DE102020133993A1 - Bearing arrangement for a rotating component of a wind turbine and wind turbine - Google Patents

Abstract

The invention relates to a bearing arrangement (114) for a rotating component of a wind turbine (100), having a roller bearing (126) with a bearing inner ring (130) and a bearing outer ring (132), the bearing inner ring (130) being coupled to a first component (118). is, the bearing outer ring (132) is coupled to a second component (142), between bearing inner and bearing outer ring (130, 132) rolling elements (134) are arranged, the first component (118) and the second component (142) with respect to an axis of rotation (116) of the bearing arrangement (114) are rotatable relative to one another, the bearing outer ring (132) has a flange projection (154) which extends in the radial direction with respect to the axis of rotation (116), and between the flange projection (154) and the second component (142 ) an adjusting device (158) is arranged, which is designed to set a bearing preload force or a bearing play in the axial direction with respect to the axis of rotation (116). The invention also relates to a Wi nd energy plant (100).

Description

The invention relates to a bearing arrangement for a rotating component of a wind turbine. The invention also relates to a wind energy plant with such a bearing arrangement.

Wind turbines with wind turbine rotor blades (hereinafter also briefly: rotor blades) are widely known from the prior art and are used to convert wind energy into electrical energy. It is known to use roller bearings to support rotating components of wind turbines. The roller bearings, such as tapered roller bearings, are often preloaded in order to enable the most trouble-free operation possible and to reduce bearing damage.

An object on which the invention is based is to specify a concept for mounting rotating components of a wind turbine that reduces or prevents the occurrence of bearing damage, so that the service life of the bearings is increased and maintenance costs are minimized.

According to a first aspect, a bearing arrangement for a rotating component of a wind turbine is disclosed. The bearing arrangement has a roller bearing with a bearing inner ring and a bearing outer ring. The bearing inner ring is coupled to a first component. The bearing outer ring is coupled to a second component. Rolling elements are arranged between the inner and outer ring of the bearing. The first component and the second component can be rotated relative to one another with respect to an axis of rotation of the bearing arrangement. The bearing outer ring has a flange projection extending in the radial direction with respect to the axis of rotation. An adjusting device is arranged between the flange projection and the second component, which is designed to set a bearing preload force or a bearing play in the axial direction with respect to the axis of rotation.

In conventional bearing arrangements, the bearing preload or bearing clearance (negative preload) would be set during (initial) assembly in production. Subsequent changing of the preload, for example in the case of an adjusted tapered roller bearing, would be extremely difficult or involve a great deal of effort. For example, measurement and additional manufacturing steps, such as grinding and, if necessary, replacement of corresponding components such as clamping rings or bearing caps, would be necessary. In other cases, as an alternative to grinding in, spacer plates with defined graduated thicknesses can also be used. To simplify assembly, segmented metal sheets could also be used in order to be able to bring them in radially. It should be noted that with such types of assembly, bearings or bearing inner rings are heated, for example, in order to be able to pull them onto a shaft, because an interference fit with a large oversize is typically provided for the connection of the bearing inner ring to the shaft in order to avoid ring creep, which frequently generate fretting corrosion and lead to a fatigue strength problem. This is especially true for bearing arrangements and loading situations where a circumferential load acts on the bearing inner ring. Typically, a dimension chain is first determined and the components for applying the prestress are ground in or suitable spacer plates are put together. These components must be prepared to such an extent that assembly can take place before the cooling process is complete, or an auxiliary device must be used to apply the prestress during the cooling process. This is followed by measuring, grinding in or the selection of the spacer plates and then assembly (the device must be able to be dismantled after the assembly of the components).

The arrangement according to the invention provides that the prestressing force or the bearing play of the roller bearing is adjusted via the flange projection. According to the invention, the prestressing force (negative or positive) acts axially between the flange projection and the second component. The preload force acts on the rolling elements and the bearing inner ring via the bearing outer ring. For this purpose, the adjusting device is provided, which is arranged or acts between the flange projection and the second component. In other words, according to the invention, the flange projection is provided for receiving the adjusting device or for receiving the force that is applied by means of the adjusting device in order to realize the prestressing of the bearing. This offers a number of advantages and technical effects, which are described below.

The bearing arrangement disclosed enables a particularly simple adjustment of the bearing preload during initial assembly and readjustment (in particular without complete disassembly) after the bearing arrangement or the machine/system such as a wind turbine has been put into operation. As a result, changes to the "ideal" bearing preload due to e.g. settling phenomena, tolerances, thermal expansion can be compensated. This leads to an increase in the bearing service life and thus to lower so-called "life cycle" costs.

Another advantage is that no additional components such as a sleeve are required to set the preload force, for example in the case of preload via a bearing outer ring a flange is provided according to the invention on the bearing outer ring. A sleeve solution would be disadvantageous, for example, in terms of realizing the necessary manufacturing requirements for a double snug fit, especially with large bearing dimensions such as those prevailing in wind turbines. By avoiding additional components, the risk of fretting corrosion is significantly reduced.

The bearing arrangement is used, for example, in the bearing of the rotors of wind turbines. Especially in the current system developments of the multi-megawatt class, rotor bearing concepts with tapered roller bearings are increasingly being seen, for example two tapered roller bearings placed in an O arrangement. Furthermore, the solution according to the invention could also be used for the offset bearings in gearbox construction in wind turbines, such as on the high-speed output shaft, in order to reduce the risk of bearing slip, among other things.

The flange projection extends radially away from the axis of rotation. According to one embodiment, the flange projection is a projection that runs annularly around the axis of rotation. According to embodiments, the flange protrusion is a partially circumferential section or several circumferential sections that are spaced apart from one another. The flange projection is preferably formed in one piece with the bearing outer ring. In other words, the flange projection is an integral part of the bearing outer ring.

The bearing outer ring and the bearing inner ring are respectively coupled or fixed to the first and second component. Appropriate fits, shaft shoulders, etc. are available for this so that the roller bearing can be preloaded accordingly. For example, an interference fit is provided between the first component and the bearing inner ring, while a transition or clearance fit is preferably formed between the second component and the bearing outer ring in order to simplify the setting of the preload. However, an interference fit between the second component and the outer bearing ring would also be conceivable. In other words, the outer bearing ring is fixed somewhat more loosely than the inner bearing ring, for example.

For example, a gap between the flange projection and the second component is to be provided for the preload setting, taking into account the dimensional chain and tolerances. During assembly, this gap is bridged by the adjusting device, thereby causing the bearing unit to be braced.

The bearing inner ring is located closer to the axis of rotation than the bearing outer ring.

According to one embodiment, the first component is, for example, a rotatable shaft and the second component is a stationary bearing housing. Fixed means that the second component is stationary with respect to the shaft. In other words, the second component is stationary in relation to the bearing arrangement.

According to one embodiment, the first component is a stationary axle and the second component is a rotatable element, for example a hollow shaft. What was said above with regard to the term stationary applies analogously, with the axis being stationary relative to the hollow shaft.

According to one embodiment, the flange projection is an integral part of the bearing outer ring. This contributes, among other things, to reduced manufacturing costs, simpler assembly and easier adjustability of the bearing preload.

According to one embodiment, the flange boss and/or the bearing cup are forged or machined from solid stock. In particular, a forged bearing outer ring including the flange projection enables comparatively low costs and high strength, which is particularly advantageous for large diameter bearings, such as a rotor bearing in a wind turbine or a planetary carrier bearing in multi-megawatt class gearboxes.

According to one embodiment, the adjusting device has one or more hydraulically axially adjustable elements, such as hydraulic rams, which act in the axial direction between the second component and the flange projection. For example, the adjusting device is formed by a plunger ring, which is arranged in a ring around the axis of rotation between the flange projection and the second component. The stamp or stamps can be actuated, for example, via a hydraulic device in order to set the bearing preload force. A bearing preload adjusted by means of such a hydraulic adjusting device can, for example, be locked or fixed mechanically so that the hydraulic adjusting device can be relieved. In other words, the adjusting device can be fixed mechanically.

According to one embodiment, the adjusting device has one or more forcing screws, which can be screwed against the second component in the axial direction by means of threads correspondingly introduced in the flange projection. By screwing the forcing screws against the second component can bridge the above-mentioned gap between the second component and the flange projection and can be increased or decreased depending on the desired prestressing force. When screwed into the flange, the screws literally push themselves off the second component in order to achieve the axial force effect. This represents a cost-effective, mechanically simple and safe solution.

According to one embodiment, the adjusting device is formed by one or more metal inserts that are arranged between the flange projection and the second component. This represents a particularly simple and inexpensive solution.

According to one embodiment, the adjusting device is formed by a nut which can be screwed onto an external thread of the flange projection against the second component. The thread is thus provided on the outer periphery of the flange projection. This is also a mechanically particularly safe and simple solution.

Alternatively, the thread is formed in or on the second component (bearing housing or structural component).

The above-mentioned embodiments for the adjusting device can also be used in combination. For example, the adjusting device could have hydraulically adjustable elements, such as the stamps mentioned, and the forcing screws. This opens up the possibility of setting the preload force purely hydraulically and securing or maintaining the set state by appropriately setting the forcing screws. As soon as the forcing screws have been screwed in accordingly, the hydraulic system can be relaxed again, i.e. the pressure can be reduced.

According to one embodiment, the bearing arrangement has a sensor device that is designed to determine the bearing preload. The bearing preload is measured once, for example, during initial assembly. The measurement can also take place during operation of the bearing arrangement, i.e. during operation of the wind turbine. For example, continuous monitoring takes place, for example at discrete time intervals, during operation. For example, length and/or pressure and/or force values, such as corresponding changes, are measured.

This makes it possible to variably set the optimum bearing preload during operation of the machine/wind energy installation or during operation of the bearing arrangement, depending on the operating and load state. For this purpose, further components, such as a control device for actuating the actuating device and/or one or more sensors for monitoring further operating parameters of the bearing arrangement and/or the wind energy plant, can be provided. These components could be integrated into a machine/plant control system, for example. It is conceivable that, in the course of the continuous monitoring, a warning message or a machine or system stop is triggered if the preload is not within a specified target range, in order to avoid premature damage and failure.

According to one embodiment, the bearing outer ring is connected to the second component by means of a transition or clearance fit in order to simplify the setting of the preload. As mentioned above, an oversize fit is also conceivable, in which case it would then be readjusted "manually" on site. In addition to the flange projection, the bearing outer ring has an outer side with which the bearing outer ring is in contact with the second component. In other words, it is a side that faces away from the axis of rotation and runs parallel to the axis of rotation. In other words, it is a cylindrical section of the bearing outer ring. Due to the transition or clearance fit, a comparatively less tight fit between the bearing outer ring and the bearing housing (in the case of a shaft concept) or to the hollow shaft (in the case of an axle concept) is provided in the design. This facilitates, for example, the assembly and also the adjustability, in particular the subsequent adjustability, of the bearing preload.

According to one embodiment, the second component has an oil groove which extends in the radial direction into a contact area between the second component and the bearing outer ring. As a result, before setting or readjusting the bearing preload, a separating oil film can be generated between the bearing outer ring and the second component by means of oil pressure via the oil groove, in particular so that the components do not seize when setting or readjusting the bearing preload, especially in the case of a transition or interference fit. The setting or readjustment of the bearing preload then takes place by means of the adjusting device, for example taking into account the actual preload to be measured simultaneously. For example, the oil pressure is released again after the adjustment has been completed and the adjusting device has been possibly fixed. When selecting the oil for assembly, attention should be paid to compatibility with the bearing lubricant for operation.

According to one embodiment, the bearing outer ring is form-fitting with the second component connected, so that the bearing outer ring is coupled against rotation with the second component. This reliably prevents the bearing outer ring from turning. In particular, this allows readjustment without complete disassembly when realizing a bearing seat that is not as tight as described above. The form fit can be implemented with one or more feather keys, for example. Other positive locking solutions are also conceivable.

According to one embodiment, the bearing inner ring is secured axially on the first component via a support ring. This is a particularly cost-effective solution.

According to one embodiment, the bearing arrangement has a further roller bearing with a further bearing inner ring and a further bearing outer ring. The roller bearing described above and the other roller bearing form a bearing package. The bearing assembly is correspondingly fixed to the components as described above, in particular secured axially. The flange projection is only provided on one bearing outer ring of the bearing assembly, as described above, via which the bearing play for the entire bearing assembly can be adjusted by means of the adjusting device. With this solution, the above advantages and functions result analogously, with a simple and safe setting and readjustment of the bearing preload for the entire bearing package being ensured.

According to one embodiment, the roller bearing and/or the second roller bearing is an angular ball bearing or a tapered roller bearing, in particular the roller bodies of the two roller bearings are set against one another in an O arrangement. Especially with an O-arrangement of two tapered roller bearings, the above advantages and functions result to a particular extent.

According to a second aspect, a wind turbine is disclosed which has a bearing arrangement according to one of the above embodiments.

The wind energy installation essentially enables the aforementioned advantages and functions.

Further advantages, features and developments result from the following exemplary embodiment explained in connection with the figures.

• 1 eine schematische Darstellung einer Windenergieanlage, und
• 2 eine Schnittdarstellung einer Lageranordnung gemäß einem Ausführungsbeispiel der Erfindung.

In the figures show:

• 1 a schematic representation of a wind turbine, and
• 2 a sectional view of a bearing assembly according to an embodiment of the invention.

1 shows a schematic representation of a wind power plant 100. The wind power plant 100 has a tower 102. FIG. The tower 102 is attached to a base by means of a foundation 104 . A gondola 106 is rotatably mounted on an end of the tower 102 opposite the ground. The nacelle 106 has, for example, a generator which is coupled to a rotor 108 via a drive train (not shown), the drive train comprising, for example, a rotor shaft, a gearbox, a clutch, a rotor brake and other components. The rotor 108 includes one or more rotor blades 110 disposed on a rotor hub 112 .

During operation, the rotor 108 is set in rotation by an air flow, for example wind. This rotational movement is transmitted to the generator via the drive train. The generator converts the kinetic energy of the rotor 108 into electrical energy.

2 shows a sectional view of a bearing assembly 114 according to an embodiment of the invention. In 2 the upper half of the bearing assembly 114 is shown relative to an axis of rotation 116 . The bearing arrangement 114 is provided for the storage of the rotor 108 . Alternatively or additionally, the bearing arrangement 114 can also be used in other applications in the wind energy installation 100 for bearing a rotating component.

The bearing arrangement 114 includes a first component 118 which, in the exemplary embodiment, is a rotatable shaft which can rotate about the axis of rotation 116 . The shaft 118 has an axial end 120 (in 2 right), from which a shaft section 122 extends to a shaft shoulder 124. In the example, the shaft section 122 is formed cylindrically with a constant diameter.

The bearing arrangement 114 has a first roller bearing 126 and a second roller bearing 128 . The first roller bearing 126 has a first bearing inner ring 130 , a first bearing outer ring 132 and first rolling elements 134 . Analogously, the second roller bearing 128 has a second inner bearing ring 136 , a second outer bearing ring 138 and second rolling elements 140 . The two roller bearings 126, 128 form a bearing assembly, with the roller bodies 134, 140 being designed as tapered rollers which are set against one another in an O arrangement. It is therefore a tapered roller bearing in an O arrangement.

The bearing inner rings 130, 136 of the two roller bearings 126, 128 are each pushed onto the shaft 118, forming an interference fit, and fixed thereto. The second roller bearing 128 is pushed with the second bearing inner ring 136 against the shaft shoulder 124 and is thereby fixed axially.

The bearing outer rings 132, 138 are attached to a second component 142. The second component 142 is a bearing housing which is arranged in a stationary manner. That is, the shaft 118 rotates relative to the bearing housing 142. The bearing housing 142 surrounds the two roller bearings 126, 128, i.e. the bearing cups 132, 138, and has an inwardly projecting portion 144 on. The second bearing outer ring 138 is supported on the section 144 protruding inwards. In the example, the second outer bearing ring 138 is fixed to the bearing housing 142 by means of a transition fit or interference fit.

The first bearing outer ring 132 is fixed to the bearing housing 142 by means of a transition or clearance fit. In the example, the first bearing outer ring 132 has a cylindrical section 146 for this purpose, the outer side 148 of which facing away from the axis of rotation 116 is in contact with the bearing housing 142 .

The first bearing inner ring 130 is secured axially on the shaft 118 via a support ring 149 .

A clearance 152 is provided between a first axial end 150 of the first bearing cup 132 facing the inwardly projecting portion 144 and the inwardly projecting portion 144 . The distance can also be designed as a small gap.

In addition, the first outer bearing ring 132 has a flange projection 154 which extends radially away from the axis of rotation 116 and is formed on the second axial end of the first outer bearing ring 132 in the example. A gap 156 is formed between the flange projection 154 and the bearing housing 142 . The flanged projection 154 is an integral part of the first bearing cup 132, i.e. it is molded in one piece therefrom. The first bearing outer ring 132 and thus the flange projection 154 are forged, for example. The flange projection 154 is thus provided on one of the two roller bearings 126, 128.

To bridge this gap 156 and to set the bearing preload, an adjusting device 158 is provided between the flange projection 154 and the second component. The flange projection 154 thus serves to accommodate the adjusting device 158.

The adjusting device 158 is indicated schematically and is designed as a hydraulic device in the example. In the example, the hydraulic adjusting device 158 is designed as a ring with one or more hydraulic rams, which act in the axial direction with respect to the axis of rotation 116, i.e. can be moved. The adjusting device 158 is designed to brace the flange projection 154 against the second component 142 in the axial direction and thus to adjust the bearing preload or the bearing play. There is a clamping force F.

As a result, the advantages and functions mentioned at the outset can be achieved. In particular, it is possible to adjust the bearing play in the bearing arrangement 114 according to the exemplary embodiment not only during initial assembly, but also after the system has been put into operation, i.e. when the system is at a standstill as well as during operation, e.g. when the wind turbine is spinning.

Optionally, a form fit between the first bearing outer ring 132 and the bearing housing 142 is provided. In the example, the first bearing outer ring 132 and the bearing housing 142 have corresponding grooves into which a feather key 160 (indicated by dashed lines) is inserted. This prevents the first bearing outer ring 132 from rotating, in particular when the bearing arrangement 114 is in operation when the shaft 118 is rotating. Of course, several such keys can be provided.

A radially running oil groove 162 is optionally provided, via which an oil film under oil pressure P can be introduced into the contact area between bearing housing 142 and first bearing outer ring 132 .

The embodiments and developments mentioned at the outset can be applied to the exemplary embodiment described. For example, a sensor device can be provided to monitor the bearing preload, such as the clamping force F. Depending on this monitoring, the force F can be set and changed as a function of the operation by actuating the actuating device 158 . The adjusting device 158 can, for example, have additional means such as the forcing screws mentioned and/or hydraulic rams.

As mentioned above, combinations are also conceivable, such as adjusting the bearing preload with one or more hydraulic rams and then fixing the Components by means of jacking screws which are screwed axially against the second component 142 through threads in the flange boss 154 .

Furthermore, it should be mentioned that the exemplary embodiment described is not limited to the special bearing details and arrangement, which relate, for example, to the shaft design or the design of the bearing housing. The provision of a flange projection on at least one bearing outer ring is essential.

Reference List

100

wind turbine

102

Tower

104

foundation

106

gondola

108

rotor

110

rotor blade

112

rotor hub

114

bearing arrangement

116

axis of rotation

118

first component

120

axial end

122

wave section

124

wave heel

126

first rolling bearing

128

second roller bearing

130

first bearing inner ring

132

first bearing outer ring

134

first rolling element

136

second bearing inner ring

138

second bearing outer ring

140

second rolling elements

142

second component

144

inward protruding section

146

cylindrical section

148

outside

149

support ring

150

first axial end

152

Distance

154

flange protrusion

156

gap

158

actuator

160

Adjusting spring

162

oil groove

f

clamping force

P

oil pressure

Claims (15)

Bearing arrangement (114) for a rotating component of a wind turbine (100), comprising a roller bearing (126) with a bearing inner ring (130) and a bearing outer ring (132), wherein the bearing inner ring (130) is coupled to a first component (118), the bearing outer ring (132) is coupled to a second component (142), rolling elements (134) are arranged between the inner and outer bearing rings (130, 132), the first component (118) and the second component (142) can be rotated relative to one another with respect to an axis of rotation (116) of the bearing arrangement (114), the bearing outer ring (132) has a flanged projection (154) extending in a radial direction with respect to the axis of rotation (116), and An adjusting device (158) is arranged between the flange projection (154) and the second component (142), which is designed to set a bearing preload force or a bearing play in the axial direction with respect to the axis of rotation (116). Bearing arrangement (114) after claim 1 , wherein the flange projection (154) is an integral part of the bearing outer ring (132). A bearing assembly (114) as claimed in any preceding claim, wherein the flange boss (154) and/or the bearing cup (132) are forged or machined from solid stock. Bearing arrangement (114) according to one of the preceding claims, wherein the adjusting device (158) has one or more hydraulically axially adjustable elements, such as hydraulic rams, which act in the axial direction between the second component (142) and the flange projection (154). Bearing arrangement (114) according to one of the preceding claims, wherein the adjusting device (158) is formed by a nut which can be screwed onto an external thread of the flange projection (154) against the second component (142). A bearing assembly (114) according to any one of the preceding claims, wherein the adjusting device (158) comprises one or more jacking screws which pass through a corresponding one in the flange boss (154) introduced threads can be screwed in the axial direction against the second component (142). Bearing arrangement (114) according to one of the preceding claims, wherein the adjusting device (158) is formed by one or more insert plates which are arranged between the flange projection (154) and the second component (142). Bearing arrangement (114) according to one of the preceding claims, wherein the bearing arrangement (114) has a sensor device which is designed to determine the bearing preload. Bearing arrangement (114) according to one of the preceding claims, wherein the bearing outer ring (132) is connected to the second component (142) by means of a interference or clearance fit. Bearing arrangement (114) according to one of the preceding claims, wherein the second component (142) has an oil groove (162) which extends in the radial direction into a contact area (146, 148) between the second component (142) and the bearing outer ring (132). . Bearing arrangement (114) according to one of the preceding claims, wherein the bearing outer ring (132) is positively connected to the second component (142), so that the bearing outer ring (132) is coupled to the second component (142) in a torsion-proof manner. Bearing arrangement (114) according to one of the preceding claims, wherein the bearing inner ring (130) is secured axially on the first component (118) via a support ring (149). Bearing arrangement (114) according to one of the preceding claims, wherein the bearing arrangement (114) has a further roller bearing (128) with a further bearing inner ring (136) and a further bearing outer ring (138). Bearing arrangement (114) according to one of the preceding claims, wherein the roller bearing (126) and/or the second roller bearing (128) is a tapered roller bearing or an angular contact ball bearing, in particular the roller bodies (134, 140) of the two roller bearings (126, 128) are in employed against each other in an O-arrangement. Wind power plant (100), having a bearing arrangement (114) according to one of Claims 1 until 14 .

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