Lubrication ring, wind turbine gearbox, wind turbine, and wind turbine gearbox assembly method

Abstract

The present invention relates to a lubrication ring, a wind turbine gearbox, a method for assembling a wind turbine gearbox, and a wind turbine. The lubrication ring is formed by a plurality of ring segments positioned relative to each other in the circumferential direction. Each of these ring segments has a first connecting element and a second connecting element, which are spaced apart from each other to form a gap that absorbs the thermal expansion of the ring segments. The lubrication ring forms at least one fluid path for transporting lubricating fluid between a first gearbox portion and a second gearbox portion positioned relative to each other. Each ring segment has at least one mounting point for fixing the ring segment to the first gearbox portion or the second gearbox portion, and at least one first opening for guiding lubricating fluid through the lubrication ring.

Description

Technical Field

[0001] The present invention relates to a lubricating ring for a wind turbine gearbox, preferably a planetary gear. This lubricating ring is configured to be positioned relative to a first gearbox portion and a second gearbox. The lubricating ring extends circumferentially and has a local radial thickness and a local axial height. The lubricating ring is shaped to transfer lubricating fluid between a first gearbox portion and a second gearbox portion via a lubricating path within the gearbox portion.

[0002] The present invention also relates to a wind turbine gearbox, a wind turbine, and a method of assembling a wind turbine gearbox including this lubricating ring.

Background Art

[0003] It is known that a wind turbine includes a gearbox, which is disposed between a rotor and a generator and is used to convert a low-speed high-torque input from the rotor into a high-speed or medium-speed low-torque output of the generator. The gearbox includes a plurality of gear stages. Each of the plurality of gear stages rotates on a respective pinion or shaft located within the gearbox with a sliding bearing or a roller bearing.

[0004] The gearbox is connected to an external lubrication system for circulating oil through the gearbox. The lubricating oil is transferred via a lubricating path to each bearing and / or gear engagement portion to ensure lubrication between contact surfaces and to cool the gears and / or bearings. A gap is formed between a stationary gearbox housing and a rotating planetary carrier to reduce or avoid wear under operating and design conditions. A known problem is that oil leakage occurs due to this gap, resulting in a pressure drop in the circulating oil.

[0005] Typically, a continuous lubrication ring is positioned between the stationary gearbox housing and the rotating planetary carrier to seal the gap between the gearbox housing and the planetary carrier. The lubrication ring forms a channel for guiding oil through this gap. A known problem is that the lubrication ring expands radially and axially when heated. This can cause the lubrication ring to block the gap or become clogged on the outside while leaving the gap open on the inside, resulting in wear of the lubrication ring and increased oil leakage.

[0006] EP3056763B1 discloses a wind turbine gearbox in which a lubrication ring assembly is positioned between the gearbox housing and the planetary gears. The lubrication ring assembly includes two rings positioned separately from each other to form a continuous opening or multiple openings between them. These rings may be made of rubber or polymer material.

[0007] EP1488139B1 discloses a U-shaped ring positioned between a planetary carrier and a solar gear. This U-shaped ring is fixed to the planetary carrier. The U-shaped ring engages with an opposing stem or U-shaped ring on the solar gear. This ring may be made of polyamide plastic material.

[0008] EP3094913B1 discloses an X-shaped ring that forms two channels separated by an intermediate panel having multiple openings. The legs of each channel have a curved profile so that the thickness at the open end is greater than the thickness of the intermediate panel. This causes the legs to press against the contact sides of the respective grooves. The X-shaped ring is made of plastic or metal.

[0009] EP1767814B1 discloses an alternative solution, in which the gearbox includes an integrated lubrication path connected to an oil lubrication supply device. A continuous U-shaped ring is fixed to the planetary carrier and extends to a groove formed in the gearbox housing. It is stated that this ring is sealed to the groove by a labyrinth structure, but no further details regarding this structure are disclosed. The drawing only shows that the groove is formed as a U-shaped channel element attached to the gearbox housing.

[0010] Lubrication rings can also be used in direct-drive wind turbines where the lubrication ring is positioned around a rotatable rod operating at high speed. An example of such a configuration is disclosed in CN112502912A. The lubrication ring forms an internal chamber, into which lubricating oil is injected via an external plug. The lubricating oil flows through the inside of the ring via a leak nozzle.

[0011] Therefore, an improved lubrication ring is needed to seal the gap between the two gearbox parts, and rotational motion is performed between the two gearbox parts. [Overview of the project]

[0012] One of the objectives of the present invention is to solve the problems of the prior art described above.

[0013] One of the objectives of the present invention is to provide a lubrication ring that reduces or avoids wear while reducing oil leakage.

[0014] One object of the present invention is realized by a lubrication ring used in a wind turbine gearbox, preferably a planetary gearbox, as described in claim 1. The lubrication ring is configured to be positioned within a first gap formed between a first gearbox portion and a second gearbox portion. The lubrication ring has a cross-sectional profile that extends circumferentially and has a local radial thickness and a local axial height. The lubrication ring forms at least one circumferentially extending fluid channel for transporting lubricating fluid between the first gearbox portion and the second gearbox portion. The fluid channel is connected to at least one first opening located in the side wall of the lubrication ring to facilitate the flow of lubricating fluid through the lubrication ring. The lubrication ring comprises a plurality of ring segments, each ring segment having a circumferentially local first end and a local second end on the opposite side, and the first end of one ring segment is configured to be positioned relative to the second end of an adjacent ring segment.

[0015] This provides a lubrication ring for wind turbine gearboxes. This lubrication ring can minimize or completely avoid wear on the gearbox components. The lubrication ring is positioned in the gap formed between two gearbox components (see first gap) and is configured to perform relative rotational motion between the two gearbox components during operation or idling. The lubrication ring is molded to substantially seal the gap, reducing oil leakage and pressure drop between the two gearbox components. The lubrication ring has a segmented configuration, which allows for faster and cheaper manufacturing and reduces waste materials.

[0016] The lubrication ring extends circumferentially, as well as radially and axially. The lubrication ring has a first axial end and a second axial end on the opposite side, and further has a first radial side and a second radial side on the opposite side. The axial direction of the lubrication ring is parallel to the axial direction of the gearbox, and the radial direction of the lubrication ring is perpendicular to the axial direction.

[0017] According to one embodiment, during assembly, a second gap is formed between the first end of one ring segment and the second end of an adjacent ring segment, and the ring segments are configured to expand circumferentially toward each other when heated.

[0018] The lubrication ring is formed by a plurality of ring segments, each ring segment having a circumferential angular length measured between a local circumferential end (see first end) and an opposite local circumferential end (see second end). The number of ring segments may depend on the diameter of the lubrication ring and / or the configuration of the lubrication path system for the gearbox. During assembly, the first end of one ring segment may be positioned relative to the second end of an adjacent ring segment, and the second end of one ring segment may be positioned relative to the first end of an adjacent ring segment.

[0019] A gap (see second gap) may be formed between the first end of one ring segment and the second end of the adjacent ring segment. The ring segments can expand or contract at least circumferentially when heated or cooled by the circulating lubricating fluid. The circumferential width of the gap can be selected, for example, to correspond to the estimated thermal expansion at the maximum operating temperature of the lubricating fluid. The number and / or width of the gaps may depend on the number of ring segments.

[0020] Therefore, the diameter of a segmented lubrication ring follows the radial thermal expansion of the ring segments, and the gaps between individual ring segments absorb most of the thermal expansion. In contrast, with conventional continuous lubrication rings, thermal expansion directly expands the lubrication ring from one diameter to a larger diameter. This can cause wear on the contact surfaces or clog the lubrication ring.

[0021] The lubrication ring forms at least one fluid channel extending circumferentially, and therefore, the ring segments form at least one fluid channel extending circumferentially. The fluid channel is formed to guide the lubricating fluid along the lubrication ring. A side wall extends between two radial side walls and includes a plurality of openings (see first opening) for guiding the lubricating fluid through the lubrication ring. The number of openings may depend on the diameter of the lubrication ring and / or the configuration of the lubrication path system in the gearbox. This allows the lubricating fluid to be transferred between the first gearbox section and the second gearbox section.

[0022] In one embodiment, the first end has a first connecting element, and the second end has a second connecting element, and the first and second connecting elements are configured to engage with each other during assembly.

[0023] The first end of one ring segment may be configured to engage with the second end of an adjacent ring segment, and the second end of one ring segment may be configured to engage with the first end of an adjacent ring segment. The first end may have a first connecting element, and the second end may have a second connecting element. The first and second connecting elements may be molded to engage during assembly. The first connecting element may have a male profile, and the second connecting element may have a female profile, or the first connecting element may have a female profile and the second connecting element may have a male profile. This facilitates the correct orientation and alignment of the ring segments during assembly.

[0024] In one embodiment, both the first and second connecting elements form a labyrinth seal in the axial, radial, and / or circumferential directions.

[0025] The first connecting element and the second connecting element may each function as a first sealing element and a second sealing element. The first sealing element and the second sealing element may interlock to form a seal in the gap, such as a multi-stage seal or a non-contact seal. Preferably, the first connecting element and the second connecting element may form a labyrinth seal extending in the axial direction, the radial direction and / or the circumferential direction. The labyrinth seal can absorb the thermal expansion of adjacent ring segments. The cross-sectional profiles of these first and second sealing elements (e.g., labyrinth seals) may depend on the cross-sectional profiles of the lubricating ring and the first gearbox part and the second gearbox part. This reduces leakage and makes it possible to keep the fluid pressure in the lubrication channel relatively constant.

[0026] However, other seal profiles can also be used to seal the gap between the seal ring segments. For example, lip seals, tongue and groove seals, male-male seals or female-female seals can be used.

[0027] In one embodiment, the ring segment has a U-shaped cross-sectional profile, an H-shaped cross-sectional profile or an X-shaped cross-sectional profile.

[0028] In the present invention, the cross-sectional profile of the ring segment can be defined at the lubricating fluid transfer opening (see the first opening).

[0029] Each ring segment may have a U-shaped cross-sectional profile. Both the two opposing radial side walls and the transverse wall form a lubrication channel. Here, the transverse wall may further form an end face at the first axial end of the ring segment. The fluid channel may be arranged at the second axial end of the ring segment. Thereby, the U-shaped ring segment can have a rigid cross-sectional profile. This simplifies the manufacturing process of the ring segment.

[0030] Each ring segment may have an H-shaped cross-sectional profile. Here, the ring segment includes a joint for at least partially receiving a nozzle or orifice element. The joint may be formed as a continuous recess disposed at the first axial end, and this recess may be formed to accommodate at least a part of the nozzle or orifice element. The joint may also be formed as individual recesses disposed at the first axial end, and each recess may be formed to accommodate at least a part of a specific nozzle or orifice element. The opening of the transverse wall may extend between the lubrication channel and the recess. Thereby, the H-shaped ring segment can have a uniform radial outer thickness and a cross-sectional profile with lower rigidity. However, compared with a U-shaped ring segment, a more complex manufacturing process may be required.

[0031] Each ring segment may have an X-shaped cross-sectional profile. Here, the ring segment may have a varying radial outer thickness. Here, the minimum radial outer thickness can be measured at the radial center line of the ring segment. The maximum radial outer thickness can be measured between the radial center line and the first axial end or the second axial end. Thereby, the X-shaped ring segment can have a cross-sectional profile with lower rigidity. However, compared with a U-shaped ring segment, a more complex manufacturing process may be required.

[0032] The ring segment may have rounded or chamfered corners, edges, or wall thicknesses to reduce wear and reduce the overall contact area with each gearbox part.

[0033] In one embodiment, the lubrication ring further includes at least one mounting point for fixing the lubrication ring to the first gearbox part or the second gearbox part. Preferably, the lubrication ring is configured to move circumferentially relative to at least one mounting point during expansion.

[0034] Each ring segment can be fixed to the first or second gearbox section at multiple mounting points. The positions of the mounting points may differ from the positions of the nozzle or orifice element. The ring segments can be fixed to the gearbox section using fastening elements such as bolts, screws, or pins. This allows the ring segment to be fixed to one of the gearbox sections and to slide relative to other gearbox sections.

[0035] In one embodiment, the mounting point includes an oval opening in the side wall, which is configured to receive a fastening element for securing the lubrication ring.

[0036] The mounting points may preferably be formed as openings in the side wall (see second opening). These openings may be oval-shaped. Fastening elements may be inserted into each mounting point to secure the ring segment to the gearbox portion. The mounting points can hold the ring segment in a predetermined position circumferentially and allow for thermal expansion or contraction of the ring segment. The position of the nozzle or orifice element can function as a coordinate origin from which thermal expansion can occur in both circumferential directions.

[0037] In one embodiment, the ring segment is made of plastic material, black metal or metal alloy, or non-ferrous metal or metal alloy.

[0038] The ring segments may be made of plastic materials such as polyamide, silicone, EPDM, rubber, or other plastic materials. The ring segments may also be made of black metal or non-ferrous metal, or black metal alloy or non-ferrous metal alloy. Other suitable materials may also be used.

[0039] The softness (or flexibility) of the ring segments can be selected based on the desired contact pressure and wear on the gearbox components. Selecting a softer material for the ring segments reduces the contact pressure on each gearbox component. Furthermore, using a softer material allows for a narrower gap between gearbox components (see first gap) without excessive wear during contact.

[0040] One of the objects of the present invention is also achieved by the wind turbine gearbox described in claim 9. This gearbox includes a first gearbox portion and a second gearbox portion. A first gap is formed between the first gearbox portion and the second gearbox portion. An internal or external lubrication system is connected to the first gap to circulate a lubricating fluid between the first gearbox portion and the second gearbox portion. The lubrication ring is positioned within the first gap.

[0041] This provides an improved wind turbine gearbox configuration that reduces wear and leakage between two gearbox parts performing relative rotational motion. The lubrication ring has a segmented configuration, allowing most of the thermal expansion to occur circumferentially. This allows for a smaller gap between the two gearbox parts while reducing wear where the sliding surfaces are in contact.

[0042] The lubrication ring is in fluid communication with the lubrication path system within the gearbox. At least one first lubrication path supplies lubrication fluid to the lubrication ring. The lubrication fluid is guided through the ring segments into at least one second lubrication path. The second lubrication path guides the lubrication fluid to each rotating gearbox portion. This ensures that the lubrication fluid is delivered to the gear meshing parts and / or planetary carrier bearings.

[0043] A lubrication system including at least a pump and a lubrication reservoir can be connected to the lubrication system to circulate a lubricating fluid, such as lubricating oil, at least within the gearbox. The lubrication system may include one or more coolers, filters, and other components to remove contaminants and heat from the lubricating fluid. One or more components of the lubrication system may be integrated into the gearbox or provided as external components connected to the lubrication system within the gearbox. This allows for better lubrication of the gearbox portion.

[0044] In one embodiment, the lubrication ring is fixed to the gearbox housing or to the planetary carrier within the gearbox.

[0045] The ring segment may slide relative to the second gearbox portion, while being fixed to the first gearbox portion. The first gearbox portion may be stationary, and the second gearbox portion may rotate relative to the first gearbox portion, or the second gearbox portion may be stationary, and the first gearbox portion may rotate relative to the first gearbox portion. Preferably, the first gearbox portion may be a gearbox housing and the second gearbox portion may be a planetary carrier, or the second gearbox portion may be a gearbox housing and the first gearbox portion may be a planetary carrier. Alternatively, both the first and second gearbox portions may rotate, and they may rotate at different speeds. Preferably, the first gearbox portion may be a first planetary carrier or shaft, and the second gearbox portion may be a second planetary carrier or shaft. This allows for the axial orientation of the lubrication ring, and therefore the axial transfer of the lubricating fluid.

[0046] In one embodiment, at least one fluid path is located inside at least one of the first gearbox portion and the second gearbox portion, and the at least one fluid path is further connected to a first gap. A nozzle or orifice element is located in the opening of the at least one fluid path facing the first gap.

[0047] The first gearbox portion may include a plurality of first lubrication paths connected to the gap between the two gearbox portions. The second gearbox portion may similarly include a plurality of second lubrication paths further connected to its gap. Each of the first and second lubrication paths may include an opening (see third opening) located on the opposing axial end faces of the respective gearbox portions that define the gap. Thus, the ring segment may be positioned between these axial end faces.

[0048] Alternatively, a first groove may be formed circumferentially on the axial end face of one gearbox portion, for example, a first gearbox portion. The first groove may be molded to at least partially receive one axial end of a ring segment, for example, a first axial end. Adjacent lubrication passages, for example, a first lubrication passage, may be connected to the first groove, preferably at the bottom. Optionally, nozzles or orifice elements may be positioned within all or part of adjacent first lubrication passages, at their respective openings. The nozzles or orifice elements may be configured to compensate for a drop in fluid pressure in these lubrication passages.

[0049] Alternatively, a plurality of first recesses may be individually formed in the circumferential direction on one axial end face of one gearbox portion. Each first recess may be connected to an adjacent lubrication path. The first recesses may be molded to at least partially receive a nozzle or orifice element. Each nozzle or orifice element may further extend into the joint of the corresponding axial end of the ring segment, as described above. Thus, the nozzle or orifice element can be used to precisely position the ring segment in one gearbox portion.

[0050] Preferably, the first groove and optionally the first recess may be formed on the first axial end face of the first gearbox portion. Alternatively, the first groove and optionally the first recess may instead be formed on the second axial end face of the second gearbox portion.

[0051] A second groove may be further formed in the circumferential direction on the opposing axial end faces of the opposing gearbox portions. The second groove may be shaped to at least partially receive the opposing axial ends of the ring segments. Adjacent lubrication passages may be connected to the second groove, preferably at their bottom surfaces. This allows the lubrication ring to extend into the grooves, at least partially, on both gearbox portions.

[0052] Preferably, the second groove may be formed on the second axial end face of the second gearbox portion. Alternatively, the second groove may be formed on the first axial end face of the first gearbox portion.

[0053] One of the objectives of the present invention is further achieved by a wind turbine. This wind turbine includes a wind turbine tower, a nacelle located at the top of the wind turbine tower, and a rotor having at least one wind turbine blade positioned relative to the nacelle. The rotor is connected to a gearbox, which is further connected to a generator. A lubrication system is connected to at least a fluid path within the gearbox to circulate a lubricating fluid through the gearbox. The gearbox is configured as described above.

[0054] This gearbox configuration is suitable for use in wind turbines, such as integrated drivetrains. However, this lubrication ring and gearbox may be used in other drivetrain configurations. The input of the gearbox may be connected to the rotor of the wind turbine. The output of the gearbox may be connected to the input of the rotor of a generator.

[0055] One of the objectives of the present invention is also achieved by a method for assembling a wind turbine gearbox. This method is - The step of providing a wind turbine gearbox including at least a first gearbox portion and a second gearbox portion, - The step of positioning the first ring segment in a gearbox portion, optionally within the first groove, - The step of fixing the first ring segment to the gearbox portion mentioned above, - A step of positioning at least the second ring segment relative to the first ring segment, - The step of fixing the second ring segment to the above-mentioned gearbox portion, - Optionally, the step of positioning an additional ring segment relative to the first or second ring segment and securing the additional ring segment to the one gearbox portion until the assembly of the lubrication ring is complete.

[0056] This provides a simple and rapid method for assembling a wind turbine gearbox. First, the first ring segment is positioned on the axial end face of one gearbox section, for example, the first gearbox section or the second gearbox section. Next, the first ring segment is secured to the gearbox section, for example, using the fastening elements described above. These steps are repeated until all ring segments are assembled and secured to form a complete lubrication ring.

[0057] Optionally, one or both gearbox portions may be pre-treated before installing the lubrication ring. For example, the first groove, the second groove, and optionally the first recess may be machined into their respective axial end faces.

[0058] Once the lubrication ring is assembled, the rest of the gearbox can be assembled. For example, the opposite gearbox section can then be positioned and aligned with the other gearbox section to create a gap.

[0059] In one embodiment, the nozzle or orifice element is positioned in the opening of at least one fluid path in one gearbox portion before positioning one or more ring segments. One or more ring segments are then positioned relative to at least one fluid path.

[0060] If necessary, one or more nozzles or orifice elements can be positioned at one or more openings in the fluid path before positioning the ring segment. Alternatively, the nozzles or orifice elements and the ring segment may be mounted in a combined step. This can compensate for pressure drops in the lubrication path.

[0061] In one embodiment, the method further includes the step of forming a first gap between a first gearbox portion and a second gearbox portion by positioning the first gearbox portion and the second gearbox portion relative to each other. Preferably, the lubrication ring extends into a second groove of the opposing gearbox portion.

[0062] After assembling this lubrication ring and fixing it to one of the gearbox sections, the opposing gearbox section is moved to its predetermined position and fixed to the gearbox, for example, the gearbox housing. Alternatively, the opposing gearbox sections are held in place, and one gearbox section is moved to its predetermined position relative to the opposing gearbox section. This allows the remaining parts of the gearbox to be assembled. [Brief explanation of the drawing]

[0063] The present invention will be described with reference to the accompanying drawings, merely as an example. [Figure 1] An exemplary embodiment of a wind turbine is shown. [Figure 2] This shows the blade shell of a wind turbine blade equipped with a spur cap. [Figure 3] This shows a cross-section of a blade shell with two reinforcing webs. [Figure 4] This shows a cross-section of a gearbox equipped with a first embodiment of the lubrication ring according to the present invention. [Figure 5] A cross-section of a gearbox equipped with a second embodiment of the lubrication ring is shown. [Figure 6] This shows multiple ring segments in the assembly configuration. [Figure 7] The ring segment in the decomposed structure is shown. [Figure 8] This shows the end joint between the assembled first ring segment and the second ring segment. [Figure 9] Figure 8 shows the first and second ring segments before assembly. [Figure 10] A cross-section of the first embodiment of the lubrication ring is shown. [Figure 11] A cross-section of a second embodiment of the lubrication ring is shown. [Figure 12] A cross-section of a third embodiment of the lubrication ring is shown. [Figure 13] This shows a cross-section of a gearbox equipped with a third embodiment of the lubrication ring according to the present invention.

[0064] The following explains each figure in turn. Different parts or locations within a figure may be indicated by the same reference number in different figures. Not all parts or locations shown in a particular figure are necessarily explained in relation to that figure. [Modes for carrying out the invention]

[0065] Figure 1 shows an exemplary embodiment of a wind turbine 1. The wind turbine 1 includes a wind turbine tower 2, a nacelle 3 located at the top of the wind turbine tower 2, and a rotor connected to a drivetrain within the nacelle 3. The rotor includes a hub 4 and at least one wind turbine blade 5 connected to the hub 4. Here, three wind turbine blades 5 are shown, but the hub may be connected to more or fewer wind turbine blades.

[0066] Although wind turbine 1 is shown as an onshore wind turbine, wind turbine 1 may also be an offshore wind turbine 1.

[0067] Figure 2 shows a blade shell 6 of a wind turbine blade 5 having a spur cap 11, the spur cap 11 being integrated with or bonded to the aerodynamic portion of the blade shell 6. Although only one spur cap is shown here, the blade shell may contain more or fewer spur caps. The blade shell 6 may be a continuous blade shell or may contain two or more shell portions. The blade shell 6 extends in the wing-length direction from a first end 7 (e.g., root) to a second end 8 (e.g., tip). The blade shell 6 further extends in the chord direction from a first edge 9 (e.g., leading edge) to a second edge 10 (e.g., trailing edge).

[0068] Figure 3 shows a blade shell 6 having two reinforcing webs 12, 12' arranged within the blade shell 6. The blade shell 6 forms a pressure side 13 including an upper spur cap and a suction side 14 including a lower spur cap.

[0069] The shear web 12 extends in the thickness direction between the upper spur cap and the lower spur cap. The shear web 12 is bonded or integrated with the upper and lower spur caps, respectively. Although only one shear web is shown here, a wind turbine blade may contain more or fewer shear webs.

[0070] Optionally, one or more reinforcing webs 12' are further positioned within the blade shell 6. The reinforcing webs 12' are positioned at a certain distance from the leading edge 9 and / or trailing edge 10. The reinforcing webs 12' are bonded or integrated with the pressure side 13 and suction side 14 of the blade shell 6.

[0071] Figure 4 shows a cross-section of a gearbox equipped with a first embodiment of the lubrication ring according to the present invention. The wind turbine 1 includes a drivetrain located within a nacelle 3. The drivetrain includes at least a gearbox 15 and a generator 16. The input of the gearbox is connected to the rotor, and the output of the gearbox is connected to the rotor input of the generator 16.

[0072] The gearbox 15 includes a first gearbox portion 17 and a second gearbox portion 18 arranged relative to each other. A gap 19 is formed between the opposing axial end faces of the respective gearbox portions 17 and 18. Here, the second gearbox portion 18 is a gearbox housing or a second rotatable gearbox portion, such as a shaft or pinion. Here, the first gearbox portion 17 is a planetary carrier or a first rotatable gearbox portion, such as another shaft or pinion.

[0073] A lubrication ring 20 is positioned in the gap 19 to seal the gap 19 and reduce oil leakage and pressure drop between the two gearbox parts during rotation. The first gearbox part 17 includes an orifice element 21, which is positioned at the opening of a plurality of first fluid paths 22 connected to the gap 19. The second gearbox part 18 includes a plurality of second fluid paths 23 connected to the gap 19.

[0074] Figure 5 shows a cross-section of a gearbox 15 having a second embodiment of the lubrication ring 20. The lubrication ring 20 forms a fluid channel 24, which extends circumferentially to transport lubricating fluid 25 between the first gearbox portion 17 and the second gearbox portion 18. The lubrication system 26 is connected to the first fluid path 22 and the second fluid path 23 and is configured to circulate the lubricating fluid 25 at least through the gearbox 15.

[0075] The first axial end of the lubrication ring 20 extends into the first groove 27 of the first gearbox portion 17. The second axial end of the lubrication ring 20 extends into the second groove 28 of the second gearbox portion 18.

[0076] The fluid channel 24 is connected to a plurality of first openings located in the side wall 29 of the lubrication ring 20, facilitating the flow of lubricating fluid 25 through the lubrication ring.

[0077] Figure 6 shows the lubrication ring 20 in its assembled configuration. The lubrication ring 20 is formed from a plurality of ring segments 20a to 20c. The lubrication ring 20 extends in the circumferential direction and has a cross-sectional profile with a local radial width and a local axial height.

[0078] Figure 7 shows the ring segments 20a to 20c in an exploded configuration, each having a first end 31 and a second end 32 in the circumferential direction. The first end 31 of one ring segment 20a to 20c is configured to be positioned relative to the second end 32 of an adjacent ring segment 20a to 20c.

[0079] The ring segments 20a to 20c include one or more openings 30a (first opening) for guiding the lubricating fluid 25 through the lubricating ring 20.

[0080] The ring segments 20a to 20c further include one or more mounting points for securing the ring segments 20a to 20c to the gearbox portions 17 and 18, where the mounting points are formed as openings 30b, preferably oval openings, to receive fastening elements 33.

[0081] Figure 8 shows the end joint between the assembled first ring segment 20a and the second ring segment 20b. A gap 34 is formed between the opposing first end 31 and second end 32 of the first ring segment 20a and the second ring segment 20b. The width of the gap 34 may correspond to the thermal expansion of the ring segments 20a and 20b, which is determined by a pre-selected operating temperature. This allows the ring segments 20a to 20c to expand circumferentially when heated (indicated by arrows). The diameters of the ring segments 20a to 20c may follow the radial thermal expansion.

[0082] Figure 9 shows the first ring segment 20a and the second ring segment 20b before assembly. The first end 31 has a first connecting element 35, for example, a male element. The second end 32 has a second connecting element 36, for example, a female element. Here, the first connecting element 35 and the second connecting element 36 also function as a first sealing element and a second sealing element. The first sealing element and the second sealing element interlock to form a seal, preferably a labyrinth seal.

[0083] Figure 10 shows a cross-section of a first embodiment of the lubrication ring 20. Here, the ring segments 20a to 20c have an X-shaped cross-sectional profile along line AA shown in Figure 7. The lubrication ring 20 has a joint formed for at least partially receiving the orifice element 21. This joint may be a recess 37 located at the first axial ends of the ring segments 20a to 20c. The opening 30a extends between the fluid channel 24 and the recess 37.

[0084] Figure 11 shows a cross-section of a second embodiment of the lubrication ring 20. Here, the ring segments 20a to 20c have a U-shaped cross-sectional profile along line AA shown in Figure 7. The first axial end has a continuous end face for contact with the gearbox portions 17 and 18. The opening 30a extends between the fluid channel 24 and the axial end face.

[0085] Figure 12 shows a cross-section of a third embodiment of the lubrication ring 20. Here, the ring segments 20a to 20c have an H-shaped cross-sectional profile along line AA shown in Figure 7. The lubrication ring 20 has a joint formed for at least partially receiving the orifice element 21. This joint may be a recess 37 located at the first axial ends of the ring segments 20a to 20c. The opening 30a extends between the fluid channel 24 and the recess 37.

[0086] Figure 13 shows a cross-section of a gearbox 15 equipped with a third embodiment of the lubrication ring 20 according to the present invention. The ring segments 20a to 20c have an X-shaped cross-sectional profile and partially extend into the first groove 27' on the first gearbox portion 17 and partially extend into the second groove 28 on the second gearbox portion 18.

[0087] Here, the orifice element 21' is positioned at the opening of the first fluid path 22'. The opening is located at the bottom of the first groove 27'.

Claims

1. A lubrication ring used in a wind turbine gearbox (15), preferably a planetary gearbox, wherein the lubrication ring (20) is configured to be positioned within a first gap (19) formed between a first gearbox portion (17) and a second gearbox portion (18), the lubrication ring (20) has a cross-sectional profile that extends circumferentially and has a local radial thickness and a local axial height, and the lubrication ring (20) has at least one circumferentially extending fluid channel (24) for moving a lubricating fluid (25) between the first gearbox portion (17) and the second gearbox portion (18). A lubricating ring is formed, wherein the fluid channel (24) is connected to at least one first opening (30a) located in the side wall (29) of the lubricating ring (20) to facilitate the flow of lubricating fluid (25) through the lubricating ring (20), and the lubricating ring (20) comprises a plurality of ring segments (20a to 20c), each ring segment having a circumferentially local first end (31) and a local second end (32) on the opposite side, and the first end (31) of one ring segment is configured to be positioned relative to the second end (32) of an adjacent ring segment.

2. The lubricating ring according to claim 1, characterized in that, during assembly, a second gap (34) is formed between the first end (31) of one ring segment and the second end (32) of the adjacent ring segment, and the ring segments (20a to 20c) are configured to expand toward each other in the circumferential direction when heated.

3. The lubrication ring according to claim 1 or 2, characterized in that the first end (31) has a first connecting element (35), the second end (32) has a second connecting element (36), and the first connecting element (35) and the second connecting element (36) are configured to engage with each other during assembly.

4. The lubrication ring according to claim 2 or 3, characterized in that both the first connecting element (35) and the second connecting element (36) form a labyrinth seal in the axial, radial, and / or circumferential directions.

5. The lubrication ring according to any one of claims 1 to 4, characterized in that the ring segments (20a to 20c) have a U-shaped cross-sectional profile, an H-shaped cross-sectional profile, or an X-shaped cross-sectional profile.

6. The lubricating ring (20) further includes at least one mounting point for fixing the lubricating ring (20) to the first gearbox portion (17) or the second gearbox portion (18), and preferably the lubricating ring (20) is configured to move circumferentially with respect to the at least one mounting point when expanded, as described in any one of claims 1 to 5.

7. The lubrication ring according to claim 6, characterized in that the mounting point includes an oval opening (30b) in the side wall (29), and the oval opening (30b) is configured to receive a fastening element (33) for fixing the lubrication ring (20).

8. The lubricating ring according to any one of claims 1 to 7, characterized in that the ring segments (20a to 20c) are made of plastic, black metal or metal alloy, or non-ferrous metal or metal alloy.

9. A wind turbine gearbox comprising a first gearbox portion (17) and a second gearbox portion (18), wherein a first gap (19) is formed between the first gearbox portion (17) and the second gearbox portion (18), and an internal or external lubrication system (26) is connected to the first gap (19) so that a lubricating fluid (25) circulates between the first gearbox portion (17) and the second gearbox portion (18), wherein a lubricating ring (20) according to any one of claims 1 to 8 is positioned in the first gap (19).

10. The wind turbine gearbox according to claim 9, characterized in that the lubrication ring (20) is fixed to the gearbox housing or the planetary carrier in the gearbox (15).

11. The wind turbine gearbox according to claim 9 or 10, characterized in that at least one fluid path (22, 23) is arranged inside at least one of the first gearbox portion (17) and the second gearbox portion (18), and the at least one fluid path (22, 23) is connected to the first gap (19), and a nozzle or orifice element (21) is arranged in an opening of the at least one fluid path (22) facing the first gap (19).

12. A wind turbine comprising a wind turbine tower (2), a nacelle (3) positioned on top of the wind turbine tower (2), and a rotor having at least one wind turbine blade (5) positioned relative to the nacelle (3), wherein the rotor is connected to a gearbox (15), the gearbox (15) is further connected to a generator (16), and a lubrication system (26) is connected to at least fluid paths (22, 23) within the gearbox (15) to circulate a lubricating fluid (25) through the gearbox (15), and the gearbox (15) is configured according to claim 9 or 11.

13. A method for assembling a wind turbine gearbox (15), wherein the method is: - A step of providing a wind turbine gearbox (15) including at least a first gearbox portion (17) and a second gearbox portion (18), - A step of positioning the first ring segment (20a) on one gearbox portion (17, 18), optionally within the first groove (27, 27'), - The step of fixing the first ring segment (20a) to the one gearbox portion (17, 18), - A step of positioning at least the second ring segment (20b) relative to the first ring segment (20a), - The step of fixing the second ring segment (20b) to the one gearbox portion (17, 18), A method comprising the optional step of positioning an additional ring segment (20c) relative to the first ring segment (20a) or the second ring segment (20b) until the assembly of the lubrication ring (20) is completed, and fixing the additional ring segment (20c) to the one gearbox portion (17, 18).

14. The method according to 13, characterized in that, before positioning one or more ring segments (20a to 20c), a nozzle or orifice element (21) is placed in the opening of at least one fluid path (22, 23) in one of the gearbox portions (17, 18), and the one or more ring segments (20a to 20c) are positioned with respect to the at least one fluid path (22).

15. The method according to 13 or 14, further comprising the step of positioning the first gearbox portion (17) and the second gearbox portion (18) relative to each other to form a first gap (19) between the first gearbox portion (17) and the second gearbox portion (18), preferably the lubrication ring (20) extends into a second groove (28) of the opposing gearbox portions (17, 18).

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