JP2012097800A - Cylindrical roller bearing and cylindrical roller bearing device - Google Patents

Abstract

PROBLEM TO BE SOLVED: To provide a cylindrical roller bearing which holds a high load capacity as the cylindrical roller bearing, has a certain degree of self-aligning properties and also can be manufactured without depending on grinding.SOLUTION: In the cylindrical roller bearing, taper surfaces 35 and 38 are formed on respective outer circumferential surfaces of both ends of an outer ring 22 and respective inner circumferential surfaces of both ends of an inner ring 23, slits 36 and 39 in an axial direction of one or more are provided at both ends of the outer ring 22 and the inner ring 23, and an outer ring pressure ring 42 of outer ring pressurizing means 29 and an inner ring pressure ring 47 of inner ring pressurizing means 31 are engaged with the respective taper surfaces 35 and 38 of the outer ring 22 and the inner ring 23. Both ends of the outer ring 22 and the inner ring 23 are elastically deformed in a radial direction by acting an outer ring pressing member 43A and an inner ring pressing member 48A to the outer ring pressure ring 42 and the inner ring pressure ring 47 respectively, and respective raceway surfaces 27 and 28 are retained in a curved state by the respective pressurizing means 29 and 31.

Description

  The present invention relates to a cylindrical roller bearing and a cylindrical roller bearing device, and more particularly to formation of raceway surfaces of inner and outer rings.

  Cylindrical roller bearings have large radial load capacity due to the linear contact between the rolling elements of cylindrical rollers and the raceway surface. On the other hand, there is no self-alignment. It cannot be used for the part where the inner / outer ring is tilted.

  A cylindrical roller bearing with a centering ring is known as a bearing that makes use of the above characteristics of the cylindrical roller bearing and further provides self-alignment (Patent Document 1). As shown in FIG. 12, the cylindrical roller bearing 1 with a centering ring includes an outer ring 2 and an inner ring 3, and a cylindrical rolling element 4 and a centering ring 5 interposed between these raceway surfaces. . An outer diameter surface of the outer ring 2 is formed into a convex spherical surface, and the outer ring 2 is fitted into a concave spherical surface formed on the inner diameter surface of the aligning ring 5. Each of these spherical surfaces is formed to have the same radius of curvature around the center of the bearing.

  The above-mentioned cylindrical roller bearing 1 with a centering ring has the characteristics of a cylindrical roller bearing and also has self-aligning properties. However, since the centering ring 5 is required, an increase in the outer diameter of the bearing can be avoided. Absent.

  On the other hand, as shown in FIG. 13, there is known a cylindrical roller bearing 6 imparted with a certain degree of self-alignment without using the aligning ring 5 (Non-patent Document 1). The raceway surfaces 9 and 10 of the outer ring 7 and the inner ring 8 of the cylindrical roller bearing 6 are formed into spherical surfaces having a radius of curvature that is about twice as large as that of a normal self-aligning roller bearing. The rolling elements 11 are in a single row and are formed in a shape having a gentle spherical surface corresponding to the raceway surfaces 9 and 10.

JP-A-11-82495

http://www.skf.com/portal/skf_jp/home Product Information “Toroidal Roller Bearings”

  Since the cylindrical roller bearing 6 shown in FIG. 13 is formed such that the width of the outer ring 7 and the inner ring 8 and the axial length of the rolling element 11 are larger than those of a normal cylindrical roller bearing, a high load capacity can be obtained. Since the raceway surfaces 9 and 10 are formed as gentle spherical surfaces, they have a certain degree of self-alignment.

  However, when the raceway surface 9 of the outer ring 7 is processed, it is necessary to form the grindstone with an R-shaped rotary dresser and press the grindstone formed in the R-shape to a fixed position on the outer ring for grinding.

  In this case, a grinding wheel wider than the bearing width is required. Further, compared to the case where the grinding stone is traversed for grinding, heat is easily generated, heat dissipation is difficult, and a long time is required for processing. From these things, processing cost may become high. The same applies to the processing of the raceway surface 10 of the inner ring 8.

  Accordingly, the present invention provides a cylindrical roller bearing and a cylindrical roller bearing device that retain a high load capacity as a cylindrical roller bearing, have a certain degree of self-alignment, and can be manufactured without using the grinding process as described above. The issue is to provide.

  In order to solve the above-described problems, an invention relating to a cylindrical roller bearing includes a cylindrical roller bearing in which a single-row cylindrical roller-shaped rolling element is interposed between raceways of an outer ring and an inner ring, and the rolling element is crowned. The outer ring and the inner ring each have left and right end portions extending in the axial direction from the intermediate portion, and the outer ring has tapered outer surfaces at both end portions, and the inner ring has tapered surfaces at inner diameter surfaces at both end portions. One or more axial slits are provided at both ends of the outer ring and the inner ring on which the tapered surfaces are formed, and an outer ring pressurizing means and an inner ring pressurizing means are provided for each of the outer ring and the inner ring, The pressure means includes a pair of outer ring pressure rings fitted to the respective tapered surfaces of the outer ring and an outer ring pressing member that presses the pressure rings in a direction approaching each other. Each taper A pair of inner ring pressure rings fitted to each other and an inner ring pressing member that presses each pressure ring in a direction approaching each other, and the outer ring and the inner ring are operated by operating the outer ring pressing member and the inner ring pressing member. Both end portions of the outer ring and the inner ring are elastically deformed in a radial direction so that the raceways of the outer ring and the inner ring are curved along the crowning of the rolling element, and the curved state is maintained by the pressing members.

  In the cylindrical roller bearing having the above-described configuration, by operating the outer ring pressing member and the inner ring pressing member during the assembly, a load in the reduced diameter direction is applied to both ends of the outer ring, and a load in the expanded direction is applied to both ends of the inner ring. In addition, the raceways of the outer ring and the inner ring are elastically deformed into a curved state. The elastically deformed curved state is maintained by the outer ring pressing member and the inner ring pressing member, respectively, and used in that state.

  The outer ring pressing member and the inner ring pressing member can be constituted by a plurality of bolts and nuts. On the outer ring side, the bolts are passed through the outer ring pressure rings on both sides and tightened with nuts to apply a load in the direction of diameter reduction to both ends of the outer ring. On the inner ring side, a bolt is passed through the inner ring pressure rings on both sides and a nut is tightened to apply a load in the diameter increasing direction to both ends of the inner ring.

  Further, in the invention related to the roller bearing device, a single-row cylindrical roller-shaped rolling element is interposed between the raceways of the outer ring and the inner ring, the rolling element is crowned, and the outer ring is housed in a bearing box, In the cylindrical roller bearing device in which the inner ring is fitted to the shaft, each of the outer ring and the inner ring has left and right end portions extending in the axial direction from the intermediate portion, the outer ring has outer diameter surfaces at both ends, and the inner ring has the Tapered surfaces are formed on the inner diameter surfaces of both end portions, and one or more axial slits are provided on both end portions of the outer ring and the inner ring on which the tapered surfaces are formed. Inner ring pressurizing means is provided, and the outer ring pressurizing means is a pair of outer ring pressurizing rings fitted to the respective tapered surfaces of the outer ring, and an outer ring pressing member that presses each pressurizing ring in a direction approaching each other. Composed of before The inner ring pressure means includes a pair of inner ring pressure rings fitted to the tapered surfaces of the inner ring and an inner ring pressure member that presses the pressure rings in a direction approaching each other. The inner ring pressing member is screwed to the outer diameter surface of the shaft on the inner diameter surface of the bearing housing, and the outer ring pressing member and the inner ring pressing member are operated from the outside so that both ends of the outer ring and the inner ring are moved in the radial direction. Elastically deformed, the raceways of the outer ring and inner ring are curved along the crowning of the rolling element, and the curved state is maintained by the pressing members.

  In this case, as the structure for advancing the outer ring pressing member and the inner ring pressing member, the former employs a structure in which the former is screwed to the inner diameter surface of the bearing box and the latter is threaded to the outer diameter surface of the shaft. There are differences. Further, since the bearing housing and the shaft are constituent elements of the invention, the invention of the apparatus is provided.

  The specific configurations of the outer ring pressing member and the inner ring pressing member are constituted by an outer ring pressing screw ring and an inner ring pressing screw ring, respectively, and the outer ring pressing screw ring is a male screw on its outer diameter surface, and the inner ring pressing ring is It is possible to adopt a configuration in which female threads are respectively formed on the inner diameter surface.

  In both inventions of the cylindrical roller bearing and the cylindrical roller bearing device, a load is applied from the outside by operating the outer ring pressing member and the inner ring pressing member from the outside during the assembly, and the raceways of the outer ring and the inner ring are elastically deformed into a curved state. The deformation state is maintained.

  For this reason, the track surface having a curved shape can be formed without using grinding. In addition, the radius of curvature of the raceway surface can be easily controlled by adjusting the pressing force of the pressing member.

  In addition, the curvature radius of the raceway surface and the crowning of the rolling element is formed in a curved surface having a certain degree of curvature radius, so that it has alignment with bearing mounting error and shaft deflection, and The axial displacement is possible and the reliability as a free-side bearing is improved. Furthermore, it has a load capacity equal to or greater than that of conventional spherical roller bearings having the same cross-sectional dimensions.

FIG. 1 is a partially omitted cross-sectional view of the cylindrical roller bearing according to the first embodiment during assembly. 2 is a cross-sectional view taken along line X1-X1 of FIG. 3 is a cross-sectional view taken along line X2-X2 of FIG. FIG. 4 is a partially omitted cross-sectional view after completion of the assembly of the tapered roller bearing of the first embodiment. Fig.5 (a) is a perspective view of an outer ring | wheel same as the above, FIG.5 (b) is sectional drawing of an outer ring | wheel. FIG. 6A is a perspective view of the inner ring, and FIG. 6B is a cross-sectional view of the inner ring. FIG. 7 is a partially omitted cross-sectional view of the cylindrical roller bearing device according to the second embodiment during assembly. 8 is a cross-sectional view taken along line X3-X3 in FIG. 9 is a cross-sectional view taken along line X4-X4 of FIG. FIG. 10A is a perspective view of the outer ring pressing screw ring, and FIG. 10B is a perspective view of the inner ring pressing screw ring. FIG. 11 is a partially omitted cross-sectional view after completion of the assembly of the tapered roller bearing device of the second embodiment. FIG. 12 is a partially omitted sectional view of a conventional cylindrical roller bearing. FIG. 13 is a partially omitted sectional view of another conventional cylindrical roller bearing.

Embodiments of the present invention will be described below with reference to the accompanying drawings. 1 to 6 relate to the first embodiment, and FIGS. 7 to 11 relate to the second embodiment.
[Embodiment 1]

    1 to 3 show a state during the assembly of the cylindrical roller bearing 21 of the first embodiment, and FIG. 4 shows a state after the assembly is completed.

  The cylindrical roller bearing 21 includes an outer ring 22, an inner ring 23, a cylindrical roller-shaped rolling element 24 interposed therebetween, and a cage 25 for the rolling element 24. The raceways 27 and 28 of the outer ring 22 and the inner ring 23 are in a cylindrical state before deformation.

  Further, the outer ring 22 and the inner ring 23 are forcibly applied with a load, and the raceway surfaces 27 and 28 are deformed into a curved state. The outer ring pressurizing means 29 and the inner ring pressurizing means 31, the other outer ring load receiving ring 32, the inner ring load. A receiving ring 33 is provided. The material of the outer ring 22 and the inner ring 23 is bearing steel.

  As shown in FIGS. 5A and 5B, the outer ring 22 has an intermediate portion 34 formed in a cylindrical shape, and tapered surfaces 35 are formed on the outer diameter surfaces of the left and right end portions 30 of the intermediate portion 34. The At both end portions 30 of the outer ring 22, axial slits 36 are formed within the range of the tapered surface 35 from the end surface. In the illustrated example, the slits 36 are formed at four positions in the circumferentially equidistant position, but may be formed at one or more positions. Further, the end portion of each slit 36 may partially enter the intermediate portion 34.

  As shown in FIGS. 6A and 6B, the inner ring 23 also has an intermediate portion 37 formed in a cylindrical shape and a tapered surface 38 formed on the inner diameter surfaces of both end portions 40 as in the case of the outer ring 22. . Further, in both end portions 40, axial slits 39 are formed within the range of the tapered surface 38 from the respective end surfaces. The slits 39 are also shown as being formed at four locations in the circumferentially equidistant position, but may be formed at one or more locations. In addition, the end portion of each slit 39 may partially enter the intermediate portion 37.

  The rolling element 24 is provided with a crowning 41 (see FIG. 1) on the entire outer peripheral surface thereof. The rolling element 24 is in contact with the cylindrical raceway surface 27 formed on the inner diameter surface of the outer ring 22 and the cylindrical raceway surface 28 formed on the outer diameter surface of the inner ring 23, but the other part is in contact therewith. This part has a gap.

  As will be described later, the raceway surfaces 27 and 28 are deformed into a curved state by the action of the outer ring pressurizing means 29 and the inner ring pressurizing means 31, and the gaps are narrowed or closely contacted in the assembled state (see FIG. 4).

  The outer ring pressing means 29 is composed of a pair of left and right outer ring pressing rings 42 and an outer ring pressing member 43A (see FIGS. 1 and 4). In the illustrated case, the outer ring pressing member 43 </ b> A includes a plurality of bolts 43 and nuts 44. The inner diameter of the outer ring pressure ring 42 is formed to be approximately the same as the inner diameter of the outer ring 22, and the outer diameter of the outer ring pressure ring 42 is formed larger than the outer diameter of the outer ring 22. A tapered surface 45 having a shape that scrapes off the corner portion is formed at the inner diameter side corner portion of the opposing surface of the left and right outer ring pressure rings 42. The angle of the tapered surface 45 is set to an angle that matches the tapered surface 35 of the outer ring 22.

  With the tapered surfaces 45 of the left and right outer ring pressure rings 42 aligned with the tapered surfaces 35 of the outer rings 22, the outer diameter surface of each outer ring pressure ring 42 protrudes larger than the outer diameter surface of the outer ring 22 in the outer diameter direction.

  Between the left and right outer ring pressure rings 42, an outer ring load receiving ring 32 is fitted to the outer diameter surface of the intermediate portion 34 of the outer ring 22. The outer diameter of the outer ring load receiving ring 32 matches the outer diameter of the outer ring pressure ring 42. Further, in the state where the tapered surface 45 of each outer ring pressure ring 42 is pressed against the tapered surface 35 of the outer ring 22 (the state shown in FIG. 1), the axial direction is provided between each outer ring pressure ring 42 and the outer ring load receiving ring 32. There is a certain interval d.

  The bolt 43 is penetrated in the axial direction through a portion where each outer ring pressure ring 42 protrudes toward the outer diameter side of the outer ring 22 and the outer ring load receiving ring 32. The bolts 43 are similarly penetrated at a plurality of equally spaced positions in the circumferential direction, and nuts 44 are screwed to the ends.

  On the other hand, the inner ring pressurizing means 31 is also constituted by a pair of left and right inner ring pressurizing rings 47 and an inner ring pressing member 48A, as in the case described above. In the illustrated case, the inner ring pressing member 48 </ b> A includes a plurality of bolts 48 and nuts 49. The outer diameter of the inner ring pressure ring 47 is formed to be approximately the same as the outer diameter of the inner ring 23, and the inner diameter of the inner ring pressure ring 47 is formed larger than the inner diameter of the inner ring 23. A tapered surface 51 is formed at the corner portion on the outer diameter side of the opposing surface of the left and right inner ring pressure rings 47 so as to scrape off the corner portion. The angle of the tapered surface 51 is set to an angle that matches the tapered surface 38 of the inner ring 23.

  With the tapered surfaces 51 of the left and right inner ring pressure rings 47 overlapped with the tapered surface 38 of the inner ring 23, the inner diameter surface of each inner ring pressure ring 47 protrudes larger than the inner diameter surface of the inner ring 23 in the inner diameter direction.

  In the illustrated case, the inner ring load receiving ring 33 is fitted between the left and right inner ring pressure rings 47 on the outer diameter surface of the intermediate portion 37 of the inner ring 23. The outer diameter of the inner ring load receiving ring 33 matches the outer diameter of the inner ring pressure ring 47. Further, in the state shown in FIG. 1 in which the tapered surface 51 of each inner ring pressure ring 47 is pressed against the tapered surface 38 of the inner ring 23 and pushed most inward in the axial direction, the inner ring pressure ring 47 and the inner ring load receiving ring 33 are There is a certain distance d in the axial direction between them.

  The bolt 48 is penetrated in the axial direction through the portion where the left and right inner ring pressure rings 47 protrude toward the inner diameter side of the inner ring 23 and the inner ring load receiving ring 33. The bolts 48 are penetrated in the axial direction at a plurality of circumferentially spaced positions, and nuts 49 are screwed to the ends.

  FIG. 1 shows a temporarily assembled state in which bolts 43 and 48 are penetrated and nuts 44 and 49 are screwed. From this state, the outer ring pressure ring 42 and the inner ring pressure ring 47 are pushed toward each other by tightening the nuts 44 and 49 of the bolts 43 and 48 in order (see the white arrows in FIG. 1). . Thereby, a load in the diameter reducing direction is applied to the tapered surface 35 on the outer ring 22 side. Similarly, on the inner ring 23 side, a load in the diameter increasing direction is applied to the tapered surface 38 of the inner ring 23.

  As a result, in the outer ring 22, the portion divided by the slits 36 at both end portions 30 is reduced in diameter, and the intermediate portion 34 is also slightly reduced in diameter as the diameter is reduced. As a result, the raceway surface 27 of the outer ring 22 is elastically deformed into a curved state as a whole (see the two-dot chain line in FIGS. 4 and 5B). Similarly, also in the inner ring 23, the diameter of the portion divided by the slits 39 at both end portions 40 is increased, and the intermediate portion 37 is also slightly increased in diameter as the diameter is increased. As a result, the raceway surface 28 of the inner ring 23 is elastically deformed into a curved state as a whole (see the two-dot chain line in FIGS. 4 and 6B).

  The radius of curvature of each raceway surface 27, 28 is controlled by the tightening condition of the nuts 44, 49. Usually, the rolling element 24 is controlled so as to have a curvature radius slightly larger than the curvature radius of the crowning 41 of the rolling element 24, and the assembled state shown in FIG. 4 is obtained. In the assembled state, the gap d is smaller than the initial value, but has a constant size.

  Since the curved deformations of the raceway surfaces 27 and 28 are elastic deformations, the cylindrical roller bearing 21 is used as a bearing with the outer ring pressurizing means 29 and the inner ring pressurizing means 31 mounted thereon. The elastic deformation state of the raceway surfaces 27 and 28 is maintained by the outer ring pressurizing means 29 and the inner ring pressurizing means 31.

  In the above description, the rolling elements 24 are arranged and held at equal intervals by the cage 25. However, the rolling elements 24 are of a so-called full roller type in which the rolling elements are arranged in contact with each other without using the cage. There may be.

  The cylindrical roller bearing 21 according to the first embodiment is as described above, and the raceways 27 and 28 of the outer ring 22 and the inner ring 23 are elastically deformed into a curved state during the assembly, and the deformed state is maintained. Accordingly, the raceway surfaces 27 and 28 having a curved shape are formed without grinding. Since the radius of curvature of the raceway surfaces 27 and 28 and the crowning 41 of the rolling element 24 can be formed as a curved surface having a certain degree of curvature radius, it has self-alignment.

  A radial load acting on the shaft is transmitted to the inner ring 23 and the rolling element 24 via the inner ring load receiving ring 33 and the pair of inner ring pressure rings 47, and further, the outer ring 22, the outer ring load receiving ring 32 and the pair of outer ring pressure rings. The bearing housing is loaded via 42.

The cylindrical roller bearing 21 is used for a portion where an axial load is not applied, for example, a free side (operation side) of a main roll (a suction couch roll, a press roll, a dryer roll, a calendar roll, etc.) of a papermaking machine. The same) bearings, and free-side bearings for main shaft bearings of wind power generators.
[Embodiment 2]

  Next, Embodiment 2 shown in FIGS. 7 to 11 relates to the cylindrical roller bearing device 52. Compared to the case of the first embodiment, there is a difference in the configuration of the outer ring pressurizing means 29 and the inner ring pressurizing means 31, and these pressurizing means 29, 31 use a bearing box 53 and a shaft 54. A cylindrical roller bearing device 52 is configured instead of the bearing.

  That is, the cylindrical roller bearing device 52 according to the second embodiment includes the outer ring 22, the inner ring 23, the cylindrical roller-shaped rolling element 24 interposed between them, and the cage 25 of the rolling element 24, as in the above case. Have. Further, an outer ring pressurizing means 29 and an inner ring pressurizing means 31, an outer ring load receiving ring 32, and an inner ring load receiving ring 33, which apply a forcing force to the outer ring 22 and the inner ring 23 to bend the cylindrical raceway surfaces 27 and 28, are provided. Have.

  Since the specific configurations of the outer ring 22, the inner ring 23, and the rolling element 24 are the same as those in the first embodiment, the same reference numerals are given to the same parts in the drawings, and the description thereof is omitted. Hereinafter, the differences will be described in detail.

  The outer ring pressurizing means 29 includes a pair of left and right outer ring pressurizing rings 42 and an outer ring pressing screw ring 55 as an outer ring pressing member. The inner and outer diameters of the outer ring pressing screw ring 55 coincide with those of the outer ring pressing ring 42, and the outer ring pressing screw ring 55 is pressed against the outer end surface of the outer ring pressing ring 42 in the axial direction. Further, a male screw 56 is formed on the outer diameter surface of the outer ring pressing screw ring 55 (see FIG. 10A). On the outer end face of the outer ring pressing screw ring 55, spanner holes 57 are provided at a plurality of locations in the circumferential direction.

  A female screw 58 for screwing the left and right outer ring pressing screw rings 55 is provided on the inner diameter surface of the bearing housing 53, and the male screw 56 of each outer ring pressing screw ring 55 is screwed to the female screw 58. A spanner is hung on the spanner hole 57 and turned to press the outer ring pressing screw ring 55 against the outer end surface of the outer ring pressure ring 42.

  Further, the inner ring pressurizing means 31 includes a pair of left and right inner ring pressurizing rings 47 and an inner ring pressing screw ring 59 as an inner ring pressing member.

  The inner and outer diameters of the inner ring pressing screw ring 59 coincide with those of the inner ring pressing ring 47, and the inner ring pressing screw ring 59 is pressed against the outer end surface of the inner ring pressing ring 47 in the axial direction. Further, a female thread 60 is formed on the inner diameter surface of the inner ring pressing screw ring 59 (see FIG. 10B). On the outer end surface of the inner ring pressing screw ring 59, spanner hanging holes 61 are provided at a plurality of locations in the circumferential direction.

  A male screw 62 for screwing the left and right inner ring pressing screw rings 59 is provided on the outer diameter surface of the shaft 54, and the female screw 60 of each inner ring pressing screw ring 59 is screwed to the male screw 62 of the shaft 54. A wrench is turned around the spanner hole 61 and the inner ring pressing screw ring 59 is pressed against the outer end face of the inner ring pressure ring 47.

  By assembling as described above, as shown in FIG. 7, a gap d is formed between the outer ring pressure ring 42 and the outer ring load receiving ring 32 on the outer ring 22 side, and similarly, an inner ring addition is formed on the inner ring 23 side. A temporary assembled state in which a distance d is generated between the pressure ring 47 and the inner ring load receiving ring 33 is obtained.

  From the temporarily assembled state, a spanner is hung on each of the spanner holes 57 and 61 of the outer ring pressing screw ring 55 and the inner ring pressing screw ring 59, and the outer ring pressing ring 42 and the inner ring additional pressure are passed through these screw rings 55 and 59, respectively. The pressure ring 47 is pushed forward (see the white arrow in FIG. 7). As a result, a load in the diameter reducing direction is applied to the tapered surface 35 of the outer ring 22. Similarly, on the inner ring 23 side, a force in the diameter increasing direction is applied to the tapered surface 38 of the inner ring 23.

  As a result, in the outer ring 22, the part divided by the slits 36 at both ends is reduced in diameter, and the intermediate part 34 is also slightly reduced in diameter as the diameter is reduced. As a result, the raceway surface 27 of the outer ring 22 is elastically deformed into a curved state as a whole (see the two-dot chain line in FIG. 5B). Similarly, also in the inner ring 23, the diameter of the portion divided by the slits 39 at both end portions is increased, and the intermediate portion 37 is also slightly increased in diameter as the diameter is increased. As a result, the raceway surface 28 of the inner ring 23 is elastically deformed into a curved state as a whole (see the two-dot chain line in FIG. 6B).

  As in the case of the first embodiment, the curved state of the raceway surface is controlled by the tightening degree of the outer ring pressing screw ring 55 and the inner ring pressing screw ring 59. Usually, the rolling element 24 is controlled so as to have a radius of curvature slightly larger than the radius of curvature of the crowning 41 of the rolling element 24, and the assembled state of FIG. 11 is obtained. In the assembled state, the gap d is smaller than the initial value, but has a constant size.

  Since the curved deformation of the raceway surfaces 27 and 28 is elastic deformation, it is used as a cylindrical roller bearing device 52 including an outer ring pressurizing means 29 and an inner ring pressurizing means 31 including a bearing box 53 and a shaft 54. The curved deformation state of 27 and 28 is maintained.

  The cylindrical roller bearing device 52 according to the second embodiment is as described above. Like the cylindrical roller bearing 21 according to the first embodiment, the raceway surfaces 27 and 28 of the outer ring 22 and the inner ring 23 are assembled. Since it is elastically deformed and maintained in a curved state in the middle, the track surfaces 27 and 28 having a curved shape are formed without grinding. Since the radius of curvature of the raceway surfaces 27 and 28 and the crowning 41 of the rolling element 24 can be formed as a curved surface having a certain degree of curvature radius, it has self-alignment.

  The cylindrical roller bearing device 52 can be used in the same manner as in the case of the above-described portion where an axial load is not applied, for example, a main roll (a suction couch roll, a press roll, a dryer roll, a calendar roll, etc.) of a papermaking machine. There are free-side bearings, free-side bearings for main shaft bearings of wind power generators, and the like.

21 cylindrical roller bearing 22 outer ring 23 inner ring 24 rolling element 25 cage 27 raceway surface 28 raceway surface 29 outer ring pressurizing means 30 end 31 inner ring pressurizing means 32 outer ring load receiving ring 33 inner ring load receiving ring 34 intermediate part 35 tapered surface 36 Slit 37 Intermediate portion 38 Tapered surface 39 Slit 40 End portion 41 Crowning 42 Outer ring pressure ring 43A Outer ring pressure member 43 Bolt 44 Nut 45 Tapered surface 47 Inner ring pressure ring 48A Inner ring pressure member 48 Bolt 49 Nut 51 Tapered surface 52 Cylindrical roller bearing Device 53 Bearing box 54 Shaft 55 Outer ring pressing screw ring 56 Male screw 57 Spanner hanging hole 58 Female screw 59 Inner ring pressing screw ring 60 Female screw 61 Spanner hanging hole 62 Male screw

Claims (11)

  In a cylindrical roller bearing in which a single-row cylindrical roller-shaped rolling element is interposed between the raceway surfaces of the outer ring and the inner ring, and the rolling element is crowned, the outer ring and the inner ring respectively extend in the axial direction from the intermediate portion. Both ends of the outer ring are formed on the outer diameter surface of the outer ring, and the inner ring is formed with a tapered surface on the inner diameter surface of the both ends. The above-described axial slits are provided, and an outer ring pressurizing unit and an inner ring pressurizing unit are provided for each of the outer ring and the inner ring, and the outer ring pressurizing unit is fitted to each tapered surface of the outer ring. A pressure ring and an outer ring pressing member that presses each pressure ring in a direction approaching each other, and the inner ring pressure means includes a pair of inner ring pressure rings fitted to each tapered surface of the inner ring and each Reciprocating pressure ring The inner ring pressing member that presses in the approaching direction, and the outer ring pressing member and the inner ring pressing member are elastically deformed in the radial direction by operating the outer ring pressing member and the inner ring pressing member from the outside, and the races of the outer ring and the inner ring. A cylindrical roller bearing characterized in that a surface is curved along the crowning of the rolling element, and the curved state is maintained by the pressing members.   The outer ring pressing member is composed of a plurality of bolts and nuts, and the bolts are penetrated through the outer ring presser ring on both sides with a larger diameter than the outer rings, and the nuts are screwed to the penetrating bolt ends. The cylindrical roller bearing according to claim 1, wherein the outer ring pressure ring is pressed against the tapered surface of the outer ring by tightening a nut so as to pressurize the outer ring in a reduced diameter direction.   The cylindrical roller bearing according to claim 1, wherein the outer ring pressure ring has a tapered surface that matches the tapered surface of the outer ring.   On the outer diameter surface of the outer ring, an outer ring load receiving ring is interposed between the large diameter portions of the outer ring pressure rings on both sides at a predetermined interval in the axial direction, and the bolts constituting the outer ring pressure means are The cylindrical roller bearing according to any one of claims 1 to 3, wherein the cylindrical roller bearing is also passed through an outer ring load receiving ring.   The inner ring pressing member is constituted by a plurality of bolts and nuts, and the bolts are passed through portions of the inner ring pressure rings on both sides that are smaller in diameter than the inner ring inner diameter, and the nuts are screwed to the penetrating bolt ends, The cylindrical roller bearing according to any one of claims 1 to 4, wherein the inner ring pressure ring is pressed against the tapered surface of the inner ring to pressurize the inner ring by tightening the nut.   The cylindrical roller bearing according to claim 5, wherein the inner ring pressure ring has a tapered surface that matches a tapered surface of the inner ring.   On the inner diameter surface of the inner ring, an inner ring load receiving ring is interposed between the small diameter portions of the inner ring pressure rings on both sides at a predetermined interval in the axial direction, and a bolt constituting the inner ring pressure means is the inner ring load. The cylindrical roller bearing according to claim 5, wherein the cylindrical roller bearing is also passed through the receiving ring.   The cylindrical roller according to any one of claims 1 to 6, wherein a radius of curvature of the raceway surface of the outer ring and the inner ring after being curved is equal to or larger than a radius of curvature of the crowning of the cylindrical roller. bearing.   Cylindrical rollers in which a single row cylindrical roller-shaped rolling element is interposed between the raceway surfaces of the outer ring and the inner ring, the rolling element is crowned, the outer ring is housed in a bearing box, and the inner ring is fitted to a shaft. In the bearing device, each of the outer ring and the inner ring has left and right end portions extending in the axial direction from the intermediate portion, and the outer ring has tapered surfaces on the outer diameter surfaces of both end portions thereof, and the inner ring has tapered surfaces on inner diameter surfaces of both end portions thereof. One or more axial slits are provided at both ends of the outer ring and the inner ring formed with the tapered surface, and an outer ring pressurizing unit and an inner ring pressurizing unit are provided for each of the outer ring and the inner ring, The outer ring pressurizing means includes a pair of outer ring pressurizing rings fitted to the respective tapered surfaces of the outer ring and an outer ring pressing member that presses each pressurizing ring in a direction approaching each other. Each tape of the inner ring A pair of inner ring pressure rings fitted to the surface and an inner ring pressing member that presses each pressure ring in a direction approaching each other, and the outer ring pressing member is formed on the inner surface of the bearing box, Members are screw-coupled to the outer diameter surfaces of the shafts, respectively, and both ends of the outer ring and the inner ring are elastically deformed in the radial direction by operating the outer ring pressing member and the inner ring pressing member from the outside. A cylindrical roller bearing device characterized in that a surface is curved along the crowning of the rolling element, and the curved state is maintained by the pressing members.   The outer ring pressing member and the inner ring pressing member are respectively composed of an outer ring pressing screw ring and an inner ring pressing screw ring. The outer ring pressing screw ring has a male screw on its outer diameter surface, and the inner ring pressing ring has a female screw on its inner diameter surface. The cylindrical roller bearing device according to claim 9. On the outer diameter surface of the outer ring, an outer ring load receiving ring is interposed between the large diameter portions of the outer ring pressure rings on both sides at a predetermined interval in the axial direction. The cylindrical roller bearing device according to claim 9 or 10, wherein an inner ring load receiving ring is interposed between the small diameter portions of the pressure ring at a predetermined interval in the axial direction.

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