed segments 313 may be adjusted according to cooling requirements, e.g. may be set as one, three, four, etc.

[0046] Further, as shown in FIGS. 8 and 9, a conical hole 315 is provided at an oil feed end of the radial auxiliary oil feed segment 313. The configuration of the conical hole 315 eliminates an obtuse angle at the oil feed end of the radial auxiliary oil feed segment 313, reducing the degree of damage after scraping of the radial sliding bearing 2 against the planet gear 6, and ensuring safe running of the planet gear 6. At the same time, the configuration of the conical hole 315 increases oil circulation and helps the radial sliding bearing 2 to form an oil film and to increase a load-bearing capacity.

[0047] As shown in FIG. 5, one end of the axial oil supply segment 311 is a blind end disposed inside the shaft body 1, and another end of the axial oil supply segment 311 is a threaded open end in communication with the outside, with a threaded plug 5 being screwed into the threaded open end. The configuration of the open end facilitates processing of the axial oil supply segment 311, while the threaded plug 5 can block the open end during running and thus prevent oil leakage.

[0048] In this embodiment, the oil discharge groove 41 is an arc-shaped oil discharge groove; this avoids stress concentration during oil delivery and enables impurities and particulates in the lubricating oil to be smoothly discharged through the oil discharge groove 41. In other embodiments, the form of the oil discharge groove 41 may be adjusted according to actual circumstances, e.g. it could also be configured as a trapezoidal oil discharge groove, a square oil discharge groove, etc.

[0049] As shown in FIG. 10, the radial sliding bearing 2 is an alloy wear-resistant bearing, which is formed on the outer surface of the shaft body 1 by laser cladding. Laser cladding results in the shaft body 1 and the alloy wear-resistant bearing being a single piece and has high processing precision and is unlikely to cause deformation of the wear-resistant bearing. Moreover, the strength of bonding between the shaft body 1 and the alloy wear-resistant bearing is high, and the risk of the two parts rotating relative to each other is low, thus avoiding the risk of gearbox damage due to bearing failure. Moreover, the alloy wear-resistant bearing weighs only about 20% of the weight of a wear-resistant layer of a shaft sleeve structure and greatly reduces material costs. In this embodiment, the alloy wear-resistant bearing uses an alloy material such as copper alloy or aluminum alloy.

[0050] As shown in FIG. 13, the wind turbine planet gear structure in this embodiment comprises a planet gear 6, a planet carrier 7 and the abovementioned wind turbine planet gear shaft. The planet gear 6 is fitted round the wind turbine planet gear shaft and rotates relative thereto, and the wind turbine planet gear shaft is fixedly mounted to the planet carrier 7. The wind turbine planet gear structure of the present invention also has the abovementioned advantages of the wind turbine planet gear shaft, and is structurally simple and compact.

[0051] Further, the planet carrier 7 is provided with an oil feed channel 71, the oil feed channel 71 being in communication with the oil supply channel 31. Moreover, an end-to-end-connecting oil feed groove 33 is provided at an end of the oil supply channel 31 which is in communication with the oil feed channel 71 such that the oil feed channel 71 and the oil supply channel 31 are in communication with each other via the end-to-end-connecting oil feed groove 33, thus avoiding a situation where end-to-end connection of the oil feed channel 71 and the oil supply channel 31 cannot be achieved due to installation error. This ensures that external oil is effectively delivered to the wind turbine planet gear shaft.

[0052] Although the present invention has been described with reference to preferred embodiments, various improvements could be made thereto and components therein could be replaced with equivalents without departing from the scope of the present invention. In particular, as long as there is no conflict in terms of structure, various technical features mentioned in various embodiments may be combined in any way. The present invention is not limited to the specific embodiments disclosed herein, but includes all technical solutions falling within the scope of the claims.