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

Abstract

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

Description

Technical Field

[0001] The present invention relates to a lubrication ring for a wind turbine gearbox, preferably for a planetary gearbox, wherein the lubrication ring is configured to be positioned relative to a first gearbox part and a second gearbox part, the lubrication ring extending in a circumferential direction and having a local radial thickness and a local axial height. The lubrication ring is shaped so as to convey lubricating fluid between the first gearbox part and the second gearbox part via lubrication paths within the gearbox parts.

[0002] The invention further relates to a wind turbine gearbox comprising a lubrication ring, a wind turbine and a method for assembling the same. Background Art

[0003] As is known, a wind turbine includes a gearbox arranged between the rotor and the generator for converting the low-speed, high-torque input from the rotor into a high-speed or medium-speed, low-torque output for the generator. The gearbox includes a plurality of gear stages, each rotating on a plain or roller bearing, which is arranged on a corresponding pinion or shaft located within the gearbox.

[0004] Gearboxes are connected to an external lubrication system for circulating oil within the gearbox. The lubricating oil is delivered via lubrication paths to the corresponding bearings and / or gear meshes, ensuring lubrication between the contact surfaces and cooling the gears and / or bearings. A clearance is created between the stationary gearbox housing and the rotating planet carrier to reduce or even eliminate wear under operating and design conditions. A known problem is that this clearance can lead to oil leakage and pressure drops in the circulating oil.

[0005] Typically, a continuous lubrication ring is placed between the stationary gearbox housing and the rotating planet carrier to seal the gap between them. The lubrication ring forms a channel for guiding oil through the gap. A known problem is that the lubrication ring expands radially and axially during heating. This can cause the lubrication ring to close the gap or, when opening the gap on the inside, become lodged on the outside. This causes the lubrication ring to wear and increase oil leakage.

[0006] EP 3056763 B1 discloses a wind turbine gearbox with a lubrication ring assembly arranged between the gearbox housing and the planetary gears. The lubrication ring assembly comprises two rings arranged separately relative to each other to form a continuous opening or multiple openings therebetween. The rings may be made of rubber or a polymer material.

[0007] EP 1488139 B1 discloses a U-shaped ring arranged between a planet carrier and a sun gear, wherein the ring is fixed relative to the planet carrier. The U-shaped ring engages with oppositely facing rods or U-shaped rings on the sun gear. The ring may be made of a polyamide plastic material.

[0008] EP 3094913 B1 discloses an X-shaped ring that forms two channels separated by a central panel, with a plurality of openings arranged therein. The legs of each channel have a curved profile, resulting in a greater thickness at the open end than at the central panel. This allows the legs to press against the contact side surfaces of the corresponding grooves. The X-shaped ring is made of plastic or metal.

[0009] Another solution is disclosed in EP 1767814 B1, in which the gearbox includes an integrated lubrication path connected to an oil lubrication source. A continuous U-shaped ring is secured to the planet carrier and extends into a groove formed in the gearbox housing. It is stated that the ring is sealed against the groove by a labyrinthine structure, but no further details regarding this structure are disclosed. The accompanying drawings merely show the groove as a U-shaped channel element attached to the gearbox housing.

[0010] Lubrication rings can also be used in direct-drive wind turbines, where they are placed around a rotatable shaft that operates at high speeds. An example of this configuration is disclosed in CN 112502912 A, where the lubrication ring forms an internal chamber into which lubricating oil is injected via an external plug. The lubricating oil flows through the interior of the ring via a leaking nozzle.

[0011] Therefore, there is a need for an improved lubrication ring that seals a gap between two gearbox parts, wherein rotational movement occurs between the two gearbox parts. Summary of the Invention

[0012] Purpose of the Invention

[0013] An object of the present invention is to solve the above-mentioned problems of the prior art.

[0014] An object of the present invention is to provide a lubrication ring which reduces or even avoids wear while reducing oil leakage.

[0015] One object of the present invention is achieved by a lubrication ring for a wind turbine gearbox, preferably for a planetary gearbox, according to claim 1, wherein the lubrication ring is configured to be positioned in a first gap formed between a first gearbox part and a second gearbox part, the lubrication ring extending in a circumferential direction and having a cross-sectional profile with a local radial thickness and a local axial height, the lubrication ring forming at least one fluid channel extending in the circumferential direction for conveying lubricating fluid between the first gearbox part and the second gearbox part, the fluid channel being connected to at least one first opening arranged in a transverse wall of the lubrication ring for facilitating the flow of lubricating fluid through the lubrication ring, wherein the lubrication ring comprises a plurality of ring segments, each ring segment having a first local end and an opposite second local end in the circumferential direction, the first end of one ring segment being adapted to be arranged relative to the second end of an adjacent ring segment.

[0016] This invention provides a lubrication ring for a wind turbine gearbox that minimizes or even eliminates wear of the gearbox parts. The lubrication ring is configured to be positioned in a gap (referred to as a first gap) formed between two gearbox parts, which undergo relative rotational movement during operation or idling. The lubrication ring is shaped to substantially seal the gap and reduce oil leakage and pressure drops between the two gearbox parts. The lubrication ring has a segmented configuration, which enables faster and cheaper production and saves material.

[0017] The lubrication ring extends in a circumferential direction and also in radial and axial directions. The lubrication ring has a first axial end and an oppositely facing second axial end, and also has a first radial side face and an oppositely facing second radial side face. The axial direction of the lubrication ring is parallel to the axial direction of the gearbox, while the radial direction of the lubrication ring is perpendicular to the axial direction.

[0018] According to one embodiment, when assembled, a second gap is formed between a first end of one ring segment and a second end of an adjacent ring segment, wherein the ring segments are adapted to expand towards each other in a circumferential direction when heated.

[0019] The lubrication ring is formed from a plurality of ring segments, each of which has an angular length in the circumferential direction, measured between a local circumferential end (referenced as the first end) and an opposite local circumferential end (referenced as the second end). The number of ring segments may depend on the diameter of the lubrication ring and / or the configuration of the gearbox's lubrication path system. During assembly, the first end of one ring segment can be positioned relative to the second end of an adjacent ring segment, and vice versa.

[0020] A gap (referred to as a second gap) may be formed between the first end of one ring segment and the second end of the adjacent ring segment. When heated or cooled by the circulating lubricating fluid, the ring segments may expand or contract at least in the circumferential direction. The circumferential width of the gap may be selected to correspond to an estimated thermal expansion, for example, 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.

[0021] Therefore, the gaps between the individual ring segments absorb most of the thermal expansion, as the diameter of the segmented lubrication ring follows the radial thermal expansion of the ring segments. In conventional continuous lubrication rings, thermal expansion would cause the lubrication ring to expand directly from one diameter to a larger diameter. This can increase wear on the contact surfaces and even cause the lubrication ring to seize.

[0022] The lubrication ring, and thus the ring segments, form at least one fluid channel extending in the circumferential direction. The fluid channel is shaped to guide lubricating fluid along the lubrication ring. A transverse wall extends between two radial sidewalls and includes a plurality of openings (referred to as first openings) for guiding 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 enables the lubrication fluid to be conveyed between the first gearbox section and the second gearbox section.

[0023] In one embodiment, the first end has a first connecting element and the second end has a second connecting element, wherein the first connecting element and the second connecting element are adapted to engage each other when assembled.

[0024] The first end of one ring segment can be configured to engage the second end of an adjacent ring segment, and vice versa. The first end can have a first connecting element, and the second end can have a second connecting element. The first and second connecting elements can be shaped to engage during assembly. The first connecting element can have a convex profile, while the second connecting element can have a concave profile, or vice versa. This helps ensure proper positioning and alignment of the ring segments during assembly.

[0025] In one embodiment, the first connecting element and the second connecting element together form a labyrinth seal in the axial direction, the radial direction and / or the circumferential direction.

[0026] The first connecting element and the second connecting element can also be used as the first sealing element and the second sealing element respectively. The first sealing element and the second sealing element can be locked to each other to form a seal at the gap, such as a multi-stage seal or a non-contact seal. Preferably, the first connecting element and the second connecting element can form a labyrinth seal extending in the axial direction, the radial direction and / or the circumferential direction. The labyrinth seal can accommodate the thermal expansion of the adjacent ring segments. The cross-sectional profile of these first sealing element and the second sealing element (for example, a labyrinth seal) can depend on the cross-sectional profile of the first gearbox part and the second gearbox part and the lubrication ring. This reduces leakage and enables the fluid pressure in the lubrication channel to be relatively constant.

[0027] However, other sealing profiles may also be used to seal the gaps between the ring segments. For example, lip seals, tongue-and-groove seals, male-male seals or female-female seals may be used.

[0028] In one embodiment, the ring segment has a U-shaped, H-shaped or X-shaped cross-sectional profile.

[0029] In the present invention, the cross-sectional profile of the ring segment may be defined at the lubricating fluid delivery opening (referenced as the first opening).

[0030] Each ring segment can have a U-shaped cross-sectional profile, wherein two oppositely facing radial sidewalls and the transverse wall together form a lubrication channel. Here, the transverse wall can also form an end surface at a first axial end of the ring segment. The fluid channel can be arranged at a second axial end of the ring segment. This allows the U-shaped ring segment to have a rigid cross-sectional profile, which also facilitates the manufacturing process of the ring segment.

[0031] Each ring segment may also have an H-shaped cross-sectional profile. Here, the ring segment also includes an interface for at least partially receiving a nozzle or orifice element. The shape of the interface may be designed as a continuous recess arranged in the first axial end, the shape of which may be designed to receive at least a portion of a nozzle or orifice element. The shape of the interface may also be designed as a separate recess arranged in the first axial end, the shape of each recess being designed to receive at least a portion of a specific nozzle or orifice element. The opening in the transverse wall may extend between the lubrication channel and the recess. Therefore, the H-shaped ring segment may have a uniform radial outer thickness and a lower rigid cross-sectional profile. However, compared to the U-shaped ring segment, a more complex manufacturing process may be required.

[0032] Each ring segment can also have an X-shaped cross-sectional profile. Here, the ring segments can have varying radially outer thicknesses, with the minimum radially outer thickness being measured at the radial centerline of the ring segment. The maximum radially outer thickness can be measured between the radial centerline and either the first axial end or the second axial end. Thus, X-shaped ring segments can have a less rigid cross-sectional profile. However, they may require a more complex manufacturing process than U-shaped ring segments.

[0033] The ring segments may have rounded or beveled corners, edges, or wall thicknesses to reduce wear and reduce the overall contact surface area with the corresponding gearbox portion.

[0034] In one embodiment, the lubrication ring further comprises at least one mounting point for securing the lubrication ring to the first gearbox part or the second gearbox part, preferably the lubrication ring is adapted to move in a circumferential direction relative to the at least one mounting point upon expansion.

[0035] Each ring segment can be secured to the first or second gearbox section at multiple mounting points. These mounting points can differ from the location of the nozzle or orifice element. Fastening elements such as bolts, screws, and pins can be used to secure the ring segment to the gearbox section. This allows the ring segment to be secured to one gearbox section while remaining slidable relative to the other gearbox section.

[0036] In one embodiment, the mounting point comprises an elongated opening in the transverse wall adapted to receive a fastening element for securing the lubrication ring.

[0037] The mounting points are preferably shaped as openings in the transverse wall (see second opening). These openings can be elongated. A fastening element can be inserted into each mounting point to secure the ring segment to the gearbox section. The mounting points maintain the ring segment in position circumferentially and accommodate thermal expansion and contraction. The position of the nozzle or orifice element serves as a coordinate origin from which thermal expansion can occur in both circumferential directions.

[0038] In one embodiment, the ring segments are made of a plastic material, a ferrous metal or metal alloy, or a non-ferrous metal or metal alloy.

[0039] The ring segments may be made of a plastic material such as polyamide, silicone, EPDM, rubber or other plastic material. The ring segments may also be made of a ferrous or non-ferrous metal, or a ferrous or non-ferrous metal alloy. However, other suitable materials may also be used.

[0040] The softness (or flexibility) of the ring segments can be selected based on the desired contact pressure and wear on the gearbox parts. Selecting a soft material for the ring segments can reduce the contact pressure on the corresponding gearbox parts. The soft material can also reduce the width of the gap (see first gap) between the gearbox parts, without causing excessive wear in the event of contact.

[0041] An object of the present invention is also achieved by a wind turbine gearbox according to claim 9, comprising a first gearbox part and a second gearbox part, wherein a first gap is formed between the first gearbox part and the second gearbox part, an internal or external lubrication system being connected to the first gap for circulating a lubricating fluid between the first gearbox part and the second gearbox part, wherein a lubrication ring as described above is positioned in the first gap.

[0042] This provides an improved wind turbine gearbox configuration that reduces wear and leakage between the two gearbox parts, where relative rotational motion occurs. The lubrication ring has a segmented configuration that allows most thermal expansion to occur in the circumferential direction. This allows for a smaller gap between the two gearbox parts while reducing wear where the sliding surfaces are in contact.

[0043] The lubrication ring is in fluid communication with a system of lubrication paths within the gearbox. At least one first lubrication path supplies lubricating fluid to the lubrication ring, where the lubricating fluid is directed through the ring segments and into at least one second lubrication path. The second lubrication path directs the lubricating fluid to the corresponding rotating gearbox section. This ensures that the lubricating fluid is delivered to the gear meshes and / or planet carrier bearings.

[0044] A lubrication system, including at least a pump and a lubrication reservoir, may be connected to the lubrication path system for circulating a lubricating fluid, such as lubricating oil, within at least the gearbox. The lubrication system may also include one or more coolers, filters, or other components for removing contaminants and heat from the lubrication fluid. One or more components of the lubrication system may be integrated into the gearbox, or they may be provided as external components connected to the lubrication path system in the gearbox. This allows for better lubrication of the gearbox portion.

[0045] In one embodiment, the lubrication ring is fixed to the gearbox housing or the planet carrier in the gearbox.

[0046] The ring segment can be fixed to the first gearbox part while being able to slide relative to the second gearbox part. The first gearbox part can be stationary, while the second gearbox part can rotate relative to the first gearbox part, or vice versa. Preferably, the first gearbox part can be the gearbox housing, and the second gearbox part can be the planet carrier, or vice versa. Alternatively, both the first gearbox part and the second gearbox part can be rotatable, wherein the first gearbox part and the second gearbox part can rotate at different speeds. Preferably, the first gearbox part can be the first planet carrier or shaft, and the second gearbox part can be the second planet carrier or shaft. This allows the lubrication ring to be axially oriented, thereby allowing axial delivery of lubricating fluid.

[0047] In one embodiment, at least one fluid path is arranged within at least one of the first and second gearbox parts and further connected to the first gap, wherein the nozzle or orifice element is arranged at an opening of the at least one fluid path facing the first gap.

[0048] 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 also include a plurality of second lubrication paths further connected to the gap. The first and second lubrication paths may each include an opening (referred to as a third opening) disposed at oppositely facing axial end surfaces of the respective gearbox portion defining the gap. Thus, the ring segment may be positioned between these axial end surfaces.

[0049] Conversely, the first groove can be formed in the axial end surface of one gearbox portion, such as the first gearbox portion, in the circumferential direction. The first groove can be shaped to at least partially receive one axial end of the ring segment, such as the first axial end. Adjacent lubrication paths, such as the first lubrication path, can preferably connect to the first groove at their bottom surface. Optionally, nozzles or orifice elements can be positioned at their respective openings within all or part of the adjacent first lubrication paths. The nozzles or orifice elements can be configured to compensate for any fluid pressure drops that occur in these lubrication paths.

[0050] Alternatively, a plurality of first recesses may be formed individually in an axial end surface of a gearbox section in the circumferential direction. Each first recess may be connected to an adjacent lubrication path. The first recess may be shaped to at least partially accommodate a nozzle or orifice element. As previously described, each nozzle or orifice element may further extend into an interface at a corresponding axial end of the ring segment. Thus, the nozzle or orifice element can be used to correctly position the ring segment on a gearbox section.

[0051] Preferably, the first groove and optionally the first recess may be formed in a first axial end surface of the first gearbox part. Alternatively, the first groove and optionally the first recess may alternatively be formed in a second axial end surface of the second gearbox part.

[0052] A second groove may further be formed in the circumferentially opposed axial end surfaces of the gearbox sections. The second groove may be shaped to at least partially receive the opposed axial end of the ring segment. The adjacent lubrication path may preferably connect to the second groove at its bottom surface. This allows the lubrication ring to at least partially extend into the grooves on both gearbox sections.

[0053] Preferably, the second groove may be formed in the second axial end surface of the second gearbox part. Alternatively, the second groove may instead be formed in the first axial end surface of the first gearbox part.

[0054] An object of the present invention is further achieved by a wind turbine comprising a wind turbine tower, a nacelle arranged on top of the wind turbine tower, and a rotor having at least one wind turbine blade, the at least one wind turbine blade being arranged relative to the nacelle, wherein the rotor is connected to a gearbox, which is further connected to a generator, wherein a lubrication system is connected to at least a fluid path in the gearbox for circulating a lubricating fluid through the gearbox, wherein the gearbox is constructed as described above.

[0055] This gearbox configuration is suitable for use in a wind turbine, for example, in an integrated drive train. However, the lubrication ring and gearbox can also be used in other drive train configurations. The input of the gearbox can be connected to the rotor of the wind turbine. The output of the gearbox can be connected to the input of the rotor of a generator.

[0056] An object of the present invention is also achieved by a method of assembling a wind turbine gearbox, the method comprising:

[0057] - providing a wind turbine gearbox comprising at least a first gearbox part and a second gearbox part,

[0058] - positioning the first ring segment on one gearbox part, optionally in the first groove,

[0059] - fixing the first ring segment to a gearbox part,

[0060] - positioning at least the second ring segment relative to the first ring segment,

[0061] - fixing the second ring segment to a gearbox part,

[0062] - Optionally, positioning a further ring segment relative to the first ring segment or the second ring segment and securing the further ring segment to a gearbox part until assembly of the lubrication ring is completed.

[0063] This provides a simple and quick method for assembling a wind turbine gearbox for use in a wind turbine. The first ring segment is initially positioned at an axial end surface of one gearbox part, such as the first gearbox part or the second gearbox part. The first ring segment is then secured to the gearbox part, for example using fastening elements as described above. These steps are then repeated until all ring segments are assembled and secured to form a complete lubrication ring.

[0064] Optionally, one or both gearbox parts may be pre-processed before the lubrication ring is installed. For example, the first groove and the second groove and optionally the first recess may be machined into the respective axial end surfaces.

[0065] Once the assembly of the present lubrication ring is complete, the remaining parts of the gearbox can be installed. For example, the opposing gearbox parts are then positioned and aligned relative to one gearbox part to form a gap.

[0066] In one embodiment, a nozzle or orifice element is arranged at an opening of at least one fluid path in one gearbox part before positioning the one or more ring segments relative to the at least one fluid path.

[0067] If necessary, one or more nozzles or orifice elements can be positioned in one or more of the corresponding openings in the fluid path before positioning the ring segments. Alternatively, the nozzles or orifice elements and ring segments can be installed in a combined step. This can compensate for any pressure drops that occur in the lubrication path.

[0068] In one embodiment, the method further comprises the step of positioning the first and second gearbox parts relative to each other such that a first gap is formed between the first and second gearbox parts, preferably with the lubrication ring extending into a second groove in the opposing gearbox part.

[0069] Once the lubrication ring is assembled and secured to one gearbox section, the opposing gearbox section is moved into position and secured to the gearbox, such as the gearbox housing. Alternatively, the opposing gearbox sections can be held in place and one gearbox section moved into position relative to the opposing gearbox section. This allows the remaining sections of the gearbox to be assembled. BRIEF DESCRIPTION OF THE DRAWINGS

[0070] The present invention is now described by way of example only and with reference to the accompanying drawings, in which:

[0071] Figure 1shows an exemplary embodiment of a wind turbine,

[0072] Figure 2 showing a blade shell of a wind turbine blade with a spar cap,

[0073] Figure 3 shows a cross section of a blade shell with two reinforcing webs,

[0074] Figure 4 shows a cross section of a gearbox with a first embodiment of a lubrication ring according to the invention,

[0075] Figure 5 A cross section of a gearbox showing a second embodiment with a lubrication ring,

[0076] Figure 6 showing a plurality of ring segments in an assembled configuration,

[0077] Figure 7 showing the ring segments in an exploded configuration,

[0078] Figure 8 shows the end interface between the first and second ring segments when assembled,

[0079] Figure 9 Shown before assembly Figure 8 the first ring segment and the second ring segment,

[0080] Figure 10 showing a cross section of a first embodiment of a lubrication ring,

[0081] Figure 11 A cross section showing a second embodiment of a lubrication ring,

[0082] Figure 12 shows a cross section of a third embodiment of a lubrication ring, and

[0083] Figure 13 A cross section of a gearbox is shown with a third embodiment of a lubrication ring according to the invention.

[0084] In the following, each of the figures will be described one by one, and different parts and positions seen in the figures will be numbered with the same numbers in different figures. It is not necessary to identify all parts and positions shown in a particular figure with that figure. Figure 1 Start discussing. DETAILED DESCRIPTION

[0085] Figure 1An exemplary embodiment of a wind turbine 1 is shown, comprising a wind turbine tower 2, a nacelle 3 arranged on top of the wind turbine tower 2, and a rotor connected to a drive train in the nacelle 3. The rotor comprises 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.

[0086] The wind turbine 1 is shown here as an onshore wind turbine, but the wind turbine 1 may also be an offshore wind turbine 1 .

[0087] Figure 2 A blade shell 6 of a wind turbine blade 5 is shown having a spar cap 11 that is integrated or bonded to the aerodynamic portion of the blade shell 6. Only one spar cap is shown here, but the blade shell may include more or less than one spar cap. The blade shell 6 may be a continuous blade shell or may include two or more shell parts. The blade shell 6 extends in the spanwise direction from a first end 7 (e.g., a root end) to a second end 8 (e.g., a tip end). The blade shell 6 further extends in the chordwise direction from a first edge 9 (e.g., a leading edge) to a second edge 10 (e.g., a trailing edge).

[0088] Figure 3 A blade shell 6 is shown, wherein two reinforcing webs 12, 12' are arranged within the blade shell 6. The blade shell 6 forms a pressure side 13, comprising an upper spar cap, and a suction side 14, comprising a lower spar cap.

[0089] A shear web 12 extends between the upper and lower spar caps in the thickness direction. The shear web 12 is bonded or integrated with the upper and lower spar caps, respectively. Only one shear web is shown here, but a wind turbine blade may include more than one or less than one shear web.

[0090] Optionally, one or more reinforcing webs 12' are also arranged in the blade shell 6. The reinforcing webs 12' are positioned at a distance from the leading edge 9 and / or the trailing edge 10. The reinforcing webs 12' are combined or integrated with the pressure side 13 and the suction side 14 of the blade shell 6.

[0091] Figure 4 A cross-section of a gearbox with a first embodiment of a lubrication ring according to the present invention is shown. A wind turbine 1 comprises a drive train arranged in a nacelle 3, wherein the drive train comprises at least a gearbox 15 and a generator 16. The gearbox input is connected to the rotor, and the gearbox output is connected to the rotor input of the generator 16.

[0092] The gearbox 15 includes a first gearbox part 17 and a second gearbox part 18 arranged relative to each other. A gap 19 is formed between the oppositely facing axial end surfaces of the respective gearbox parts 17, 18. Here, the second gearbox part 18 is a gearbox housing or a second rotatable gearbox part, such as a shaft or a pinion. Here, the first gearbox part 17 is a planet carrier or a first rotatable gearbox part, such as another shaft or a pinion.

[0093] A lubrication ring 20 is positioned in gap 19 to seal gap 19 and reduce oil leakage and pressure drops between the two gearbox sections during rotation. First gearbox section 17 includes an orifice element 21 disposed at the opening of a plurality of first fluid paths 22 connected to gap 19. Second gearbox section 18 includes a plurality of second fluid paths 23 connected to gap 19.

[0094] Figure 5 A cross section of a gearbox 15 is shown having a second embodiment of a lubrication ring 20. The lubrication ring 20 forms a circumferentially extending fluid passage 24 for conveying lubricating fluid 25 between the first gearbox portion 17 and the second gearbox portion 18. A lubrication system 26 is connected to the first fluid path 22 and the second fluid path 23 and is configured to circulate the lubrication fluid 25 through at least the gearbox 15.

[0095] A first axial end of the lubrication ring 20 extends into a first groove 27 in the first gearbox part 17 . A second axial end of the lubrication ring 20 extends into a second groove 28 in the second gearbox part 18 .

[0096] The fluid passage 24 is connected to a first plurality of openings arranged in a transverse wall 29 of the lubrication ring 20 for facilitating the flow of lubrication fluid 25 through the lubrication ring.

[0097] Figure 6 The lubrication ring 20 is shown in an assembled configuration. The lubrication ring 20 is formed from a plurality of ring segments 20a-20c. The lubrication ring 20 extends in a circumferential direction and has a cross-sectional profile having a local radial width and a local axial height.

[0098] Figure 7 The ring segments 20a-20c are shown in an exploded configuration, wherein each ring segment 20a-20c has a first end 31 and a second end 32 in a circumferential direction. The first end 31 of one ring segment 20a-20c is configured to be positioned relative to the second end 32 of an adjacent ring segment 20a-20c.

[0099] The ring segments 20 a - 20 c include one or more openings 30 a (first openings) for directing the lubrication fluid 25 through the lubrication ring 20 .

[0100] The ring segments 20a-20c further comprise one or more mounting points for securing the ring segments 20a-20c to the gearbox parts 17, 18. Here, the mounting points are shaped as openings 30b, preferably elongated openings, which are shaped to receive fastening elements 33.

[0101] Figure 8 The end interface between the first and second ring segments 20a, 20b is shown during assembly. A gap 34 is formed between the oppositely facing first and second ends 31, 32 of the first and second ring segments 20a, 20b. The width of gap 34 can correspond to the thermal expansion of the ring segments 20a, 20b at a preselected operating temperature. This allows the ring segments 20a-20c to expand in the circumferential direction (indicated by the arrows) when heated. The diameter of the ring segments 20a-20c can follow the thermal expansion in the radial direction.

[0102] Figure 9 The first ring segment 20a and the second ring segment 20b are shown before assembly. The first end 31 has a first connecting element 35, such as a male element. The second end 32 has a second connecting element 36, such as a female element. Here, the first and second connecting elements 35, 36 also serve as first and second sealing elements. The first and second sealing elements interlock to form a seal, preferably a labyrinth seal.

[0103] Figure 10 A cross section of a first embodiment of a lubricating ring 20 is shown. Here, the ring segments 20a-20c have a Figure 7 Here, an interface for at least partially receiving the orifice element 21 is formed in the lubrication ring 20. This interface can be a recess 37 arranged at the first axial end of the ring segments 20a-20c. The opening 30a extends between the fluid channel 24 and the recess 37.

[0104] Figure 11 A cross section of a second embodiment of a lubricating ring 20 is shown. Here, the ring segments 20a-20c have a Figure 7 Here, the first axial end portion has a continuous end surface for contacting the gearbox parts 17, 18. An opening 30a extends between the fluid channel 24 and the axial end surface.

[0105] Figure 12 A cross section of a third embodiment of a lubricating ring 20 is shown. Here, the ring segments 20a-20c have a Figure 7Here, an interface for at least partially receiving the orifice element 21 is formed in the lubrication ring 20. This interface can be a recess 37 arranged at the first axial end of the ring segments 20a-20c. The opening 30a extends between the fluid channel 24 and the recess 37.

[0106] Figure 13 A cross section of a gearbox 15 is shown with a third embodiment of a lubrication ring 20 according to the invention. The ring segments 20a-20c have an X-shaped cross-sectional profile, which extends partially into a first groove 27' on the first gearbox part 17 and partially into a second groove 28 on the second gearbox part 18.

[0107] Here, the orifice element 21 ' is arranged 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 for a wind turbine gearbox (15), preferably a planetary gearbox, wherein: The lubrication ring (20) is configured to be positioned in a first gap (19) formed between a first gearbox portion (17) and a second gearbox portion (18), the lubrication ring (20) extending in a circumferential direction and having a cross-sectional profile having a local radial thickness and a local axial height, the lubrication ring (20) forming at least one fluid channel (24) extending in the circumferential direction for conveying a lubricating fluid (25) between the first gearbox portion (17) and the second gearbox portion (18), the fluid channel (24) being connected to at least one first opening (30a) arranged in a transverse wall (29) of the lubrication ring (20) for facilitating the flow of the lubricating fluid (25) through the lubrication ring (20), characterized in that the lubrication ring (20) comprises a plurality of ring segments (20a-c), each ring segment having a first local end (31) and an opposite second local end (32) in the circumferential direction, the first end (31) of one ring segment being adapted to be arranged relative to the second end (32) of an adjacent ring segment.

2. The lubricating ring according to claim 1, characterized in that When assembled, a second gap (34) is formed between the first end (31) of the one ring segment and the second end (32) of the adjacent ring segment, wherein the ring segments (20a-c) are adapted to expand circumferentially toward each other when heated.

3. The lubricating ring according to claim 1 or 2, characterized in that: The first end (31) has a first connecting element (35) and the second end (32) has a second connecting element (36), wherein the first connecting element (35) and the second connecting element (36) are adapted to engage with each other when assembled.

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

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

6. The lubricating ring according to any one of claims 1 to 5, characterized in that The lubrication ring (20) further comprises at least one mounting point for securing the lubrication ring (20) to the first gearbox part (17) or the second gearbox part (18), preferably, the lubrication ring (20) is adapted to move circumferentially relative to the at least one mounting point upon expansion.

7. The lubricating ring according to claim 6, characterized in that The mounting point comprises an elongated opening (30b) in the transverse wall (29), the elongated opening being adapted to receive a fastening element (33) for securing the lubrication ring (20).

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

9. A wind turbine gearbox comprising a first gearbox part (17) and a second gearbox part (18), wherein: A first gap (19) is formed between the first gearbox part (17) and the second gearbox part (18), an internal or external lubrication system (26) being connected to the first gap (19) for circulating a lubricating fluid (25) between the first gearbox part (17) and the second gearbox part (18), characterized in that a lubrication 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, wherein: The lubrication ring (20) is fixed to a planet carrier or a gearbox housing 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 in at least one of the first gearbox part (17) and the second gearbox part (18) and is further connected to the first gap (19), wherein a nozzle or orifice element (21) is arranged at an opening of the at least one fluid path (22), the opening facing the first gap (19).

12. A wind turbine comprising a wind turbine tower (2), a nacelle (3) arranged on top of the wind turbine tower (2), and a rotor having at least one wind turbine blade (5), the at least one wind turbine blade being arranged relative to the nacelle (3), wherein: The rotor is connected to a gearbox (15), which is further connected to a generator (16), wherein a lubrication system (26) is connected to at least the fluid paths (22, 23) in the gearbox (15) for circulating a lubricating fluid (25) through the gearbox (15), characterized in that the gearbox (15) is constructed according to claim 9 or 11.

13. A method of assembling a wind turbine gearbox (15), comprising: - providing a wind turbine gearbox (15) comprising at least a first gearbox part (17) and a second gearbox part (18), - positioning the first ring segment (20a) on one of the gearbox parts (17, 18), optionally in the first groove (27, 27'), - fixing said first ring segment (20a) to said one gearbox part (17, 18), - positioning at least a second ring segment (20b) relative to said first ring segment (20a), - fixing the second ring segment (20b) to the one gearbox part (17, 18), - Optionally, positioning a further ring segment (20c) relative to the first ring segment (20a) or the second ring segment (20b) and fixing the further ring segment (20c) to the one gearbox part (17, 18) until assembly of the lubrication ring (20) is completed.

14. The method according to claim 13, characterized in that Prior to positioning one or more of the ring segments (20a-c), a nozzle or orifice element (21) is arranged at the opening of at least one fluid path (22, 23) in the one gearbox part (17, 18), wherein the one or more ring segments (20-c) are positioned relative to the at least one fluid path (22).

15. The method according to claim 13 or 14, characterized in that The method further comprises the step of positioning the first gearbox part (17) and the second gearbox part (18) relative to each other such that a first gap (19) is formed between the first gearbox part (17) and the second gearbox part (18), preferably with the lubrication ring (20) extending into a second groove (28) in the opposing gearbox parts (17, 18).

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