DE102017106957A1 - roller bearing - Google Patents

Abstract

The invention relates to a double-row tapered roller bearing (12) formed roller bearing (10), for example, for a wind turbine, which has a first inner ring (14), a second inner ring (16) and a coaxially arranged above outer ring (18), in the radially between the two inner rings (14, 16) and the outer ring (18) rolling elements (26, 30) in two rows of rolling elements (28, 36) are arranged, wherein the rolling elements (26) of the first row of rolling elements (28) on a first inner ring raceway (22 ) and a first outer ring raceway (24) and the rolling elements (30) of the second rolling element row (36) roll on a second inner ring raceway (32) and a second outer ring raceway (34), in which the rolling elements (26, 30) in at least one Wälzkörperkäfig ( 42, 44) are arranged, and in which a bearing interior (50) is at least partially filled with a lubricant (52). According to the invention, provision is made in each case for a carrier ring (62; 68) to be arranged on the two axial end faces (60; 66) of the outer ring (18), that these carrier rings (62; 68) each radially inwardly comprise a sealing element (64; or that the sealing elements (64; 70) each sealingly cooperate with a radially outwardly facing sealing surface (84; 90) of an associated inner ring (14; 16), and that the carrier rings (62; 68) in each case at least one radially outwardly directed outlet bore (72) for leakage of lubricant (52) from the bearing interior (50).

Description

The invention relates to a designed as a double-row tapered roller bearings, for example, for a wind turbine, which has a first inner ring, a second inner ring and a coaxially disposed outer ring, in which radially between the two inner rings and the outer ring rolling elements are arranged in two rows of rolling elements, in which the rolling elements of the first row of rolling elements roll on a first inner ring raceway and a first outer ring raceway and the rolling elements of the second row of rolling elements on a second inner ring raceway and a second outer ring raceway, wherein the rolling elements are arranged in at least one Wälzkörperkäfig, and wherein a bearing interior at least partially with a lubricant is filled.

Rolling bearings are known to be used for low-friction storage of rotating machine elements. In the field of wind turbines, large-diameter bearings are used, among other things, for supporting the rotor shaft. In order to enable a low-friction and low-noise operation, the interior of such large rolling bearing is at least partially filled with a lubricant, such as a high-viscosity bearing grease or the like. To seal the interior, for example, are radial shaft seals. The lubricants required for operation can be supplied to the rolling bearing, for example, via a housing-fixed bearing ring and be removed from this. Due to such a supply and Abführprozesses act in the known rolling bearings undesirable mechanical stresses on the radial shaft seals, which can lead to unwanted leakage in the region of the sealing lips of the radial shaft seals.

The invention is therefore based on the object to introduce a sealed rolling bearing with an improved Schmiermittelabführvorrichtung. The construction of such a rolling bearing should also be suitable for slewing bearings, which serve as the main rotor bearing of wind turbines, for example.

The solution of this problem is achieved with a roller bearing having the features of claim 1. Advantageous developments are defined in the dependent claims.

Accordingly, the invention relates to a designed as a double-row tapered roller bearing, for example, for a wind turbine, which has a first inner ring, a second inner ring and a coaxially disposed outer ring, are arranged in the radially between the two inner rings and the outer ring rolling elements in two rows of rolling at in which the rolling elements of the first row of rolling elements roll on a first inner ring raceway and a first outer ring raceway and the rolling elements of the second row of rolling elements on a second inner ring raceway and a second outer ring raceway, wherein the rolling elements are arranged in at least one Wälzkörperkäfig, and wherein a bearing interior at least partially with a Lubricant is filled.

To achieve the object, it is provided that in each case a support ring is arranged at the two axial end faces of the outer ring, that these support rings radially inside each carrying a sealing element or that the sealing elements cooperate sealingly with a radially outwardly facing sealing surface of an associated inner ring , and that the carrier rings each have at least one radially outwardly directed outlet bore for a discharge of lubricant from the bearing interior.

By the at least one outlet hole, a controlled exit of the lubricant from the bearing interior is made possible in the outer environment of the rolling bearing when the rolling bearing, for example, new lubricant is supplied. In this process, the leakage of the lubricant can be promoted or supported by the centrifugal forces occurring during operation of the bearing so that mechanical stress on the sealing elements due to pressure spikes in the lubricant, which can lead to unwanted leaks, are largely avoided. Regardless of the random distribution of the lubricant in the bearing interior is ensured by a larger number of outlet holes always controlled leakage of the lubricant in each rotational position of the bearing. Preferably, at each axial end side of the outer ring, a Auslassbohrungen exhibiting carrier ring is arranged, and the outlet bores are circumferentially arranged uniformly spaced from each other.

According to an advantageous embodiment, it is provided that the carrier rings are each arranged in an annular recess on axially opposite end faces of the outer ring. As a result, a mechanically reliable attachment of the two carrier rings on a shoulder of the wells, for example by means of a press fit, feasible. For this purpose, the respective recesses have a sufficient depth.

Another development provides that the sealing elements have two radially inwardly directed sealing lips, which bear against a radially outwardly facing sealing surface of the associated inner ring. As a result, is a reliable Ensured sealing between the outer ring and the two inner rings of the bearing.

Preferably, the first sealing element and the second sealing element are designed as radial shaft seals. As a result, a particularly effective, durable and at the same time low-friction sealing of the example, in relation to the two inner rings rotating outer ring is given.

Furthermore, it is preferably provided that an annular collecting plate is fastened to the associated end face of the outer ring radially above each carrier ring. As a result, any lubricants escaping from the outlet bores during relubrication of the roller bearing do not enter the external environment of the rolling bearing in an uncontrolled manner. The collecting plates may, for example, have a U-shaped cross-section geometry with radially inwardly projecting long legs, so that the collecting plates each have radially inwardly open collecting spaces. In this way, escaping lubricant can drain from these independently of the circumferential position of the outlet openings or be reliably collected when rotating the outer ring. The outlet openings may also have connection elements to which a drainage line for leaking lubricant can be secured leak-tight during maintenance work.

According to another advantageous embodiment, it is provided that the carrier rings each have a radially inwardly and axially outwardly open annular groove for receiving the respective sealing element. As a result, these sealing elements are secured in position radially and at the same time axially inwardly.

According to a technically advantageous embodiment, it is provided that in each case a retaining ring is arranged on the axially outwardly facing end faces of the carrier rings. As a result, the axial position assurance of the two main sealing elements is completed. In addition, the two provided on the support rings retaining rings allow the attachment of other structural components. The attachment of the retaining rings to the support rings can be done for example by means of strong magnets, by gluing, clamping, by means of a resilient locking ring or the like.

In addition, it can be provided that a radially inwardly extending cover plate is attached to the respective retaining ring. In this way, a gap-based, additional protective barrier is provided against foreign particles and / or fluids which penetrate from outside into the area of the sealing elements and completes the sealing effect of the rolling bearing.

Preferably, at least one sealing ring is provided between the outer ring and the two carrier rings. As a result, the seal of the rolling bearing is completed.

According to another embodiment of the invention, it is provided that no separate sealing elements are arranged on the carrier rings, but that the carrier rings are formed radially inside each as part of a labyrinth seal. In this case, the carrier rings interact radially inwardly by means of the labyrinth seal with the associated inner rings to seal the rolling bearing.

In addition or as an alternative to the outlet bores in the carrier rings, outlet bores can also be formed in the rotatably arranged outer ring, which radially outwardly lead to the two named collecting plates.

For a better understanding of the invention, the description is accompanied by a drawing of an embodiment, which will be explained below.

The single FIGURE shows a partial longitudinal section through an inventive large rolling bearing 10 , which acts as a double row tapered roller bearing 12 for a wind turbine or the like. This tapered roller bearing 12 has a first inner ring 14 , a second inner ring 16 and a coaxial over these two inner rings 14 . 16 arranged outer ring 18 on. Radial between the two inner rings 14 . 16 and the outer ring 18 are frustoconical rolling elements 26 . 30 in two rows of rolling elements 28 . 36 arranged. The rolling elements 26 the first row of rolling elements 28 roll on a first inner ring track 22 and a first outer ring raceway 24 down, and the rolling elements 30 the second row of rolling elements 36 roll on a second inner ring track 32 and a second outer raceway 34 from. Every row of rolling elements 28 . 26 is a Wälzkörperkä 42 . 44 assigned, in which the rolling elements 26 . 30 are received rotatably. The warehouse interior 50 tapered roller bearing 12 In addition, at least partially with a lubricant 52 filled, which is not separately graphically marked here. Both the outer ring 18 as well as the two inner rings 14 . 16 and the two Wälzkörperkäfige 42 . 44 can be designed to simplify the manufacture, assembly and maintenance in a target application, for example, segmented in the circumferential direction. Axial on both sides of the two inner ring raceways 22 . 32 is in each case a guide board for axial guidance of the rolling elements 26 . 30 provided while the two outer ring raceways 24 . 34 of the outer ring 18 are board-free.

Due to the V-shaped rows of rolling elements 28 . 36 can handle the slewing bearing 10 or the tapered roller bearing 12 to absorb equally high radial forces as well as significant axial forces, as they occur for example in bearings of rotor shafts in wind turbines.

To reduce the bearing friction, for noise reduction and to prevent the penetration of foreign particles and / or liquids as completely as possible, is a bearing interior 50 at least partially with the lubricant 52 filled. For the lubricant 52 it is preferably a highly viscous and substantially non-compressible bearing grease.

The two axially interconnected on inner joints 14 . 16 tapered roller bearing 12 are penetrated by a plurality of axial through holes, of which only a through hole 54 is shown. Through the through holes extend in the axial direction, not shown bolts for mechanically fixed connection of the two inner rings 14 . 16 together. For sealing the bearing interior 50 are also two annular seal 56 . 57 in ring grooves 58 . 59 the inner rings 14 . 16 taken, for example, as an O-ring or as a hollow cylindrical sealing ring made of a suitable plastic.

In the region of a first axial end face 60 of the outer ring 18 is a first carrier ring 62 for fastening a first sealing element 64 arranged. Accordingly, in the region of an axially opposite second end face 66 of the outer ring 18 a second carrier ring 68 for fastening a second sealing element 70 arranged. According to the invention, these two carrier rings 62 . 68 A plurality of radially outwardly directed outlet bores 72 for the lubricant 52 on, of which here only one outlet hole 72 is recognizable. The outlet holes 72 are preferably in the same number and circumferentially evenly spaced from each other in each case in the two carrier rings 62 . 68 introduced and can be designed as cylindrical through holes or stepped holes whose larger diameter portions are radially further outward.

The first carrier ring 62 is at the first end face 60 of the outer ring 18 in a substantially annular recess 74 added. Likewise, the second carrier ring is also 68 in a substantially annular recess 76 in the second end face 66 of the outer ring 18 added. These recesses are so large that the carrier rings 62 . 68 can be kept in it. As a result, the arrangement of the two carrier rings 62 . 68 on the outer ring 18 also designed mirror-symmetrical.

In the two carrier rings 62 . 68 is in each case a radially inwardly and axially outwardly open annular groove 92 . 94 for receiving the two mentioned sealing elements 64 . 70 educated. In the ring groove 92 of the first carrier ring 62 is the first sealing element 64 taken up and fixed radially here and at the same time positionally secured axially inwards. In addition, the second sealing element 70 in the ring groove 94 of the second carrier ring 68 taken up and thereby likewise locked radially and at the same time positionally secured inwardly.

The two sealing elements 64 . 70 are preferably as low-friction and low-maintenance and durable radial shaft seals 96 . 98 executed. They each have first sealing lip 80 . 86 and a second sealing lip 82 . 88 on, which are each directed radially inwardly and with a relatively low contact force in mechanical contact with a respectively associated, radially outwardly directed cylindrical sealing surface 84 . 90 of the first inner ring 14 or second inner ring 16 are. The first sealing lips 80 . 86 both sealing elements 64 . 70 are in relation to the respective second sealing lips 82 . 88 arranged axially further outboard.

To complete the sealing of the tapered roller bearing 12 is axially between the first carrier ring 62 and the depression associated therewith 74 of the outer ring 18 a sealing ring 100 arranged. Likewise, axially between the second carrier ring 68 and the depression associated therewith 76 of the outer ring 18 another sealing ring 102 arranged. The two sealing rings 100 . 102 For example, each may be manufactured as an O-ring or as a hollow cylindrical sealing ring made of a suitable plastic.

At the first end face 60 of the outer ring 18 Here is merely an example, a first, annular collecting plate 104 and at the second end face 66 of the outer ring 18 is a second, annular collecting plate 106 each radially outward with respect to the two carrier rings 62 . 68 attached in a suitable manner. The two collecting trays 104 . 106 Here, for example, each have an approximately U-shaped cross-sectional geometry. The catchment areas 108 . 110 the two channel-like collecting plates 104 . 106 are each radially inwardly open. Thus, along a lubrication path indicated by a dotted line 112 from the warehouse interior 50 and ultimately from the outlet wells 72 leaking lubricant 52 from the two collecting trays 104 . 106 be equally reliably collected.

The flow movement of the exiting lubricant 52 along the lubricant path 112 is due to the resulting centrifugal force supported, which in the operation of the tapered roller bearing 12 due to relative to the housing-fixed inner rings 14 . 16 rotating outer ring 18 is caused. It can also be seen that the lubricant path 112 axially spaced from each other as a radial shaft seal 96 . 98 trained sealing elements 64 . 70 runs, so in the case of a maintenance-related supply of fresh lubricant 52 in the sense of relubricating in the bearing interior 50 by means of a grease gun, etc. no significant pressure load in the region of the sealing elements 64 . 70 occurs. As a result, the risk of leaks in the area of the sealing lips 80 . 82 ; 86 . 88 the two sealing elements 64 . 70 practically impossible.

If the two containment areas 108 . 110 the collecting trays 104 . 106 with the lubricant 52 filled, the lubricant can 52 from the collecting trays 104 . 106 be removed by means of a suitable tool. This reliably prevents the lubricant 52 uncontrolled from the warehouse interior 50 into the external environment 114 tapered roller bearing 12 reach and thus contaminate it.

At the axially outwardly facing end face 120 of the first carrier ring 62 is a first retaining ring 122 and on the axially outwardly facing end face 124 of the second carrier ring 68 is a second retaining ring 126 attached. The attachment of the two retaining rings 122 . 126 at the associated carrier rings 62 . 68 For example, by gluing, clamps, retaining rings, magnetic brackets, Velcro connections or the like. Through the two retaining rings 122 . 126 are the sealing elements 64 . 70 secured radially outward. The cross-sectional geometry of the two retaining rings 122 . 126 Here, for example, in each case corresponds to the rectangles adjoining one another along their longitudinal sides.

In a first inner ring groove of the first retaining ring 122 is a first, approximately circular cover 128 added. Likewise, in a second inner ring groove of the second retaining ring 126 is a second, substantially also annular cover 130 attached. Through the two cover discs 128 . 130 is an acting in the manner of a gap seal, additional protective barrier against any, from the outside environment 114 to the area of the two as radial shaft seals 96 . 98 trained sealing elements 64 . 70 penetrating foreign particles and / or fluids created.

Deviating from the exactly radial course of the outlet bores shown in the figure 72 in the carrier rings 62 . 68 can the outlet holes 72 also have an axial direction component, so that they in the carrier rings 62 . 68 from radially and axially inside obliquely lead radially and axially outside. The two collecting trays 104 . 106 would then be correspondingly geometrically adapted to be able to absorb escaping lubricant. In extreme cases, such oblique outlet holes 72 also by the adjacent retaining ring 122 . 126 be guided.

Additionally or alternatively to the outlet holes 72 in the carrier rings 62 . 68 can also drain holes 72 * in the rotatably arranged outer ring 18 be formed, which radially inward with the bearing interior 50 are connected and radially outward to the associated collecting plate 104 . 106 to lead. This embodiment is indicated on the left half in the figure with a dashed line.

LIST OF REFERENCE NUMBERS

10

slewing bearings

12

Tapered roller bearings

14

First inner ring

16

Second inner ring

18

outer ring

22

First inner ring raceway

24

First outer ring raceway

26

rolling elements

28

First row of rolling elements

30

rolling elements

32

Second inner ring raceway

34

Second outer ring raceway

36

Second row of rolling elements

42

First rolling element cage

44

Second rolling element cage

50

Warehouse interior

52

lubricant

54

Axial through-hole

56

First seal

57

Second seal

58

First ring groove

59

Second ring groove

60

First face of the outer ring

62

First carrier ring

64

First sealing element

66

Second end face of the outer ring

68

Second carrier ring

70

Second sealing element

72

Outlet bore in the carrier ring

72 *

Outlet bore in the outer ring

74

deepening

76

deepening

80

First sealing lip

82

Second sealing lip

84

Sealing surface of the first inner ring

86

First sealing lip

88

Second sealing lip

90

Sealing surface of the second inner ring

92

Ring groove in the first carrier ring

94

Ring groove in the second carrier ring

96

First radial shaft seal

98

Second radial shaft seal

100

First sealing ring

102

Second sealing ring

104

First collecting tray

106

Second collecting tray

108

Collection room in the first collecting tray

110

Collecting room in the second collecting tray

112

lubricant path

114

External environment of the rolling bearing

120

Front side of the first carrier ring

122

First retaining ring

124

Front side of the second carrier ring

126

Second retaining ring

128

First cover

130

Second cover

Claims (10)

Rolling bearing (10) formed as a double-row tapered roller bearing (12), for example, for a wind turbine, which has a first inner ring (14), a second inner ring (16) and a coaxially above these two inner rings (14, 16) arranged outer ring (18) , in which between the two inner rings (14, 16) and the outer ring (18) rolling elements (26, 30) in two rows of rolling elements (28, 36) are arranged, in which the rolling elements (26) of the first row of rolling elements (28) a first inner ring raceway (22) and a first outer ring raceway (24) and the rolling elements (30) of the second rolling body row (36) roll on a second inner ring raceway (32) and a second outer ring raceway (34), wherein the rolling elements (26, 30) in at least one Wälzkörperkäfig (42, 44) are arranged, and in which a bearing interior (50) is at least partially filled with a lubricant (52), characterized in that at the two axial end faces (60; 6) of the outer ring (18) each have a carrier ring (62; 68) is arranged such that these carrier rings (62; 68) bear radially in each case a sealing element (64; 70) or that the sealing elements (64; 70) each have a radially outwardly facing sealing surface (84; Inner rings (14; 16) sealingly cooperate, and that the support rings (62; 68) each have at least one radially outwardly directed outlet bore (72) for an outlet of lubricant (52) from the bearing interior (50). Rolling bearings after Claim 1 , characterized in that the carrier rings (62; 68) are each arranged in an annular recess (74; 76) on axially opposite end faces (60; 66) of the outer ring (18). Rolling bearings after Claim 1 or 2 , characterized in that the sealing elements (64, 70) each have two radially inwardly directed sealing lips (80, 82, 86, 88), which at the associated, radially outwardly facing sealing surface (84, 90) of the associated inner ring (14; 16) abut. Rolling bearings according to one of Claims 1 to 3 , characterized in that the sealing elements (64; 70) are formed as radial shaft sealing rings (96, 98). Rolling bearings according to one of Claims 1 to 4 characterized in that radially above each support ring (62; 68) an annular collecting plate (104; 106) is fixed to the associated end face (60; 66) of the outer ring (18), and that the collecting plates (104; 106) each have a radial inwardly open receiving space (108; 110). Rolling bearings according to one of Claims 1 to 5 , in that the carrier rings (62; 68) each have an annular groove (92; 94) open radially inwards and axially outwardly for receiving the sealing element (64; 70). Rolling bearings according to one of Claims 1 to 6 , characterized in that on the axially outwardly facing end face (120; 124) of the respective carrier ring (62; 68), a retaining ring (122; 126) is arranged. Rolling bearings after Claim 7 , characterized in that on the respective retaining ring (122; 126) a radially inwardly extending cover plate (128; 130) is fixed. Rolling bearings according to one of Claims 1 to 8th , characterized in that additionally or Alternatively to the outlet bores (72) in the support rings (62; 68) outlet holes (72 *) are formed for the lubricant (52) in the rotatably arranged outer ring (18), which radially outwardly lead to associated collecting plates (104, 106). Rolling bearings according to one of Claims 1 to 9 characterized in that no separate sealing elements (64; 70) are arranged on the carrier rings (62; 68), but that the carrier rings (62; 68) are formed radially inside each as part of a labyrinth seal which sealingly with the two inner rings (62; 14, 16) cooperate.

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