DE102019003330A1 - Rolling bearing arrangement, in particular for a wind turbine - Google Patents

Abstract

The application relates to a roller bearing arrangement with a first ring and a second ring, which is mounted rotatably about an axis of rotation relative to the first ring. The first ring and the second ring partially overlap axially, so that one of the rings forms an outer ring and the other ring forms an inner ring. The second ring has an end connection surface for connection to a first machine part. Furthermore, the roller bearing arrangement preferably has a first row of roller bodies and a second row of roller bodies, the second row being arranged axially at a distance from the first row; the rolling elements of the two rows are arranged rolling between the first ring and the second ring. On its side facing the second ring, the first ring has an annular collar with a circular cylindrical jacket surface and two circular ring-shaped end faces, with a raceway for the first and second row of rolling elements being formed on each of the end faces. Furthermore, the roller bearing arrangement has an additional ring that is non-rotatably connected to the first ring, extends around the axis of rotation and axially at least partially aligned with the first ring, a bearing gap being formed between the first ring and the additional ring connected to it on the one hand and the second ring on the other, so that the additional ring delimits a portion of the bearing gap. The additional ring has a section that protrudes axially beyond the second ring, the protruding section of the additional ring having an end connection surface of the additional ring for a second machine part, which protrudes radially at least partially beyond the second ring.

Description

The present application relates to a roller bearing arrangement, in particular for a wind turbine.

Technical background

With the increasing use of alternative energies, the size of the wind turbines used for this purpose has also increased. This means that the stresses on the supporting and bearing units of such wind turbines have also grown.

A wind turbine typically comprises a tower, at the upper end of which a machine house is arranged. In the machine house, a rotor is rotatably mounted about a horizontal axis with the help of a so-called main bearing. Rotor blades, for example three rotor blades, are mounted on a hub of the rotor, each via a blade bearing. The blade bearing enables the rotor blade to rotate about its longitudinal axis. The nacelle can be pivoted about a vertical axis via a so-called tower bearing, so the direction of the rotor's axis of rotation can be aligned with the wind.

With the help of the blade bearing, the angle of attack of the rotor blade can thus be adapted to different wind conditions. Tilting moments typically occur here as the greatest load, which transfer the wind load concentrated in the center of the wind pressure to the blade bearing. With regard to such a tilting moment, the blade bearing represents a pivot, and due to the considerable lever arm, the wind load results in a very high bending stress on the blade root and the blade bearing.

In the case of a main bearing of a wind power plant, the bending moments that are transmitted from the individual rotor blades to the hub are generally less dominant, since these bending moments usually at least partially compensate each other. In addition, the rotor and thus the main bearing of a wind power plant usually rotate during the introduction of torques, so that the rolling elements of the main bearing are in motion and thus practically no local permanent loads occur.

State of the art

From the WO 2006/131301 A2 a bearing unit for a rotor blade of a wind turbine is known. The bearing unit has an inner ring and an outer ring which is mounted rotatably about an axis of rotation relative to the inner ring. Three rows of roller-shaped rolling elements are arranged between the inner ring and the outer ring. Two of the three rows are arranged axially spaced apart, the axes of rotation of the rolling elements of these two rows being oriented perpendicular to the axis of rotation. They are therefore primarily used to absorb axially acting forces and tilting moments. The third row of roller-shaped rolling elements is arranged axially between these two rows, their axes of rotation being oriented parallel to the axis of rotation, so that they are primarily used to absorb radially acting forces. The rolling elements in the third row are smaller than the rolling elements in the other two rows. This is advantageous in the case of a bearing on which tilting moments act primarily because the latter can primarily be suitably absorbed by the two rows of rolling elements mentioned first. The outer ring (inner ring) has on its inner side (outer side) an annular collar that extends all around and bulges radially inward (outward) with an inner-cylindrical (outer-cylindrical) surface and two adjoining, circular end faces. Raceways for the rolling elements of the two first-mentioned rows are formed on the two end faces and a raceway for the third row of rolling elements is formed on the outer surface.

The inner ring also has a connection surface formed normal to the axis of rotation for connection to a rotor blade, and the outer ring has a connection surface, likewise formed normal to the axis of rotation, for connection to a rotor hub. Alternatively, the connection surface of the inner ring can be provided for connection to a rotor hub and the connection surface of the outer ring for connection to a rotor blade. For connection to the rotor blade or the rotor hub, fastening bores are each formed in a ring on the inner ring and the outer ring.

The bearing gap formed between the inner ring and the outer ring opens into an outer area of the bearing unit via two axially opposite circular outlet openings. Two annular sealing elements serve to seal the bearing gap.

The bearing unit is particularly suitable as a rotor blade bearing for wind turbines, since it can meet the special requirements for such components, in particular the particularly large tilting moment under strong wind loads, and can withstand the relatively difficult load situation. The rotor blade bearing has a long service life.

When the rotor blade is stationary in relation to the blade bearing, aerodynamic suction and pressure forces act when the rotor blade sweeps past the tower, which results in a significant overturning moment load lead the blade bearing. In this way, the lubricating film located between the rolling elements and the raceways can be displaced and, as a result, the raceways can degenerate. Therefore, for the operation of the rotor blade bearing, it is very often provided that the rotor blade is continuously pivoted back and forth through small angles. In this way, the lubricating film between the rolling elements and the running surfaces can continuously regenerate, which prevents dry running and reduces wear.

Since the outer ring (inner ring) has the inwardly (outwardly) oriented annular collar, the two circular exit openings of the bearing gap are, viewed radially, closer to the through openings of the outer ring (inner ring) than to the through openings of the inner ring (outer ring). As a result, the sealing element located on the side of the rotor hub is located radially close to the rotor hub (or the sealing element located on the side of the rotor blade is located radially close to the blade bolt).

In order to nevertheless be able to design the connection surface of the outer ring or inner ring, which is used for connection to the rotor hub, to be suitably large, the outer ring or inner ring is designed with a relatively large radial extension. In addition, this radial extension is selected to be comparatively large, because in this way suitable accessibility to the sealing element located there can be achieved. In this way, the sealing element can be serviced or replaced without the bearing arrangement having to be separated from the rotor hub for this purpose, which, for example, in the case of a blade bearing of a typical wind turbine, would only be possible with disproportionately high effort.

For these reasons, too, the prior art provides that the ring in question extends relatively far in the radial direction. As a result, the storage unit has a correspondingly large mass. This is fundamentally disadvantageous in terms of material consumption and weight. Subsequently, this also has a disadvantageous effect on the dimensioning of the rotor hub, since it must have a correspondingly large diameter. In addition, the comparatively large radial extension of the ring in question also has a disadvantageous effect on the raceway system of the three rows of rolling elements, since the lever ratios become more unfavorable as the radial distance between the forces acting on the bearing unit and the position of the rolling elements increases.

The problem mentioned does not only arise in the case of blade bearings, but also in other bearings in which the bearing gap, viewed radially, does not open out in the middle of two corresponding hole circles of the inner ring on the one hand and outer ring on the other hand, but off-center, i.e. either closer to the bolt circle of the Outer ring or closer to the bolt circle of the inner ring. For example, corresponding three-row bearings are also used as main bearings or tower bearings in wind turbines.

task

The aim of the arrangement disclosed here is to specify an improved rolling element arrangement, the rolling element arrangement being able to be made smaller and lighter, particularly with advantageous bearing properties.

solution

This object is achieved with a rolling element arrangement according to independent claim 1. Preferred refinements are given in the dependent claims.

A roller bearing arrangement, in particular for a wind power plant, has a first ring and a second ring which is mounted so as to be rotatable about an axis of rotation relative to the first ring. The first ring and the second ring partially overlap axially, so that the first ring forms an inner ring and the second ring forms an outer ring or the first ring forms an outer ring and the second ring forms an inner ring. In the first case, the first ring as the inner ring has a smaller diameter than the second ring as the outer ring. In the second case, the first ring as the outer ring has a larger diameter than the second ring as the inner ring.

The second ring has an end connection surface for connection to a first machine part.

The rolling element arrangement furthermore comprises an additional ring which is connected non-rotatably to the first ring, extends around the axis of rotation and axially at least partially aligned with the first ring. The additional ring has a section protruding by an axial projection over the second ring. A bearing gap is formed between the first ring and the additional ring connected to it, on the one hand, and the second ring, on the other hand, so that the additional ring delimits a section of the bearing gap, the protruding section of the additional ring being an end face of the additional ring which radially at least partially protrudes beyond the second ring for a second machine part.

This design allows the execution of the raceway system to be separated from the connection surface of the additional ring, so that the connection surface of the additional ring can be designed practically independently of the space requirement of the raceway system.

In particular, it can be achieved that - with a small radial extension of the first ring - the connection surface of the additional ring extends radially so far that it has a suitable size for connection to the second machine part.

In addition, because the additional ring extends axially over the second ring, the roller bearing arrangement can be designed in such a way that suitable accessibility, for example for replacement or maintenance of a sealing arrangement acting between the additional ring and the second ring, is ensured even when the Rolling bearing arrangement is installed in a device, for example a wind turbine, so the additional ring and the second ring are connected to machine parts as intended. For this purpose, the second ring preferably has a planar delimiting surface on its side axially opposite the connection surface of the second ring, which is adjoined by a corresponding free space.

Overall, in comparison to the prior art mentioned at the beginning, the first ring can be designed with a reduced radial extent, so that the roller bearing arrangement can be designed to be smaller overall. In this way, material can be saved and the weight of the roller bearing arrangement can be reduced.

Particularly suitable conditions can be achieved if the connection surface of the additional ring on its side facing closer to the second ring has a circular boundary line that is symmetrical in particular to the axis of rotation, the additional ring delimiting the section of the bearing gap with an in particular cylindrical outer surface area, with between the boundary line and the outer surface area a radial projection a is formed, the following applies to the ratio between the radial projection a and the axial projection h: 1/10 ≤ a / h 5 3/1, preferably 1/5 a / h 2/1.

The annular radial delimitation line can in particular extend symmetrically around the axis of rotation; on the other hand, the connection surface of the additional ring can be delimited by a further circular delimitation line, which preferably also extends symmetrically around the axis of rotation. If you look at the connection surface of the additional ring in the direction of the axis of rotation, it describes a circular ring shape. If the connection surface of the additional ring were formed without the radial protrusion a and would only extend radially as far as the outer surface area of the additional ring delimiting the section of the bearing gap, it would be smaller by an annular surface with the radial extension a. A corresponding enlargement of the connection surface of the additional ring can therefore be brought about by the radial projection a.

For the ratio between the radial protrusion a and the axial protrusion h, for example 0.4 ≤ a / h, 1.1, in particular 0.4 a / h 0.6, so that the protruding section of the additional ring on its side facing the second ring can extend outwards approximately at an inclination of about 30 ° relative to the axis of rotation. Alternatively, 0.9 a / h 1.1 can be provided, for example, so that the protruding area can extend outward at approximately an inclination of 45 ° relative to the axis of rotation.

The connection surface of the second ring preferably has a radial width B, the following applies to the ratio between the radial projection a and the radial width B: 1/20 a / B 1/2.

The radial width B 'of the connection surface of the additional ring can be approximately as large as the radial width B of the connection surface of the second ring. For example, the following can apply to the ratio B '/ B: 3/2 B' / B 2/3, preferably 4/3 B '/ B 3/4, particularly preferably 5/4 B' / B 4/5.

For example, it can be provided that the following applies to the axial projection h compared to the axial extension H of the second ring: 1/20 h / H 1/2.

The additional ring preferably has a first protruding area on its side facing the second ring to form the connection surface of the additional ring. In this way, suitable stability of the connection surface of the additional ring can be achieved with little material consumption, in particular if the first protruding area has a frustoconical boundary surface formed symmetrically about the axis of rotation with a cone angle that is smaller than 50 °, preferably smaller than 45 °. In particular, the first protruding area can be formed on the protruding section of the additional ring.

Furthermore, the additional ring preferably has on its side facing away from the second ring to form the connection surface of the additional ring, a second cantilevered area, which preferably has a frustoconical boundary surface formed symmetrically about the axis of rotation Has cone angle which is smaller than 70 °, preferably smaller than 50 °. So can. cause an even further increase in the size of the connection surface. The second cantilevered area can be designed to encompass the first section and the second section.

Furthermore, the rolling element arrangement preferably has a first row of rolling elements and a second row of rolling elements, the second row being axially spaced from the first row. The rolling elements of the first row and the second row are arranged rolling between the first ring and the second ring. On its side facing the second ring, the first ring has an annular collar with a circular cylinder-shaped jacket surface and two circular ring-shaped end faces, with a raceway for the first and second row of rolling elements being formed on each of the end faces.

As a result of the fact that - compared to the prior art mentioned at the beginning - the connecting surface extends further radially, it can subsequently also be achieved that the axially acting forces which are transmitted to the raceway system by the second machine part connected to the connecting surface are radially viewed closer to the rolling elements of the first and second row. In this way, axially transmitted forces from the second machine part can be absorbed more effectively by the bearing system.

The second ring preferably has a first section and a second section, a raceway for the first row of rolling elements being formed on the first section and a raceway for the second row of rolling elements being formed on the second section. This provides an advantageous option for mounting the roller bearing arrangement.

The additional ring is preferably formed in one piece.

The connection surface for the second machine part formed on the protruding section of the additional ring can, for example, be planar and oriented normal to the axis of rotation. Alternatively, it can be designed, for example, symmetrically about the axis of rotation in the shape of a truncated cone, in particular a flat truncated cone, that is to say with a relatively large cone angle of for example more than 80 °. The same applies to the connection surface of the outer ring. The machine parts that are connected non-rotatably to the additional ring or to the second ring can be, for example, a rotor hub or a housing or a rotor blade of a wind power plant.

According to a preferred embodiment, the additional ring has fastening bores arranged in a ring around the axis of rotation for fastening the second machine part to the connection surface of the additional ring. The second ring preferably has fastening bores arranged in a ring around the axis of rotation for fastening the first machine part to the connection surface of the second ring, the fastening bores of the additional ring and the fastening bores of the second ring being radially opposite one another with respect to the first row of rolling elements. In this way, a suitable connection to the other machine parts can be achieved, for example with the aid of bolts, threaded bolts or screws that are guided into the fastening bores or through the fastening bores. The fastening bores can, for example, be through bores or blind bores.

Furthermore, the first ring preferably has fastening bores arranged in a ring around the axis of rotation for the rotationally fixed connection to the additional ring. For this purpose, the fastening bores of the inner ring are preferably aligned with the fastening bores of the additional ring. In this way, the additional ring can easily be connected to the first ring in a rotationally fixed manner.

The additional ring is preferably connected directly to the inner ring. For example, for this purpose the additional ring can have a delimiting surface oriented normal to the axis of rotation, which makes flat contact with a delimiting surface of the first ring that is likewise oriented normal to the axis of rotation.

In one variant, the additional ring, the first ring and the second ring have no bores and the connection to the relevant machine parts is provided otherwise, for example in the form of a welded connection or a joint connection.

The first and the second row of rolling elements can be designed to be axially aligned. In other words, the first row of rolling elements can at least partially cover the axial projection of the second row of rolling elements. The rolling elements of the first row and the rolling elements of the second row can be arranged in an essentially cylindrical shape and in such a way that their axes of rotation are oriented essentially perpendicular to the axis of rotation. With this design it can be achieved that the first row of rolling elements can absorb forces acting axially in a first direction and the second row of rolling elements can absorb forces that are also axially but directed opposite to the first-mentioned direction. The design is therefore suitable for absorbing a tilting moment, because such a tilting moment can be caused by part of the Rolling bodies of the first row and part of the rolling bodies of the second row are received, the two parts mentioned being opposite one another with respect to the axis of rotation.

The rolling elements in the first row do not have to be cylindrical. For example, they can alternatively have a cone shape, a needle shape or a barrel shape. In principle, they can also be spherical. If the rolling elements are not spherical but roller-shaped, the corresponding raceway is less stressed, since in this case line-like contact surfaces with the raceways result.

For example, it can be provided that the axes of rotation of the rolling bodies of the first row enclose an angle with a plane normal to the axis of rotation which is smaller than 45 °, preferably smaller than 25 °, particularly preferably smaller than 10 °. The same applies to the design of the second row. If the axes of rotation are tilted accordingly, the design can furthermore be such that the rolling elements in the first row and the rolling elements in the second row are tilted in opposite directions with respect to the plane oriented normal to the axis of rotation.

The rolling elements of the first row and the second row can be made the same size. They can also have the same shape.

Furthermore, the rolling element arrangement can have a third row of rolling elements arranged axially between the first row and the second row. The rolling bodies of the third row can also be essentially cylindrical, their axes of rotation being oriented essentially parallel to the axis of rotation. In this way, radial forces can be absorbed with the third row. It can be provided that the rolling elements of the third row are smaller than the rolling elements of the first and second row. This can be advantageous if the forces acting radially on the bearing are smaller than the forces acting axially, as is the case, for example, with a blade bearing.

The rolling elements in the third row do not necessarily have to be cylindrical either. They can also alternatively have a conical shape, a needle shape or a barrel shape or a spherical shape, with a roll shape being preferred over a spherical shape for the reasons mentioned above.

In one variant, the rolling elements of the three rows are kept at a mutual distance by spacers or cages.

It is also possible to provide a plain bearing instead of the third row of rolling elements, in particular when the radial forces are particularly low. To this end, the first ring can have a corresponding cylindrical sliding surface which interacts with a corresponding inner cylindrical sliding surface of the second ring.

In principle, it is also possible that no further bearing point is provided between the first row of rolling elements and the second row of rolling elements.

In a variant, the two end faces of the annular collar extend equally far in the radial direction. The radial extension of the end faces can be matched to the radial extension of the rolling bodies of the first or second row. For example, the rolling elements of the first and the second row have the same radial extent, the radial extent of the end faces being as large as or insignificantly larger than the radial extent of the rolling elements. An overall space-saving design is thus possible.

If the roller bearing arrangement has the third row of roller bodies, a raceway for the roller bodies of this third row can be formed on the cylindrical outer surface of the annular collar.

Furthermore, the second ring can have a recess on its side facing the first ring, into which the annular collar of the first ring and the rolling elements engage. Three raceways for the three rows of rolling elements are formed on the recess. This is also advantageous for a space-saving design. As mentioned, the first ring can have raceways for the three rows of rolling elements on its annular collar.

The bearing gap can be provided or filled with a lubricant, for example with lubricating grease or lubricating oil.

According to one embodiment, the roller bearing arrangement furthermore has a sealing arrangement for sealing the section of the bearing gap which extends between the additional ring and the second ring. The axially protruding section of the additional ring ensures suitable accessibility to the sealing arrangement, especially when the additional ring is connected to the second machine part as intended. This is advantageous because the sealing arrangement can be exchanged or serviced without the roller bearing arrangement having to be separated from a connected machine part. A sealing contact surface for the sealing arrangement is preferably on the additional ring educated. Alternatively, a seal contact surface for the seal arrangement is formed on the second ring.

The additional ring is preferably made of a different material than the first ring and / or the second ring. Since no raceway surfaces have to be formed on the additional ring, the requirements for the material for the additional ring are lower than the requirements for the material of the first or second ring. The latter can for example consist of roller bearing steel. The additional ring can therefore consist of a different material, in particular of a cheaper material, than the first ring, for example of a less tempered steel. More generally, the additional ring can consist of aluminum, structural steel, steel or cast iron. This can reduce costs. Compared with the case in which the additional ring is made of the same material as the first ring, a weight saving can also be achieved with the appropriate choice of material.

The effects shown here are particularly relevant when the roller bearing arrangement exceeds a certain size, in particular when the first ring and / or the second ring has a diameter of more than 1000 mm. For example, the roller bearing arrangement can be a blade bearing for a wind turbine.

Embodiments

Figure list

Further features, properties, advantages and possible modifications will become clear to a person skilled in the art on the basis of the description below, in which reference is made to the accompanying drawings.

• 1 eine Schnittdarstellung zu einem ersten Ausführungsbeispiel einer anmeldungsgemäßen Wälzlageranordnung, und
• 2 eine Schnittdarstellung zu einem zweiten Ausführungsbeispiel einer anmeldungsgemäßen Wälzlageranordnung.

Show it

• 1 a sectional view of a first embodiment of a roller bearing arrangement according to the application, and
• 2 a sectional view of a second embodiment of a rolling bearing arrangement according to the application.

The attached drawings, the technical content and the detailed description relate to preferred embodiments, which, however, should not be interpreted as a restriction of the subject matter of the application. All equivalent variations and changes made in accordance with the appended claims of the present application are covered by these claims.

1 shows a partial sectional view of a first embodiment of a roller bearing arrangement. The roller bearing arrangement comprises a first ring 110 , which here forms an inner ring of the roller bearing assembly and a second ring 120 , which forms an outer ring, the second ring 120 rotatable about an axis of rotation D relative to the first ring 110 is stored. The section of the illustration is laid through the axis of rotation D, the illustration only showing the relationships on one side of the axis of rotation D. On the opposite side, the overall ring-shaped design results in mirror-symmetrical relationships.

In the variant shown here are between the first ring 110 and the second ring 120 a first row 131 of rolling elements, a second row 132 of rolling elements and a third row 133 formed by rolling elements, the rolling elements of the three rows 131 , 132 , 133 are arranged such that they are between the first ring 110 and the second ring 120 can roll off. The variant shown here can be varied in such a way that, for example, the second and / or the third row of rolling elements can be omitted.

The first row 131 of rolling elements and the second row 132 of rolling elements are axially spaced from one another. In the variant shown here, the first row overlap 131 and the second row 132 move radially so that the first row 131 of rolling elements in the axial projection of the second row 132 intervenes or covers the latter. In the variant shown here, the first row extends 131 and the second row 132 the same distance in the radial direction. The first row 131 and the second row 132 are designed identically here.

The first ring 110 points to his, the second ring 120 facing side, here an annular collar on its radially outwardly facing side 115 on, which has a circular cylindrical surface 116 and two circular end faces 117 includes. The end faces 117 lie with respect to the lateral surface 116 across from. Here are the two end faces 117 symmetrically designed. On a first of the two end faces 117 is a front row career 131 formed by rolling elements and on the opposite end face 117 a career for the second row 132 of rolling elements. On the outer surface 116 of the ring collar 115 is a third tier career track 133 formed by rolling elements.

The rolling elements of the three rows 131 , 132 , 133 are essentially cylindrical in the example shown. This is also intended to denote bodies of revolution that are not cylindrical in the mathematical sense, but each have a lateral surface as well two of them, for example, each have an edge or a region with a reduced radius of curvature, end face surfaces, that is to say for example cylinder, cone, needle or barrel shapes.

The first row of rolling elements 131 and the second row 132 are arranged here in such a way that their axes of rotation are oriented essentially perpendicular to the axis of rotation D. The third row rolling elements 133 are arranged in such a way that their axes of rotation are oriented parallel to the axis of rotation D.

The first row of rolling elements 131 and the second row 132 are the same size in the example shown, while the rolling elements of the third row 133 are smaller. As a result, the rolling element arrangement is particularly suitable for absorbing tilting moments.

The first ring 110 furthermore has a frontal boundary surface 118 which is designed flat and is oriented normal to the axis of rotation D. The first ring has on the axially opposite side 110 another frontal boundary surface 119 on, which is preferably also designed flat and is oriented normal to the axis of rotation D. The ring collar 115 is preferably viewed axially in a central area between the boundary surface 118 and the further boundary surface 119 formed, but closer to the boundary surface 118 than on the wider boundary surface 119 .

The first ring 110 has mounting holes 113 on, of which in 1 one is shown. The mounting holes 113 extend in the shape of a ring and, in the variant shown, symmetrically with respect to the axis of rotation D and are designed here oriented parallel to the axis of rotation D.

Furthermore, the first ring 110 on his, the second ring 120 facing away, here a toothing on its radially inwardly facing side 111 have by which a driving force on the first ring 110 can be transferred.

The second ring 120 has an end connection surface 121 for a permanent connection with a first machine part, for example a rotor hub of a wind turbine. The connection surface 121 of the second ring 120 is designed here flat and oriented normal to the axis of rotation D. The second ring 120 is designed in such a way that it is on the side of the connection surface 121 axially the first ring 110 towers above, for example by an axial projection h '.

The second ring is used to connect the first machine part 120 Mounting holes 123 on, of which in 1 one is shown. The mounting holes 123 extend in the shape of a ring and preferably symmetrically with respect to the axis of rotation D and are designed here to be oriented parallel to the axis of rotation D. The mounting holes 123 open in the example shown at the connection surface 121 of the second ring 120 .

On his, the connection surface 121 axially opposite side has the second ring 120 here a likewise planar end-face boundary surface oriented normal to the axis of rotation D. 127 on.

The axial extension H of the outer ring 120 thus corresponds to the axial distance between the connection surface 121 and the boundary surface 127 . The axial extent of the first ring 110 is smaller than the axial extension H of the second ring 120 . Here is the second ring 120 axially on both sides over the first ring 110 above.

The second ring 120 is designed in two parts, making it a first section 128 and a second section 129 comprises, on the first section 128 the boundary surface 127 is formed and on the second section 129 the connection surface 121 . The two sections mentioned 128 , 129 are aligned axially, the (imaginary) parting plane being formed in an axially central area.

The two sections 128 , 129 of the second ring 120 can, for example, be non-rotatably connected to one another with screws or bolts that pass through or into the mounting holes 123 are plugged. However, there is also another non-rotatable connection of the two sections 128 , 129 possible.

The second ring 120 points to his, the first ring 110 facing side, so here on its radially inwardly facing side a recess 122 on, being the parting line of the two sections 128 , 129 by the bottom of this recess 122 runs. In the recess 122 grab the three rows 131 , 132 , 133 of rolling elements. This is on the first section 128 of the second ring 120 a career for the front row 131 formed by rolling elements and on the second section 129 a career for the second row 132 of rolling elements and another raceway for the third row 133 formed by rolling elements. As a result of this configuration, the roller bearing arrangement can advantageously be mounted by the second section in a first step 129 of the second ring 120 with the introduction of the rolling elements of the second row 132 and the third row 133 with the first ring 110 is put together and in a further step by introducing the rolling elements of the first row 131 the first section 128 of the second ring 120 is added.

The roller bearing arrangement also has an additional ring 140 on, which extends around the axis of rotation D and which rotatably with the first ring 110 is connected and at least partially axially with the first ring 110 flees. For example, the additional ring 140 a plane boundary surface oriented normal to the axis of rotation D. 147 have, the two-dimensional the boundary surface 118 of the first ring 110 contacted.

Here is between the first ring 110 and the associated additional ring 140 one hand and the second ring 120 on the other hand, a bearing gap 160 formed so that the additional ring has a section 162 of the bearing gap 160 limited, so that portion of the bearing gap 160 between the additional ring 140 and the second ring 120 is formed.

In one variant, the additional ring has 140 Fastening holes arranged in a ring around the axis of rotation D. 143 which are oriented here parallel to the axis of rotation D and which are here axially with the mounting holes 113 of the first ring 110 cursing. Here are the rotationally fixed connection between the additional ring 140 and the first ring 110 Screws or bolts into these mounting holes 143 , 113 intervening arranged.

The fastening bores are located here when viewed radially 143 of the additional ring 140 and the mounting holes 123 of the second ring 120 with respect to the first row 131 of rolling elements opposite.

The additional ring 140 has a first section 141 which extends axially within that region which is from the second ring 120 is taken, as well as a second section 142 , by an axial projection h over the second ring 120 survives. The second section 142 therefore forms a protruding section 142 of the additional ring 140 . In 1 is the parting line through which the two sections mentioned 141 , 142 of the additional ring 140 are separated from each other by a dash-dotted line 444 indicated.

The additional ring 140 , especially its first section 141 delimits the section 162 of the bearing gap 160 in particular with a cylindrical surface area 146 .

The two sections 141 , 142 of the additional ring 140 are preferably connected directly to one another and integrally with one another. In particular, the additional ring 140 consist of one piece or be made integrally. In the example shown, the parting line runs 444 between the first section 141 and the second or protruding section 142 accordingly in that plane oriented normal to the axis of rotation, in which also the frontal boundary surface 127 of the second ring 120 lies.

The protruding section 142 of the additional ring 140 has an end connection surface 144 of the additional ring 140 for a second machine part, this connection surface 144 at least partially the second ring 120 protrudes radially. In other words, the connection surface engages 144 of the additional ring 140 in the axial projection of the second ring 120 one. The fastening bores open for a suitable fastening option for the second machine part 143 of the additional ring 140 especially about the connection surface 144 of the additional ring 140 outward.

The connection surface 144 of the additional ring 140 thus lies axially of the connection surface 121 of the second ring 120 across from.

The connection surface preferably has 144 of the additional ring 140 on her closer to the second ring 120 facing side, here on its radially outer side, a circular boundary line that is symmetrical in particular to the axis of rotation D. 145 on, being between the gauge 145 and the lateral surface area 146 of the additional ring 140 a radial projection a is formed. The lateral surface area 146 of the additional ring 140 preferably extends symmetrically about the axis of rotation D.

Due to the radial projection a, the connection surface 144 of the additional ring 140 make it extra large. The following applies to the ratio between the radial projection a and the axial projection h: 1/10 a / h 3/1, preferably 1/5 a / h 2/1. For example, 0.20 a / h 0.35 can apply.

The annular connection surface in the variant shown 121 of the second ring 120 can have a radial width B, that is to say transverse to the axis of rotation, the following applies to the ratio of the radial projection a to the radial width B: 1/20 a / B 1/2. For example, 0.04 a / B 0.10 can apply.

For the ratio between the axial projection h and the axial extent H of the second ring 120 the following can apply: 1/10 ≤ h / H ≤ 1/2.

The additional ring 140 points to his, the second ring 120 facing side to form the connection surface 144 of the additional ring 140 in particular a first projecting area 180 on, the preferably one, symmetrical around the Axis of rotation D formed frustoconical lateral surface 181 having. The cone angle α of the lateral surface 181 is for example smaller than 50 °, preferably smaller than 45 °, particularly preferably smaller than 20 °.

The section 162 of the bearing gap 160 opens here between the boundary surface 127 of the second ring 120 and the first cantilever area 180 of the additional ring 140 outward.

The additional ring has on the radially opposite side 140 to form the connection surface 144 of the additional ring 140 preferably a second cantilevered area 182 on, in particular one, symmetrically formed about the axis of rotation D frustoconical lateral surface 183 having a cone angle β which is smaller than 70 °, preferably smaller than 50 °. The second cantilevered area 182 can cover both sections 141 , 142 of the additional ring 140 extend away.

In the example shown, the connection surface is 144 of the additional ring 140 oriented flat and normal to the axis of rotation D. Alternatively, it can, for example, have a flat truncated cone shape, the cone angle of the truncated cone shape preferably being greater than 70 °, particularly preferably greater than 80 °.

In the bearing gap 160 a lubricant, for example lubricating grease or lubricating oil, is preferably arranged to reduce wear. To seal the section 162 of the bearing gap 160 the roller bearing arrangement furthermore has a sealing arrangement 170 on, preferably directly between the additional ring 140 one hand and the second ring 120 on the other hand is designed to act. A sealing contact surface of the sealing arrangement can thereby 170 advantageous on the additional ring 140 be educated.

Because the additional ring 140 with its second section 142 over the second ring 120 survives, a suitable accessibility to the sealing arrangement can be 170 ensure, especially if the additional ring 140 is connected as intended to the second machine part. In this way it can be achieved that the sealing arrangement also in the installed state of the roller bearing arrangement 170 suitably exchanged or serviced.

For the radial position of the mouth of the section 162 of the bearing gap 160 can apply that the radial distance R1 between the center lines of the mounting holes 143 of the additional ring 140 and the center of the mouth to the radial distance R2 between the center of the mouth and the center lines of the mounting holes 123 of the second ring 120 behaves as follows: 5/10 R1 / R2 <9/10, preferably 6/10 R1 / R2 8/10.

For sealing the bearing gap 160 on the axially opposite side, i.e. between the boundary surface 119 of the first ring 110 and the second ring 120 near its connection surface 121 is preferably a further sealing arrangement 171 intended.

On the additional ring 140 is preferably no raceway formed for rolling elements. Hence the material requirements for the additional ring 140 lower than the requirements for the material of the first ring 110 and the second ring 120 .

2 shows a corresponding sectional view of a second embodiment. Unless otherwise stated below, the above statements also apply analogously to this second exemplary embodiment. In this example forms a first ring 210 an outer ring and a second ring 220 an inner ring. Some of the reference symbols are used in an analogous manner.

The first ring 210 has mounting holes 213 on and on its radially inwardly facing side an annular collar 215 with a circular cylindrical surface 216 and two circular end faces 217 . For the arrangement of the three rows 131 , 132 , 133 of rolling bodies result in the sectional view accordingly mirror-symmetrical conditions compared to the first embodiment.

The second ring 220 has mounting holes 223 on and an end connection surface 221 on.

There is also an additional ring 240 with mounting holes 243 provided that rotatably with the first ring 210 , here is connected to the outer ring. The additional ring 240 has a first section 241 which extends axially within that region which is from the second ring 220 is taken, as well as immediately following the first section 241 subsequent second or protruding section 242 , which extends axially by an axial projection h over the second ring 220 extends beyond. The second section has the front 242 a pad 244 for a second machine part.

The additional ring 240 delimits a section 162 of the bearing gap 160 between the additional ring 240 and the second ring 220 opens outwards. A sealing arrangement is used here for sealing 270 arranged. A corresponding further sealing arrangement 271 is to seal the axially opposite second mouth of the bearing gap 160 intended.

In the second embodiment, the additional ring 240 a suitable connection surface in a corresponding manner 244 form for the second machine part, which extends radially advantageously far inward. The result can be the first ring 210 , so here the outer ring can be designed with a correspondingly reduced radial extent.

The information on size ratios mentioned above in connection with the first exemplary embodiment apply analogously to the second exemplary embodiment.

The additional ring 240 can be used to form the connection surface 244 on the radially outer side a second protruding area 282 have, which is shown in the drawing by way of example only with a very small radial extent. The frustoconical outer surface of the second protruding area 282 is denoted by 283, the first protruding area with 280 and the frustoconical surface of the first protruding area with 281. Furthermore, the boundary line of the connection surface is corresponding 244 denoted by 245, the surface area of the additional ring 240 at 246, the first section of the second ring 220 with 228 and the second section of the second ring 220 with 229.

The above-described variants of the roller bearing arrangement and their design and operational aspects serve only to provide a better understanding of the structure, the mode of operation and the properties; they do not restrict the disclosure to the exemplary embodiments. The figures are schematic, with essential properties and effects in some cases being shown significantly enlarged in order to clarify the functions, operating principles, technical configurations and features. Any mode of operation, any principle, any technical design and any feature that is / are disclosed in the figures or in the text, with all claims, each feature in the text and in the other figures, other modes of operation, principles, Technical configurations and features contained in this disclosure or resulting therefrom can be freely and arbitrarily combined, so that all conceivable combinations of the described system can be assigned. Combinations between all the individual statements in the text, that is, in each section of the description, in the claims and also combinations between different variants in the text, in the claims and in the figures are also included. The claims also do not limit the disclosure and thus the possible combinations of all the features shown with one another. All the features disclosed are explicitly disclosed here also individually and in combination with all other features.

QUOTES INCLUDED IN THE DESCRIPTION

This list of the documents listed by the applicant was generated automatically and is included solely for the better information of the reader. The list is not part of the German patent or utility model application. The DPMA assumes no liability for any errors or omissions.

Patent literature cited

• WO 2006/131301 A2 [0006]

Claims (15)

Rolling bearing arrangement, in particular for a wind power plant, comprising - a first ring (110, 210) and - a second ring (120, 220) which is mounted rotatably about an axis of rotation (D) relative to the first ring (110, 210); wherein the first ring (110, 210) and the second ring (120, 220) partially overlap axially, so that the first ring (110) forms an inner ring and the second ring (120) an outer ring or the first ring (210) forms an outer ring and the second ring (220) forms an inner ring; wherein the second ring (120, 220) has an end connection surface (121, 221) for connection to a first machine part, characterized by a non-rotatably connected to the first ring (110, 210), extending around the axis of rotation (D) and axially additional ring (140, 240) at least partially aligned with the first ring (110, 210); wherein the additional ring (140, 240) has a portion (142, 242) protruding by an axial projection h over the second ring (120, 220); whereby a bearing gap (160) is formed between the first ring (110, 210) and the additional ring (140, 240) connected to it on the one hand and the second ring (120, 220) on the other hand, so that the additional ring (140, 240) has a section (162) of the bearing gap (160) limited; and wherein the protruding section (142, 242) of the additional ring (140, 240) has an end face (144, 244) of the additional ring (140, 240) for a second machine part, which radially at least partially protrudes beyond the second ring (120, 220) . Rolling bearing arrangement according to Claim 1 , in which the connection surface (144, 244) of the additional ring (140, 240) on its side facing closer to the second ring (120, 220) has a circular boundary line or (145, 245) symmetrical in particular to the axis of rotation (D), wherein the Additional ring (140, 240) delimits the section (162) of the bearing gap (160) with an in particular cylindrical outer surface area (146, 246), a radial projection a being formed between the boundary line (145, 245) and the outer surface area (146, 246) The following applies in particular to the ratio between the radial projection a and the axial projection h: 1/10 a / h 3/1, preferably 1/5 a / h 2/1. Rolling bearing arrangement according to Claim 2 , in which the connection surface (121, 221) of the second ring (120, 220) has a radial width B, the following applies to the ratio between the radial projection a and the radial width B: 1/20 a / B 1 / 2. Rolling bearing arrangement according to one of the preceding claims, in which the second ring (120, 220) has an axial extension H, wherein for the ratio between the axial projection h of the additional ring (140, 240) and the axial extension H of the second ring (120, 220) The following applies: 1/20 ≤ h / H ≤ 1/2. Rolling element arrangement according to one of the preceding claims, in which the additional ring (140, 240) has a first protruding area (180) on its side facing the second ring (120, 220) to form the connection surface (144, 244) of the additional ring (140, 240) , 280), which preferably has a frustoconical lateral surface (181, 281) formed symmetrically about the axis of rotation (D) with a cone angle (a) which is smaller than 50 °, preferably smaller than 45 °. Rolling element arrangement according to Claim 5 in which the additional ring (140, 240) has a second protruding area (182, 282) on its side facing away from the second ring (120, 220) to form the connection surface (144, 244) of the additional ring (140, 240), which preferably has a frustoconical lateral surface (183, 283) formed symmetrically about the axis of rotation (D) with a cone angle (β) which is smaller than 70 °, preferably smaller than 50 °. Rolling bearing arrangement according to one of the preceding claims, further comprising - A first row (131) of rolling elements; - A second row (132) of rolling elements, the second row (132) being axially spaced from the first row (131); wherein the rolling elements of the two rows (131, 132) are arranged rolling between the first ring (110, 210) and the second ring (120, 220); wherein the rolling elements of the first row (131) and the rolling elements of the second row (132) are preferably essentially cylindrical and are arranged in such a way that their axes of rotation are oriented essentially perpendicular to the axis of rotation (D); wherein the first ring (110, 210) on its side facing the second ring (120, 220) has an annular collar (115, 215) with a circular cylindrical lateral surface (116, 216) and two circular ring-shaped end faces (117, 217), with the end faces (117, 217) each have a track for the first and second row (131, 132) of rolling elements. Rolling bearing arrangement according to Claim 7 , wherein the second ring (120, 220) has a first section (128, 228) and a second section (129, 229), wherein on the first section (128, 228) a raceway for the first row (131) of Rolling elements is formed and on the second section (129, 229) a raceway for the second row (132) of rolling elements. Rolling element arrangement according to one of the preceding claims, in which the additional ring (140, 240) has fastening bores (143, 243) arranged in a ring around the axis of rotation (D) for fastening the second machine part to the connection surface (144, 244) of the additional ring (140, 240) . Rolling bearing arrangement with the in the Claims 7 and 9 said features, in which the second ring (120, 220) has fastening bores (123, 223) arranged in a ring around the axis of rotation (D) for fastening the first machine part to the connection surface (121, 221) of the second ring (120, 220), wherein the fastening bores (143, 243) of the additional ring (140, 240) and the fastening bores (123, 223) of the second ring (120, 220) lie radially opposite one another with respect to the first row (131) of rolling elements; wherein the first ring (110, 210) preferably has fastening bores (113, 213) arranged in a ring around the axis of rotation (D) for the rotationally fixed connection to the additional ring (140, 240). Rolling bearing arrangement according to one of the preceding claims, in which the connection surface (144, 244) of the additional ring (140, 240) is flat and oriented normal to the axis of rotation (D) or has a truncated cone shape, the cone angle of the truncated cone shape preferably being greater than 70 ° , particularly preferably greater than 80 °. Rolling bearing arrangement according to one of the preceding claims, in which the rolling bearing arrangement furthermore has a sealing arrangement (170, 270) for sealing the section (162) of the bearing gap (160), with a sealing contact surface for the sealing arrangement (170, 170) preferably on the additional ring (140, 240). 270) is formed. Rolling element arrangement according to one of the preceding claims, in which the additional ring (140, 240) consists of a different material than the first ring (110, 210) and / or the second ring (120, 220). Rolling element arrangement according to one of the preceding claims, in which the additional ring (140, 240) consists of aluminum, structural steel, steel or cast iron. Rolling element arrangement according to one of the preceding claims, in which the diameter of the first ring (110, 210) and / or the diameter of the second ring (120, 220) is more than 1000 mm.

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