阅读说明：本技术 滚动轴承，尤其是大直径滚动轴承 (Rolling bearing, in particular large-diameter rolling bearing ) 是由 布鲁诺·卡波尔迪 赫维·东丹 于 2020-04-22 设计创作，主要内容包括：一种滚动轴承,包括内圈(12)和外圈(14),至少所述内圈或所述外圈形成为分体式圈并且被分成多个连续的周向环段(20、22)。所述滚动轴承还包括至少一个对齐构件(34、36),所述至少一个对齐构件(34、36)在周向上介于所述分体式圈的连续的环段的每对面对端部(20a、22a)之间,所述对齐构件(34、36)被固定到所述面对端部(20a、22a)中的一个面对端部上,并且突出到形成在另一面对端部上的凹部(30、32)中,以使所述对的面对端部在径向方向和轴向方向上对齐。(A rolling bearing comprises an inner ring (12) and an outer ring (14), at least the inner ring or the outer ring being formed as a split ring and divided into a plurality of continuous circumferential ring segments (20, 22). The rolling bearing further comprises at least one alignment member (34, 36), the at least one alignment member (34, 36) being circumferentially interposed between each pair of facing ends (20a, 22a) of successive ring segments of the split ring, the alignment member (34, 36) being fixed to one of the facing ends (20a, 22a) and protruding into a recess (30, 32) formed on the other facing end to align the pair of facing ends in a radial direction and in an axial direction.)

1. Rolling bearing comprising an inner ring (12) and an outer ring (14), at least the inner ring or the outer ring being formed as a split ring and divided into a plurality of consecutive circumferential ring segments (20, 22), characterized in that it further comprises at least one alignment member (34, 36), the at least one alignment member (34, 36) being interposed circumferentially between each pair of facing ends (20a, 22a) of the consecutive ring segments of the split ring, the alignment member (34, 36) being fixed to one of the facing ends (20a, 22a) and projecting into a recess (30, 32) formed on the other facing end, so as to align the pair of facing ends in a radial direction and in an axial direction.

2. Rolling bearing according to claim 1, wherein the alignment member (34, 36) is fixed into a recess (30, 32) formed on the one facing end which faces a recess (30, 32) formed on the other facing end.

3. Rolling bearing according to claim 1 or 2, comprising a first alignment member (34) extending in an axial direction and a second alignment member (36) extending in a radial direction, said first alignment member (34) and said second alignment member (36) being circumferentially interposed between facing ends (20a, 22a) of said pair of consecutive segments of said split ring.

4. Rolling bearing according to claim 3, wherein each of said first and second alignment members (34, 36) comprises a pin.

5. Rolling bearing according to any of the preceding claims, further comprising fixing means (40) for fixing the consecutive ring segments of the split ring together.

6. Rolling bearing according to claim 5, wherein said fixing member (40) is fixed to the outer surface of said split ring.

7. Rolling bearing according to any of the preceding claims, wherein a circumferential space (28) is provided between each pair of facing ends of successive ring segments (20a, 22a) of the split ring.

8. Rolling bearing according to claim 7, further comprising a plate (50) circumferentially interposed between the pair of facing ends to close said circumferential space (28).

9. Rolling bearing according to claim 8, further comprising at least one row of rolling elements (16) radially interposed between the raceways of the inner and outer rings, the plate (50) locally delimiting the raceways of the split ring.

10. Rolling bearing according to any of the preceding claims, wherein the alignment members (34, 36) are set back or flush with respect to the front face of the split ring and/or with respect to the bore and the outer surface of the split ring.

Technical Field

The present invention relates to the field of large diameter rolling bearings, in particular for use in tunnel boring machines or in defense equipment such as radar, char (/ char) (chars) or excavator (excator) applications. The large diameter rolling bearing may also be used for mounting the rotor blade on a wind turbine.

Background

A large-diameter rolling bearing generally comprises two concentric inner and outer rings, and at least one row of rolling elements radially interposed between the inner and outer rings.

In certain fields of application, rolling bearings are delivered (/ shipped) in a state in which the inner and outer rings are formed as split-rings (split-rings), to allow transport and/or assembly on the respective machine. In this case, each of the inner ring and the outer ring is divided into a plurality of successive circumferential ring segments (circumferential ring segments).

Therefore, after delivery, the ring segments (/ ring segments) must be joined together to assemble each split ring.

However, during assembly, the ring segments may not be aligned in the axial and radial directions. In this case, the assembly process of the rolling bearing is interrupted until the ring segments are disassembled and then realigned.

This adjustment step can be laborious and interrupts the assembly process and leads to an increase in the cost of the entire rolling bearing.

Disclosure of Invention

It is an object of the present invention to overcome these disadvantages.

In one embodiment, the rolling bearing comprises an inner ring and an outer ring, at least the inner ring or the outer ring (formed as a split ring and) being divided into a plurality of continuous circumferential ring segments.

According to a general feature of the invention, the rolling bearing further comprises at least one alignment member circumferentially interposed between each pair of facing ends of successive ring segments of the split ring.

The alignment member is fixed to one of the facing ends and protrudes into a recess formed on the other facing end to align the facing ends of the pair in a radial direction and an axial direction.

With this configuration, the ring segments of the split ring can be easily and perfectly aligned in the axial and radial directions during assembly. The use of such alignment members facilitates assembly and avoids disassembly of the split ring in the event of imperfect alignment of the ring segments. The total cost can be reduced and the flow can be simplified.

The alignment member may be fixed into a recess formed on the one facing end, the recess on the one facing end facing a recess formed on the other facing end.

In a particular embodiment, the rolling bearing comprises a first alignment member extending in an axial direction and a second alignment member extending in a radial direction, the first and second alignment members being circumferentially interposed between the facing ends of the pair of consecutive segments of the split ring. In this case, each of the first and second alignment members may include a pin, for example, a ball pin.

Alternatively, only one alignment member may be circumferentially interposed between the pair of facing ends. In this case, the alignment member may be spherical.

A chamfer may be provided for better adjustment between each recess on the associated facing end of the ring segment.

Advantageously, the rolling bearing may further comprise fixing means for fixing together the successive ring segments of the split ring. In one embodiment, the securing member is secured to an outer surface of the split ring.

A circumferential space may be provided between each pair of facing ends of successive ring segments of the split ring.

In a particular embodiment, the rolling bearing further comprises a plate circumferentially interposed between the pair of facing ends to close the circumferential space.

The rolling bearing may also comprise at least one row of rolling elements radially interposed between (the raceway of) the inner ring and the raceway of the outer ring. In this case, the plate may partially define the raceway of the split ring. For example, the rolling elements may be balls. Alternatively, it is also contemplated to use other types of rolling elements, such as cylindrical rollers. The rolling elements may be arranged in a cage, for example made of plastic, steel or the like. The cage can also be segmented (segmented) or made in one piece (/ in one part). Alternatively, the rolling bearing may include a plurality of spacers interposed between the rolling elements in the circumferential direction.

Advantageously, the alignment member is set back or flush with respect to a front face of the split ring. Thus, the alignment member does not protrude beyond the front face of the split ring in the axial direction. Due to this configuration, in the axial direction, there is no additional space requirement for the mounting of the alignment member.

Alternatively or in combination, the alignment member may be set back or flush with respect to the bore and outer surface of the split ring. Thus, the alignment member does not protrude beyond the bore and the outer surface of the split ring in the radial direction. Due to this configuration, in the radial direction, there is no additional space requirement for the mounting of the alignment member.

Drawings

The invention and its advantages will be better understood by studying the detailed description of a specific embodiment, given by way of non-limiting example and illustrated by the accompanying drawings, in which:

figure 1 is a partial side view of a rolling bearing according to a first example of the invention,

figure 2 is a partial perspective view of the rolling bearing of figure 1,

FIG. 3 is a section on III-III of FIG. 1,

figure 4 is a section on IV-IV of figure 1,

figure 5 is a partial section of a rolling bearing according to a second example of the invention,

Figure 6 is a partial side view of the rolling bearing of figure 5, an

Fig. 7 is a partial section on VII-VII of fig. 6.

Detailed Description

As shown in fig. 1 and 2, the rolling bearing 10 is a large-diameter rolling bearing including an inner ring 12 and an outer ring 14. The inner and outer races 12, 14 are concentric (/ coaxial) and extend axially along a bearing axis of rotation X-X' (fig. 3 and 4) that extends in an axial direction.

For example, the rolling bearing 10 may be used in a tunnel boring machine (tunnel boring machine), a wind turbine, or any other application that uses a large diameter rolling bearing.

As shown more clearly in fig. 3, the rolling bearing 10 also comprises an array of rolling elements 16 mounted between the inner ring 12 and the outer ring 14, the rolling elements 16 here being provided in the form of balls. The rolling bearing 10 further comprises a cage 18 for maintaining a regular circumferential spacing of the rolling elements 16.

The outer ring 14 comprises a cylindrical bore 14a, an outer cylindrical outer surface 14b and two opposite radial front lateral faces (front lateral faces) 14c, 14d, the two opposite radial front lateral faces 14c, 14d axially delimiting the bore 14a and the outer surface 14 b. In the disclosed example, the cylindrical bore 14a defines a raceway for the rolling elements 16. Alternatively, a circular race may be formed in the bore 14a of the outer race to define the race.

The inner ring 12 comprises a cylindrical bore 12a and an outer cylindrical surface 12b, and a circular ring-shaped raceway (not numbered) for the rolling elements 16 is formed by the outer cylindrical surface 12b, which raceway points radially outwards. The inner ring 12 further comprises two opposite radial frontal lateral faces 12c, 12d, the two opposite radial frontal lateral faces 12c, 12d axially delimiting the ring bore 12a and the outer surface 12 b. The lateral face 12d of the inner race is coplanar with the lateral face 14d of the outer race. The lateral face 12c of the inner race is axially offset outwardly relative to the lateral face 14c of the outer race.

Referring again to fig. 1 and 2, the inner ring 12 is segmented and formed of two continuous circumferential ring segments 20, 22. The inner ring 12 is formed as a split-ring (split-ring).

The outer race 14 is also formed as a split ring. The outer ring 14 is also formed of two continuous circumferential ring segments 24, 26. Alternatively, at least one of the inner race 12 and the outer race 14 may be formed of at least three consecutive ring segments.

In the disclosed embodiment, the axial length of the inner ring 12 is greater than the axial length of the outer ring 14 to hold the ring segments 20, 22 of the inner ring together by assembling bolts, as will be described later.

The ring segments 20, 22 forming the inner ring 12 are identical to each other. Each ring segment 20, 22 comprises a first end 20a, 22a and a second end (not visible in the figures) delimiting said ring segment in the circumferential direction. The first ends 20a, 22a of the ring segments 20, 22 face each other in the circumferential direction. A circumferential space 28 is provided between the first ends 20a, 22 a. The second ends of the ring segments 20, 22 also face each other in the circumferential direction. A circumferential space is also provided between these second ends.

As shown in fig. 1, 2 and 3, a first axial recess 30 is formed on each first end 20a, 22a of the ring segments 20, 22. The recesses 30 face each other in the circumferential direction. The recesses 30 are identical. Each recess 30 extends in the axial direction from a lateral face of the ring segment 20, 22 partially delimiting the lateral face 12c of the inner ring. Each recess 30 extends axially into the thickness of the ring segments 20, 22. Here, each recess 30 is a blind recess (/ blind groove) (blind recess).

A second radial recess 32 is also formed on each first end 20a, 22a of the ring segments 20, 22. Only the second radial recess 32 formed on the first end 22a of the ring segment 22 is visible (fig. 4).

The second radial recesses 32 face each other in the circumferential direction. The recesses 32 are identical. Each recess 32 extends radially from the hole of the ring segment 20, 22 partially delimiting the hole 12a of the inner ring. Each recess 32 extends radially into the thickness of the ring segment 20, 22 and is radially distanced (spaced) from the outer surface of said ring segment. In the disclosed example, each radial recess 32 opens into an axial recess 30. Alternatively, the radial recesses 32 may be spaced in a radial direction relative to the axial recesses 30.

In order to align the first ends 20a, 22a of the ring segments 20, 22 of the inner ring, the rolling bearing 10 further comprises axial pins 34 and radial pins 36 respectively located in the recesses 30, 32 of said ring segments.

The axial pins 34 extend into the two recesses 30 of the ring segments 20, 22 of the inner ring. The pin 34 extends axially into the recess 30. The pin 34 is completely accommodated within the recess 30 in the axial direction. The pin 34 is retracted (set back) with respect to the lateral surface 12c of the inner ring. The pin 34 also extends circumferentially into the recess 30. The pin 34 is fixed to one of the first ends 20a, 22a of the ring segments 20, 22 of the inner ring, where it is fixed to the first end 22 a. The pin 34 may be secured to the first end 22a by any suitable means, here by screwing (screwing) to the first end 22 a.

The radial pins 36 extend into the two recesses 32 of the ring segments 20, 22 of the inner ring. The pin 36 extends radially into the recess 32. The pin 36 is completely accommodated in the recess 32 in the radial direction. The pin 36 is retracted with respect to the bore 12a of the inner ring. The pin 36 also extends circumferentially into the recess 32. Similar to the axial pin 34, the radial pin 36 is also fixed to the first end 22a of the ring segment 22 by means of a threaded connection (/ screw joint).

The recesses 30, 32 are complementary in shape to the associated pins 34, 36. In the disclosed example, each pin 34, 36 has a cylindrical shape. Alternatively, each pin 34, 36 may have a different cross-sectional shape, such as rectangular, square, etc.

The first ends 20a, 22a of the ring segments 20, 22 of the inner ring are positioned in the radial direction to each other by means of the axial pin 34. The radial pins 36 enable the first ends 20a, 22a of the ring segments 20, 22 to be positioned one to the other in the axial direction. Thus, the first ends 20a, 22a of the ring segments 20, 22 are aligned in the radial direction as well as in the axial direction.

Like the first ends 20a, 22a of the ring segments 20, 22 of the inner ring, the rolling bearing 10 also comprises axial and radial pins (not visible in the figures) interposed circumferentially between the second ends of the ring segments 20, 22.

The rolling bearing 10 further comprises first and second fixing parts 40 to fix the segments 20, 22 of the inner ring together. Only the first fixing element 40 is visible in the figures.

The first fixing member 40 includes two flanges 40, 42 fixed to the outer surface of the inner race 12. The flanges 40, 42 are fixed to a portion of the inner race 12 that protrudes in the axial direction with respect to the outer race 14. The flange 40 is fixed to the ring segment 22, while the flange 42 is fixed to the ring segment 22. The flanges 40, 42 are fixed close to the circumferential space 28 provided between the first ends 20a, 22a of the ring segments 20, 22. The first fixing member 40 is also provided with a bolt 46 extending through the holes of the flanges 40 and 42 and a nut 48 fixing the bolt. The second fixing member is identical to the first fixing member 40. The first fixing element and the second fixing element are diametrically opposed (diametrically opposed).

The rolling bearing 10 further comprises a plate 50, the plate 50 closing the space 28 provided between the first ends 20a, 22a of the ring segments 20, 22. The plate 50 is fixed to the first end 22a of the ring segment 22 by means of a threaded connection. The plate 50 comprises an upper surface 50a flush with the raceway of the inner ring to prevent surface discontinuities at the height (/ level) of the space 28. The plate 50 partially forms a raceway for the rollers 16. A similar plate (not visible) may also foresee closing the space provided between the second ends of the ring segments 20, 22.

As previously mentioned, the outer ring 14 is also provided with ring segments 24, 26 identical to each other.

Each ring segment 24, 26 comprises a first end 24a, 26a and a second end (not visible in the figures) delimiting said ring segment in the circumferential direction. The first ends 24a, 26a of the ring segments 24, 26 face each other in the circumferential direction. A circumferential space 52 is provided between the first ends 24a, 26 a. The second ends of the ring segments 24, 26 also face each other in the circumferential direction. A circumferential space is also provided between these second ends.

Similar to the ring segments 20 and 22, the rolling bearing 10 comprises an axial pin 54 and a radial pin 56 interposed circumferentially between the first ends 24a, 26a of the ring segments 24, 26.

As shown in fig. 1, 2 and 3, a first axial recess 58 is formed on each first end 24a, 26a of the ring segments 24, 26. The recesses 58 face each other in the circumferential direction. The recesses 58 are identical. Each recess 58 extends axially from a lateral face of the ring segment 24, 26 that partially defines the lateral face 14c of the outer ring. Each recess 58 extends axially into the thickness of the ring segments 24, 26.

A second radial recess 60 is also formed on each first end 24a, 26a of the ring segments 24, 26. Only the second radial recess 60 formed on the first end 26a of the ring segment 26 is visible (fig. 4). The second radial recesses 60 face each other in the circumferential direction. The recesses 60 are identical. Each recess 60 extends radially from an outer surface of the ring segment 24, 26 that partially defines the outer ring outer surface 14 b. Each recess 60 extends radially into the thickness of the ring segment 24, 26 and is radially distanced from the aperture of said ring segment. Each recess 60 is a blind slot. In the disclosed example, each radial recess 60 extends through the axial recess 58. Alternatively, the radial recesses 60 may be spaced in a radial direction relative to the axial recesses 58.

The axial pins 54 extend into two recesses 58 of the ring segments 24, 26 of the outer ring. The pin 54 extends axially into the recess 58. The pin 54 is completely accommodated in the recess 58 in the axial direction. The pin 54 is retracted relative to the lateral face of the outer race. The pin 54 also extends circumferentially into the recess 58. The pin 54 is fixed to one of the first ends 24a, 26a of the outer ring segments 24, 26, where it is fixed to the first end 26 a. The pin 54 may be secured to the first end 26a by any suitable means, here by a threaded connection (/ threaded).

The radial pins 56 extend into two recesses 60 of the outer ring segments 24, 26. The pin 56 extends radially into the recess 60. The pin 56 is completely accommodated in the recess 60 in the radial direction. The pin 56 is retracted relative to the outer race outer surface 14 b. The pin 56 also extends circumferentially into the recess 60. Similar to the axial pin 54, a radial pin 56 is also fixed to the first end 26a of the ring segment 26 by means of a threaded connection (/ screw joint). The shape of the recesses 58, 60 is complementary to the shape of the associated pins 54, 56.

Like the first ends 24a, 26a of the ring segments 24, 26 of the outer ring, the rolling bearing 10 also comprises axial and radial pins (not visible in the figures) inserted circumferentially between the second ends of the ring segments 24, 26.

The rolling bearing 10 also comprises a fixing part 62 which fixes the ring segments 24, 26 of the outer ring together. The fixing member 62 comprises a plate ring 64 mounted to the outer surface of the outer race 14 and a plurality of radial screws 64 for fixing the plate ring to the outer race. The plate ring 64 may be annular or may be divided into a plurality of sections.

The rolling bearing 10 further comprises a plate 68, the plate 68 closing the space 52 provided between the first ends 24a, 26a of the ring segments 24, 26. The plate 68 is fixed to the first end 26a of the ring segment 26 by means of a threaded connection. Plate 68 includes a lower surface (not labeled) that is flush with bore 14a of the outer race. The plate 68 partially forms a raceway for the rollers 16. A similar plate (not visible) may also foresee closing the space provided between the second ends of the ring segments 24, 26.

In addition, as previously described, in the illustrated example, both the inner ring 12 and the outer ring 14 of the rolling bearing are formed as split rings. Alternatively, the rolling bearing can have only one ring formed by successive circumferential ring segments.

For example, in the example shown on fig. 5 to 7, in which like parts are given like reference numerals, only the outer ring 14 is formed by consecutive circumferential ring segments 24, 26. In this example, the plate ring 64 extends over a limited angular sector. Similar ring segments (not visible) are diametrically opposed. With respect to the first example, the relative radial arrangement of the pins 54, 56 is reversed.

In this example, the inner ring 12 comprises two parts stacked relative to each other in the axial direction. Two portions of the inner race 12 are provided with a plurality of aligned through holes (not numbered) to be joined together by fitting bolts (not shown).