JP2009097525A - Rolling bearing with cage - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To realize a structure of not violently colliding mutual adjacent these respective cage elements 21c and 21c, when the mutual respective cage elements 21c and 21c constituting a divided cage 20b are displaced in the circumferential direction in operation. <P>SOLUTION: In a state of forming the whole in a conical cylindrical shape by combining a plurality of cage elements 21c and 21c in series in the circumferential direction, the relationship between the total H of the whole clearances in the circumferential direction of mutual opposed circumferential directional end surfaces of the adjacent respective cage elements 21c and 21c and the peripheral length L of a pitch circle P<SB>21c</SB>of this cage, is set to 0<H≤0.001L. The problem is solved thereby. <P>COPYRIGHT: (C)2009,JPO&INPIT

Description

  A rolling bearing with a cage according to the present invention is a rotating shaft coupled and fixed to a rotation center of a rotor (a rotating body with blades such as blades) constituting a wind power generator, or between the rotating shaft and a generator. Is used to rotatably support the rotating shaft constituting the transmission provided on the wind turbine generator housing.

  In recent years, wind power generation, which is a power generation method using natural energy, has been attracting attention for the purpose of improving the global environment by reducing carbon dioxide. 11 to 12 show a structure described in Patent Document 1 as an example of a conventional structure of a wind turbine generator. FIG. 11 is an overall configuration diagram of a propeller-type wind power generator. The windmill 1 includes a blade 2 that takes in the kinetic energy of the wind, a rotor 3, a housing 4, and a tower 5 for installing the housing 4 at a height position sufficiently separated from the ground (for example, about 40 m). In addition, as shown in FIG. 12, the housing 4 contains a rotating shaft 6, rolling bearings 7, 7, a speed increasing gear 8, and a generator 9. The rotating shaft 6 includes rolling bearings 7, 7 is rotatably attached to the housing 4. Then, the rotational force taken by the blade 2 from the kinetic energy of the wind is transmitted to the rotating shaft 6, further accelerated by the speed increaser 8, and then transmitted to the generator 9 for power generation.

  Roller bearings or the like are used as bearings used in the transmissions such as the rolling bearings 7 and 7 and the speed increaser 8 constituting the wind turbine 1 in order to support a large radial load. As described above, the roller bearing used in the wind power generator is provided at a high place such as above the steel tower, and it is difficult to perform maintenance work such as replacement. For this reason, it is not preferable that the roller bearing reaches the end of its service life early. Therefore, in order not to perform the maintenance work of the wind power generator for a long period (at least 20 years, preferably a longer period), the durability of the roller bearing should be sufficiently secured. Is desired.

FIG. 13 shows a structure of a conventionally known tapered roller bearing 10 as an example of such a roller bearing. The tapered roller bearing 10 includes an outer ring 11, an inner ring 12, a plurality of tapered rollers 13 and 13, and a cage 14.
Of these, the outer ring 11 is provided with a conical concave outer ring raceway 15 in an intermediate portion of the inner peripheral surface.
Further, the inner ring 12 is provided with a conical convex inner ring raceway 16 in the middle part of the outer peripheral surface. Further, of the outer peripheral surface both ends of the inner ring 12, a large-diameter side flange portion 17 is provided at the large-diameter side end portion (left end portion in FIG. 13) and a small-diameter side end portion is provided at the small-diameter side end portion (right end portion in FIG. 13). The flanges 18 are formed respectively.
Further, the plurality of tapered rollers 13 and 13 have a tapered outer peripheral surface. Further, it is rotatably provided between the outer ring raceway 15 and the inner ring raceway 16 while being held by a cage 14 described below.
The retainer 14 is formed in a conical cylinder shape, and has a plurality of pockets 19 and 19 formed at equal intervals in the circumferential direction. The tapered rollers 13 and 13 are held so as to freely roll.

As such a retainer 14, a so-called integrated retainer is used which is generally composed of a single member having a generally conical cylindrical shape. However, when used in an environment that receives a large load such as a main shaft of the wind power generator or the like, the tapered roller bearing 10 is increased in size, and the retainer 14 constituting the tapered roller bearing 10 is also increased in size. For this reason, the capacity of the manufacturing apparatus is exceeded, and it may be difficult to manufacture the integrated cage 14 as described above. Moreover, even if it can be manufactured, if the capacity of the assembling apparatus is exceeded, it may be difficult to perform the assembling work.
Therefore, when the tapered roller bearing 10 is enlarged as described above, a so-called split cage may be used instead of the integral cage. FIG. 14 is a schematic diagram for explaining the structure of the split type cage. The divided cage 20 has a conical cylindrical shape as a whole by combining a plurality of cage elements 21 and 21 each formed in an arc shape in series in the circumferential direction. Each of the cage elements 21 and 21 constituting such a split cage 20 is smaller than the size of the integral cage. For this reason, the possibility of exceeding the capability of the manufacturing apparatus and the assembly apparatus is small.

Patent Document 1 describes the structure of a split cage. FIG. 15 is a schematic diagram for explaining the structure of this conventionally known split type cage. The split cage 20a has a conical cylindrical shape as a whole by combining a plurality of cage elements 21a, 21a, each formed in an arc shape, in series in the circumferential direction without being coupled. And the said split type holder | retainer 20a is a state which opposed each of the circumferential direction end surfaces of each adjacent holder | retainer element 21a, 21a in the state which arranged each said holder | retainer element 21a, 21a in series in the circumferential direction. There is a gap between the end faces. As shown in FIG. 15, the total length of the gaps is such that the first retainer element 21a and the last retainer element 21a are arranged in a state where the retainer elements 21a and 21a are arranged without gaps. It becomes equal to the length of the gap X between the other end surface. In the invention described in Patent Document 1, the length of such a gap X is restricted to a range of 0.15 to 1% of the pitch circle P _21a of the split cage 20a.
As shown in FIG. 16, each of the cage elements 21 a and 21 a includes a pair of rim portions 22 a and 22 a that are provided at both ends in the axial direction and each have a circular arc shape. Further, the rim portions 22a and 22a are coupled to each other by a plurality of column portions 23a and 23a. Further, the tapered rollers 13 and 13 are rolled around a portion surrounded by the inner side surfaces of the rim portions 22a and 22a and the circumferential side surfaces of the column portions 23a and 23a adjacent in the circumferential direction. Pockets 19a and 19a are provided for free holding. Out of the inner surfaces of these pockets 19a, 19a, both ends in the circumferential direction are used as guide surfaces for the pillar portions 23a, 23a for guiding the rolling surfaces of the tapered rollers 13, 13.

  In the case of such a split cage 20a, the length of the gap X is restricted in consideration of thermal expansion in the circumferential direction of the cage elements 21a and 21a due to a temperature rise inside the bearing. When the temperature inside the bearing rises, the cage elements 21a and 21a constituting the split cage 20a thermally expand. Due to this thermal expansion, the difference between the gap X and the total amount of thermal expansion in the circumferential direction of all the cage elements 21a, 21a remains as a circumferential gap. However, when the temperature inside the bearing during operation is not so high, the sum of the thermal expansion amounts becomes smaller than the gap X, and a gap close to the gap X remains in the circumferential direction. Thus, if a relatively large gap remains in the circumferential direction, the amount of displacement of each of the cage elements 21a, 21a in the circumferential direction during operation increases, and the circle between adjacent cage elements 21a, 21a increases. The circumferential end faces collide strongly. For this reason, there is a possibility that abnormal noise is generated or a large stress is generated due to the collision, and the cage elements 21a and 21a may be damaged with long-term use.

  Further, the split type cage described in Patent Document 2 is similar to the split type cage 20a described in Patent Document 1 above, and includes a plurality of cage elements 21b and 21b each formed in an arc shape. By combining them in series in the circumferential direction, the whole is formed into a conical cylinder shape. However, the split-type cage described in Patent Document 2 mechanically couples the cage elements 21b and 21b adjacent to each other. FIGS. 17 to 18 are perspective views showing the circumferential ends of the cage elements 21b and 21b for explaining the coupling state. Each of these cage elements 21b and 21b has a joint convex portion 24 formed at one end portion in the circumferential direction and a joint concave portion 25 engaged with the joint convex portion 24 at the other end portion. And these joining convex part 24 and joining recessed part 25 are engaged as shown in FIG. 18, and also welding is carried out by ultrasonic welding, and it couple | bonds together.

  In the case of such a split type cage described in Patent Document 2, no circumferential gap is provided between the adjacent cage elements 21b, 21b. For this reason, like the above-mentioned split type cage 20a of Patent Document 1, the cage elements 21a, 21a adjacent to each other when the cage elements 21a, 21a are displaced in the circumferential direction during the operation of the bearing. There is no problem that the opposing circumferential end faces collide violently. However, when the cage elements 21b and 21b are thermally expanded due to a temperature rise inside the bearing, the following problems can be considered. When the temperature inside the bearing rises, each of the cage elements 21b and 21b tends to thermally expand in all directions. However, the cage elements 21b and 21b are mechanically coupled, and no gap is provided between the circumferential end faces of the cage elements 21b and 21b facing each other. For this reason, both end surfaces in the circumferential direction of the cage elements 21b and 21b cannot thermally expand in the direction of expanding in the circumferential direction, and the portion that cannot be thermally expanded in the circumferential direction is divided into the cages. It appears as a deformation of the guide surface of each pocket of the elements 21b and 21b. The deformation restrains the rolling elements held by these pockets, which may cause abnormal noise, increase torque, etc., and damage the cage elements 21b and 21b. It is done.

German Patent Application No. 10246825 JP 2004-125088 A

  In the present invention, in view of the circumstances as described above, each cage element constituting this cage is displaced in the circumferential direction during bearing operation, so that each of these neighboring cage elements collide violently. The invention was invented to realize a structure that can prevent the occurrence of abnormal noise or breakage to ensure durability, and that can prevent distortion of the inner surface of the pocket when the temperature rises.

A rolling bearing with a cage that is a subject of the present invention includes an inner ring, an outer ring, a plurality of rolling elements, and a cage.
Of these, the inner ring has an outer ring raceway on the outer peripheral surface.
The outer ring has an outer ring raceway on the inner peripheral surface.
Each rolling element is provided between the outer ring raceway and the inner ring raceway so as to roll freely.
Further, the cage is a so-called split type cage, in which a plurality of cage elements, each formed in an arc shape, are combined in series in the circumferential direction so as to be cylindrical or conical as a whole. In addition, each of these cage elements is formed by connecting a pair of rim portions, each having an arc shape, provided at both ends in the axial direction by a plurality of column portions. Further, a portion surrounded by the inner edge of both the rim portions and the circumferential side edge of each column portion adjacent in the circumferential direction is used as a pocket for holding the rolling elements in a freely rollable manner. .

  In particular, in the rolling bearing with a cage of the present invention, the cage elements are not mechanically coupled, but are combined in series in the circumferential direction to form a cylindrical or conical cage. The relationship between the total gap H in the circumferential direction between the circumferential end faces facing each other of the adjacent cage elements and the circumferential length L of the pitch circle of this cage is H ≦ 20 ° C. at room temperature (20 ° C.). It is 0.001L. That is, in the state where each of the above cage elements is combined in series in the circumferential direction without any gap with respect to a certain cage element, the circumferential direction of the leading cage element The total value H, which is the distance in the circumferential direction between the one end surface and the other circumferential end surface of the last cage element, is a positive value not more than 0.001 times the circumferential length L.

When the present invention as described above is implemented, preferably, the relationship between the total value H and the circumferential length L is 0 <H ≦ 0.001L.
Further, when the invention described in claims 1 and 2 is carried out, preferably, as described in claim 3, the displacement of each rolling element in each pocket in the radial direction of the cage. Is provided between the inner surface of each pocket and the rolling surface of each of the rolling elements.
In carrying out the invention described in claims 1 to 3, preferably, as described in claim 4, the outer peripheral surface of the cage and the guide peripheral surface which is the inner peripheral surface of the outer ring. Or an outer ring guide structure for positioning the cage in the radial direction by sliding contact with or in close proximity to each other, or an inner circumferential surface of the cage and a guide circumferential surface which is an outer circumferential surface of the inner ring. A raceway surface guide structure, which is one of the inner ring guide structures for positioning the cage in the radial direction by making it face each other, is adopted.

Further, when the invention described in claim 4 is implemented, preferably, as described in claim 5, each of the guide peripheral surfaces (in the case of an outer ring guide structure, the inner peripheral surface of the outer ring, the inner ring In the case of the guide structure, the peripheral surface of the retainer that is in sliding contact or close proximity to the outer peripheral surface of the inner ring is a guide portion provided in a part of each column portion. In addition, a notch for holding or supplying the lubricant is formed in a part of the guide.
Moreover, when implementing the invention described in the first to fifth aspects, preferably, as described in the sixth aspect, the guide peripheral surface side of the circumferential side surfaces of the column portions is arranged. A guide surface that restricts the radial position of the cage based on the engagement with the rolling surface of each rolling element is provided in the vicinity.
Moreover, when implementing the invention described in the fourth to sixth aspects, preferably, as described in the seventh aspect, the position in the radial direction is a part of the circumferential side surface of each column part. A locking projection is formed on a portion opposite to the guide circumferential surface. Further, the distance in the circumferential direction between the leading edges of the locking projections facing each other in each pocket is made smaller than the outer diameter of each rolling element.
Moreover, when implementing the invention described in claims 1 to 7, preferably, as described in claim 8, the axial end portion protrudes from the circumferential end surface of each of the cage elements. Convex shape.
Further, when the invention described in claims 1 to 8 is carried out, preferably, each of the rolling elements is a roller as described in claim 9.
In carrying out the inventions described in the first to ninth aspects, preferably, the cage is synthesized with aromatic nylon, polyetheretherketone, polyphenylene sulfide, etc., as described in the tenth aspect. Made of resin.

The rolling bearing with a cage of the present invention configured as described above is a gap provided so that the gap between the circumferential end surfaces of the adjacent cage elements constituting the cage is not too large. Is regulated. By regulating the circumferential clearance in this way, the temperature inside the bearing does not increase during the operation of the bearing, and each of the cage elements can be used even when the amount of thermal expansion in the circumferential direction is small. It is possible to prevent the cage element from being greatly displaced in the circumferential direction, and to prevent the opposed circumferential end faces of these adjacent cage elements from colliding violently.
In addition, when the temperature inside the bearing rises during operation of the bearing and the cage elements thermally expand, the circumferential end surfaces of the cage elements are provided with the gap. Since thermal expansion is possible in the direction of expansion in the circumferential direction, the amount of deformation of the guide surfaces of the pockets and the like can be reduced compared to the case where the cage elements adjacent in the circumferential direction are coupled to each other. Can do. For this reason, the guide surfaces of these pockets prevent the noise and the increase in torque that occur when the rolling elements that are held are constrained, improving the durability of each cage element, As a result, it is possible to improve the durability of the rolling bearing incorporating these cage elements.

Further, as described in claim 3, between the inner surface of each pocket and the rolling surface of each rolling element, the displacement of each of the rolling elements in each pocket in the radial direction of the cage is changed. If the structure is provided with a permissible radial gap, the inner surface of each pocket restrains each ball even if each cage element thermally expands radially outward as the temperature inside the bearing increases. Can be prevented.
Further, as described in claim 4, by adopting a raceway surface guide structure of either the outer ring guide structure or the inner ring guide structure, it is possible to prevent the cage from being inclined during the operation of the bearing. For this reason, it can prevent that the inner surface of each said pocket and the rolling surface of each said rolling element rub against each other strongly, and it can also prevent that rotation resistance becomes large. In particular, in the case of the inner ring guide structure, the temperature inside the bearing rises and does not prevent the cage elements from thermally expanding radially outward. For this reason, it is possible to prevent excessive internal stress from being generated in each of the cage elements, and to prevent the inner surfaces of the pockets from being distorted.
In addition, as described in claim 5, the guide portion provided on a part of each column portion with a peripheral surface of the cage that is in sliding contact with or close to the guide peripheral surface of either the outer ring or the inner ring. If a notch portion for holding or supplying the lubricant is formed in a part of the guide portion, the lubricity inside the bearing can be improved and the temperature inside the bearing can be prevented from rising. Further, the contact area between the guide portion and the guide peripheral surface can be reduced by providing the notch portion. For this reason, the bearing torque during operation can be reduced, and heat generation due to friction can also be reduced.
In addition, as described in claim 6, among the circumferential side surfaces of each of the pillar portions, the guide peripheral surface (in the case of the outer ring guide structure, the inner peripheral surface of the outer ring, in the case of the inner ring guide structure, the above described By providing a guide surface for restricting the radial position of the cage based on the engagement with the rolling surface of each rolling element at a portion near the outer peripheral surface) side of the inner ring, Even in the case of thermal expansion, the guide structure of the cage can be shifted during operation from the inner ring guide structure to the rolling element guide structure or from the rolling element guide structure to the outer ring guide structure. For this reason, the radial positioning of the cage is not prevented by thermal expansion.
In addition, as described in claim 7, a holding protrusion is formed on a part of the circumferential side surface of each of the column portions at a position opposite to the guide circumferential surface in the radial direction. Even before the rolling element and each rolling element are assembled between the inner peripheral surface of the outer ring and the outer peripheral surface of the inner ring, the respective rolling elements from the respective pockets on the radial side provided with the respective locking projections. It can be prevented from falling off. For this reason, the assembly work of a rolling bearing becomes easy.
Further, as described in claim 8, if the circumferential end face of each of the cage elements is formed in a convex shape with the axial center portion protruding, the cage elements are incorporated when the cage elements are assembled. Since the circumferential end face of the element can be elastically deformed in the circumferential direction, the assembling work can be easily performed. In addition, even when the adjacent circumferential end surfaces of the adjacent cage elements collide with each other during the operation of the bearing, the circumferential end surfaces of the cage elements are elastic in the circumferential direction. Because it can be deformed, the impact can be reduced. Furthermore, even after the gap has disappeared due to the temperature rise, the thermal expansion can be absorbed.
Further, as described in claim 9, if the rolling elements are rollers, the load capacity of the bearing can be increased.
Further, as described in claim 10, if the cage is made of a synthetic resin such as aromatic nylon, polyetheretherketone, polyphenylene sulfide, etc., it is lightweight, self-lubricating, low friction characteristics, corrosion resistance, and quietness. It is possible to obtain a cage excellent in the above points. Such a cage made of synthetic resin can be manufactured by injection molding suitable for mass production.

[First example of embodiment]
1-4 show a first example of an embodiment of the present invention corresponding to claims 1 to 5 and 7 to 10. The feature of the rolling bearing with a cage of this example is that the structure of the cage constituting the rolling bearing is devised. The structure and operation other than this characteristic portion are the same as those of conventionally known rolling bearings including the rolling bearing shown in FIG. For this reason, the overlapping description will be omitted or simplified, and the following description will focus on the features of this example.

FIG. 1 is a schematic diagram for explaining the structure of a split-type cage constituting the rolling bearing with a cage of this example. As shown in FIG. 1, each of the split cages 20b includes a plurality of cage elements 21c and 21c each formed by injection molding a synthetic resin such as aromatic nylon, polyetheretherketone, polyphenylene sulfide, The whole is configured in a cylindrical shape or a conical cylindrical shape by combining in series in the circumferential direction without mechanically coupling. Also, in this combined state, the total H of all the gaps existing between the opposing circumferential end faces of the adjacent cage elements 21c, 21c, and the pitch circle P _{21c of} this cage. The relationship with the circumferential length L is 0 <H ≦ 0.001L. In FIG. 1, the length of the gap between one end surface of the first cage element 21c and the other end surface of the last cage element 21c in a state where the cage elements 21c and 21c are arranged without gaps. The above H is shown.

Each of the cage elements 21c and 21c is formed in an arc shape as shown in FIGS. Further, a pair of rim portions 22b, 22b provided at both ends in the axial direction, each having an arc shape, are coupled by a plurality of column portions 23b, 23b. In addition, the tapered rollers 13 and 13 can freely roll around a portion surrounded by the inner side surfaces of the rim portions 22b and 22b and the circumferential side surfaces of the column portions 23b and 23b adjacent in the circumferential direction. The pockets 19b and 19b are used for holding. Of the inner surfaces of the pockets 19b and 19b, the side surfaces in the circumferential direction of the column portions 23b and 23b serve as guide surfaces for guiding the rolling surfaces of the tapered rollers 13 and 13, respectively.
Further, a radial gap A that allows the tapered rollers 13 and 13 in the pockets 19b and 19b to be displaced in the radial direction of the split type retainer 20b is provided with an inner surface of each of the pockets 19b and 19b and the tapered shape. It is provided between the rolling surfaces of the rollers 13 and 13.
Further, among the pillar portions 23b and 23b, guide portions 26 and 26 are provided at the radially inner end portion of the split cage 20b, and the radially inner side surfaces of the guide portions 26 and 26, The inner ring guide structure is configured such that the guide type circumferential surface 27 which is the outer peripheral surface of the inner ring 12 is slidably contacted or closely opposed, thereby positioning the split type cage 20b in the radial direction. Moreover, each of these guide portions 26, 26, the distance B ₁ in the circumferential direction of the leading edge between the respective guide portions 26, 26 in the circumferential direction face each other, corresponding each cone in axial position The rollers 13 and 13 are smaller than the outer diameter D (B ₁ <D).
Further, notches 28 and 28 for holding or supplying the lubricant are formed at the axially central portion of the split type retainer 20b of the guide portions 26 and 26, respectively.
Further, locking projections 29 and 29 are respectively formed at both end portions in the axial direction of the portions near the outer diameter of the side surfaces in the circumferential direction of the column portions 23b and 23b. Further, the distance C ₁ in the circumferential direction between the leading edges of the locking projections 29 and 29 facing each other in the pockets 19b and 19b is set to the tapered rollers 13 corresponding to the axial positions. 13 is smaller than the outer diameter D (C ₁ <D).
Each of the cage elements 21c and 21c shown in FIGS. 1 to 3 has a flat end surface in the circumferential direction of the cage elements 21c and 21c. On the other hand, as shown in the schematic diagram of FIG. 4, by curving the column portion 23b located at the circumferential end of each of the cage elements 21c and 21c so as to protrude to the opposite side of the pocket 19b, The shape of the circumferential end face of each of the cage elements 21c, 21c may be a convex shape with the central portion in the axial direction protruding.

As described above, the rolling bearing with a retainer of the present example does not mechanically connect the adjacent retainer elements 21c and 21c constituting the split retainer 20b, and the retainer elements 21c, The total H of all the gaps between the circumferential end faces 21c facing each other is regulated. Therefore, when the rolling bearing with a cage is operated, the temperature inside the rolling bearing does not increase, and even when the thermal expansion amount in the circumferential direction of the cage elements 21c and 21c is small, the rolling bearing has a large circumferential direction. Since there is no gap, the amount of displacement of each of these cage elements 21c, 21c in the circumferential direction can be kept small. For this reason, it can prevent that the circumferential direction end surfaces which these adjacent cage elements 21c and 21c oppose face each other severely.
Further, when the temperature inside the bearing rises during the operation of the rolling bearing and the cage elements 21c and 21c are thermally expanded, the circumferential ends of the cage elements 21c and 21c As long as H is provided, thermal expansion can be performed in a direction extending in the circumferential direction. For this reason, the internal stress which arises in each said retainer element 21c, 21c can be made small compared with the case where each said retainer element adjacent to the circumferential direction is mechanically couple | bonded. In addition, the amount of deformation of the guide surfaces of the pockets 19b and 19b can be kept small. For this reason, the guide surfaces of the pockets 19b and 19b prevent the abnormal noise and the increase in torque that are generated when the tapered rollers 13 and 13 held by the guides are restrained. It is possible to improve the durability of the cage elements 21c and 21c, and thus the durability of the bearing incorporating these cage elements 21c and 21c.

Further, the split cages of the tapered rollers 13 and 13 in the pockets 19b and 19b are provided between the inner surfaces of the pockets 19b and 19b and the rolling surfaces of the tapered rollers 13 and 13, respectively. Since the radial gap A that allows displacement in the radial direction of 20b is provided, even when the temperature inside the bearing rises and the split cage 20b thermally expands radially outward, the pockets 19b, It is possible to prevent the inner surface of 19b from constraining the tapered rollers 13, 13.
Further, the radial inner surface of each guide portion 26, 26 of the split type retainer 20b and the guide peripheral surface 27 are brought into sliding contact or close proximity to each other, thereby positioning the split type retainer 20b in the radial direction. Since the inner ring guide structure is used, it is possible to prevent the split cage 20b from being inclined during the operation of the bearing. For this reason, the inner peripheral edge of each said pocket 19b, 19b and the rolling surface of each said tapered roller 13,13 do not mutually rub strongly, and a rotation resistance does not become large. Further, when the temperature inside the rolling bearing rises, it does not prevent the cage elements 21c, 21c from thermally expanding outward in the radial direction. For this reason, it is possible to prevent an excessive internal stress from being generated in each of the cage elements 21c and 21c.
Further, since notches 28 and 28 for holding or supplying a lubricant are formed in a part of each of the guide portions 26 and 26 which are in sliding contact with or close to the guide peripheral surface 27, lubrication inside the bearing is performed. Thus, the temperature inside the bearing can be prevented from rising. Further, the contact area between the radially inner side surfaces of the guide portions 26 and 26 and the guide peripheral surface 27 can be reduced by the provision of the notch portions 28 and 28. For this reason, the bearing torque during operation can be kept small, and heat generated by friction can be reduced. Further, each of the guide portions 26 and 26, the distance B ₁ in the circumferential direction of the leading edge between the respective guide part in the circumferential direction face each other, corresponding each tapered roller at an axial position 13, Since the diameter of each of the tapered rollers 13 and 13 is smaller than the diameter D of the inner ring 12, the tapered rollers 13 and 13 are assembled in the pockets 19b and 19b and before being assembled around the inner ring 12. Can be prevented from falling inward in the radial direction from the pockets 19b and 19b.
Also, the locking projections 29, 29 formed at the axial end portions of the portions of the pillar portions 23b, 23b in the circumferential direction at positions opposite to the guide circumferential surface 27 in the radial direction. Since the distance C ₁ in the circumferential direction between the tip edges of each of the tapered edges 13 is smaller than the outer diameter D of each of the tapered rollers 13 and 13 corresponding to the axial position (C ₁ <D), each of these tapered rollers is Even after being assembled in the pockets 19b and 19b and before being assembled on the inner diameter side of the outer ring 11, the tapered rollers 13 and 13 can be prevented from falling off from the pockets 19b and 19b in the radially outward direction. . As a result, the assembly work of the rolling bearing with cage can be facilitated.
In addition, as shown in FIG. 4 above, by making the shape of the circumferential end face of each of the cage elements 21c into a convex shape in which the central portion in the axial direction protrudes, when incorporating these cage elements 21c, Assembling work can be easily performed by elastically deforming the protruding portion of the circumferential end face of each cage element 21c in the circumferential direction. Further, even when the adjacent circumferential end faces of the adjacent cage elements 21c collide with each other during the operation of the rolling bearing, the protruding portions of the circumferential end faces of the cage elements 21c are thus provided. Can be elastically deformed in the circumferential direction, so that the impact can be reduced. Furthermore, even after the gap disappears when the temperature rises, it is possible to absorb thermal expansion and prevent the pockets 19b and 19b from being distorted.
Each of the cage elements 21c and 21c is formed by injection molding a synthetic resin of aromatic nylon, polyetheretherketone, or polyphenylene sulfide, so that it is lightweight, self-lubricating, low friction characteristics, corrosion resistance, A cage excellent in quietness can be obtained. Moreover, since it can be formed by injection molding in this way, it is suitable for mass production.

The position where the notch portions 28 and 28 are formed in the previous period is not limited to the central portion in the axial direction of the guide portions 26 and 26 as in this example. Further, as in this example, the guide portions 26 and 26 may be formed not only at one location but also at a plurality of locations such as axial end portions.
Further, the locking projections 29 and 29 are not limited to the structures formed at both ends in the axial direction of the portions near the outer diameter of the column portions 23b and 23b as in this example, but are continuous in the axial direction. You may make it the latching protrusion of the shape.
In this example, the tapered rollers 13 and 13 are used as rolling elements, but the same effect can be obtained even when applied to a roller bearing using a cylindrical roller or a needle.

[Second Example of Embodiment]
FIGS. 5-6 has shown the 2nd example of embodiment of this invention corresponding to Claims 1-10. Each cage element 21d constituting the split type cage of the rolling bearing with cage of the present example is a guide circumferential surface that is an outer circumferential surface of the inner ring 12 among both circumferential side surfaces of the column portions 23c and 23c. 27, guide surfaces 30 and 30 are provided for restricting the radial position of the split cage based on the engagement of the tapered rollers 13 and 13 with the rolling surfaces.

  According to such a rolling bearing with a retainer of this example, the split retainer is in a state where the inner ring guide structure is not established due to thermal expansion, centrifugal force, or the like (the radially inner surface of each guide portion 26, 26 and When the distance to the guide circumferential surface 27 becomes large and the sliding surface or the state where the guide circumferential surface 27 cannot be opposed to each other), the guide surfaces 30 and 30 are engaged with the rolling surfaces of the tapered rollers 13 and 13. Thereby, the displacement to the radial direction outer side of the said split type holder can be controlled. Displacement of the split cage inward in the radial direction is restricted by the cage elements 21d sticking in the circumferential direction. In this way, it is possible to shift from the inner ring guide structure to the rolling element guide structure during operation.

Further, in this example, the inner ring guide structure is adopted, but the respective locking projections 29, 29 formed on the outer diameter side portions of the side surfaces in the circumferential direction of the respective column portions 23c, 23c, and the tapered rollers 13, The size of the radial gap L ₁ (not shown) with the 13 rolling surfaces and the size L ₂ of the distance between the radial inner side surfaces of the guide portions 26 and 26 and the guide peripheral surface 27. (Not shown) When the relationship with L ₁ <L ₂ is established, the rolling element guide structure in which the radial displacement of the split cage is always restricted by the tapered rollers 13 and 13 is used. I can do it.
Since the configuration and operation of the other parts are the same as those in the first example of the above-described embodiment, redundant description is omitted.

[Third example of embodiment]
FIGS. 7-8 has shown the 3rd example of embodiment of this invention corresponding to Claims 1-5, 7-10. The cage element 21e constituting the split type cage of the rolling bearing with cage of this example has a guide portion at the outer end portion in the radial direction of the split type cage among the pillar portions 23d and 23d. 26a and 26a are provided. And the radial direction outer surface of these guide parts 26a and 26a and the guide peripheral surface 27a which is the inner peripheral surface of the outer ring | wheel 11 are slidably contacted or adjoined, and positioning with respect to the radial direction of the said split type holder | retainer is aimed at. The outer ring guide structure is adopted. Moreover, each of these guide portions 26a, 26a, these respective guide portions 26a of the circumferential direction face each other, the distance B ₂ in the circumferential direction of the leading edge between the 26a, the tapered rollers corresponding in axial position Is smaller than the outer diameter D (B ₂ <D).
In addition, notches 28a and 28a for holding or supplying the lubricant are formed in the axially central portions of the divided cages of the guide portions 26a and 26a.
Further, locking projections 29a and 29a are formed at both axial ends of the radially inward portions of the circumferential side surfaces of the column portions 23d and 23d, respectively. In addition, the distance C ₂ in the circumferential direction between the end edges of the locking projections 29a, 29a facing each other in the pockets 19c, 19c is set to the corresponding tapered roller 13, 13 in the axial position. It is smaller than the outer diameter D (C ₂ <D).

Such a rolling bearing with a retainer of this example is configured such that the radially outer surface of each of the guide portions 26a, 26a of the split type retainer and the guide peripheral surface 27a are in sliding contact or in close proximity to each other. Since the outer ring guide structure is used for positioning in the radial direction of the mold cage, even if the rotational speed becomes high during the operation of the bearing, the split cage retains a swinging motion by a force such as centrifugal force. It is possible to effectively prevent such things as waking up or tilting. Therefore, the inner peripheral edges of the pockets 19c and 19c and the rolling surfaces of the tapered rollers 13 and 13 do not strongly rub against each other, and the rotation resistance does not increase.
Further, each of the guide portions 26a, of 26a, facing each other in the circumferential direction are respective guide portions 26a, the distance B ₂ in the circumferential direction of the leading edge between the 26a, corresponding each cone in axial position Since the diameter is smaller than the diameter D of the rollers 13 and 13 (B ₂ <D), the tapered rollers 13 and 13 may be dropped from the pockets 19c and 19c radially outward during the assembly. Can be prevented.
Further, the locking projections 29a, 29a formed on the axially opposite ends of the portions of the pillars 23d, 23d in the circumferential direction at positions opposite to the guide circumferential surface 27a in a part of the circumferential side surface. Since the distance C ₂ in the circumferential direction is smaller than the outer diameter D of the tapered rollers 13 and 13 corresponding to the axial position (C ₂ <D), the tapered rollers 13 and 13 can be prevented from falling off from the pockets 19c and 19c inward in the radial direction. In the case of the structure of this example, by adopting the convex column structure shown in FIG. 4 described above, when the temperature rises, the radially outer surface of each of the guide portions 26a, 26a and the guide peripheral surface 27a An increase in surface pressure at the sliding contact portion can be suppressed.
Since the configuration and operation of the other parts are substantially the same as those in the first example of the above-described embodiment, a duplicate description is omitted.

[Fourth Example of Embodiment]
FIGS. 9-10 has shown the 4th example of embodiment of this invention corresponding to Claims 1-10. The cage element 21f constituting the split type cage of the rolling bearing with cage of this example has a guide circumference which is an inner circumferential surface of the outer ring 11 among both circumferential side surfaces of the column portions 23e and 23e. Guide surfaces 30a and 30a are provided in portions close to the surface 27a to restrict the radial position of the split cage based on the engagement of the tapered rollers 13 and 13 with the rolling surfaces. When the rolling bearing is operated at a relatively low temperature and at a low speed, the rolling bearing of the split type cage is based on the engagement between the guide surfaces 30a and 30a and the rolling surfaces of the tapered rollers 13 and 13. It moves by a rolling element guide structure for positioning in the radial direction. At this time, the guide circumferential surface 27a and the radially outer surfaces of the guide portions 26a, 26a of the cage element 21f do not come into contact with each other and face each other through a slight gap E (FIG. 10). opposite.

In such a rolling bearing with a retainer of this example, when the internal temperature rises during operation or the centrifugal force acting on each retainer element 21f increases as the rotational speed increases, the retainer element 21f When the heat expands and is displaced radially outward, the radially outer surfaces of the guide portions 26a and 26a and the guide peripheral surface 27a are in sliding contact or close to each other. That is, the rolling element guide structure shifts to the outer ring guide structure.
In this manner, even when the guide surfaces 30a and 30a are disengaged from the rolling surfaces of the tapered rollers 13 and 13 by shifting from the rolling element guide structure to the outer ring guide structure during operation. It is possible to prevent the split type cage from tilting or swinging around due to centrifugal force.
The configuration and operation of the other parts are substantially the same as in the third example of the above-described embodiment, and thus the overlapping description is omitted.

The schematic diagram of the holder | retainer for demonstrating the circumferential direction clearance in the state which arranged each holder | retainer element in the circumferential direction which shows the 1st example of embodiment of this invention. Similarly, a perspective view of a cage element. Similarly, the figure equivalent to the II cross-sectional view of FIG. 2 in the state which combined the outer ring | wheel, the inner ring | wheel, the tapered roller, and the holder | retainer. Similarly, the schematic diagram for demonstrating another example of the structure of the edge part of a holder | retainer element. The perspective view of a holder | retainer element which shows the 2nd example of embodiment of this invention. Similarly, the figure equivalent to the roll sectional view of FIG. 5 in a state where the outer ring, the inner ring, the tapered roller and the cage are combined. The perspective view of a holder | retainer element which shows the 3rd example of embodiment of this invention. Similarly, the cross-sectional view of FIG. 7 in the state where the outer ring, the inner ring, the tapered roller and the cage are combined. The perspective view of a holder | retainer element which shows the 4th example of embodiment of this invention. Similarly, the knee cross-sectional view of FIG. 9 in a state where the outer ring, the inner ring, the tapered roller and the cage are combined. The figure which shows one example of the wind power generator which incorporates the tapered roller bearing used as the object of this invention. The partial cutaway perspective view which similarly shows the inside of the housing of a wind power generator. Sectional drawing of the tapered roller bearing of conventional structure. The schematic diagram for demonstrating the structure of a split type holder | retainer. The schematic diagram for demonstrating the circumferential direction clearance gap in one example of the split type holder | retainer of a conventional structure. The perspective view of a holder | retainer element which shows an example of the conventional structure. Similarly, it is a figure for demonstrating the characteristic part of the cage | basket element of another structure, and is a perspective view of the circumferential direction both ends of a cage | basket element. Similarly, the perspective view of the circumferential direction both ends of these each retainer element in the state which couple | bonded the circumferential direction end surfaces of the adjacent retainer element.

Explanation of symbols

DESCRIPTION OF SYMBOLS 1 Windmill 2 Blade 3 Rotor 4 Housing 5 Tower 6 Rotating shaft 7 Rolling bearing 8 Speed increaser 9 Generator 10, 10a Tapered roller bearing 11 Outer ring 12 Inner ring 13 Tapered roller 14, 14a Retainer 15 Outer ring track 16 Inner ring track 17 Large diameter Side flange 18 Small diameter side flange 19, 19a, 19b, 19c Pocket 20, 20a, 20b Split type cage 21, 21a, 21b, 21c, 21d, 21e, 21f Cage element 22, 22a, 22b Rim portion 23, 23a, 23b, 23c, 23d, 23e Column 24 Joint convex part 25 Joint concave part 26, 26a Guide part 27, 27a Guide peripheral surface 28, 28a Notch part 29, 29a Locking projection part 30, 30a Guide surface

Claims (10)

An inner ring having an inner ring raceway on the outer peripheral surface, an outer ring having an outer ring raceway on the inner peripheral surface, a plurality of rolling elements provided between the outer ring raceway and the inner ring raceway, and a rolling element And a cage that can freely roll, and this cage is formed in a cylindrical shape or a conical cylindrical shape by combining a plurality of cage elements each formed in an arc shape in series in the circumferential direction. Each of the cage elements is formed by connecting a pair of rim portions, each having an arc shape, provided at both ends in the axial direction with a plurality of column portions. Rolling with a cage that uses a portion surrounded by the inner edge of the rim and the circumferential side edge of each column adjacent in the circumferential direction as a pocket to hold the rolling elements freely. In bearings,
In the state where the cage elements are combined in series in the circumferential direction to form a cylindrical or conical cage, the sum of the gaps in the circumferential direction between the circumferential end faces of the adjacent cage elements facing each other. A rolling bearing with a cage, wherein the relationship between H and the circumferential length L of the pitch circle of the cage is H ≦ 0.001L at room temperature.   The relationship between the total gap H in the circumferential direction between the adjacent circumferential end faces of each adjacent cage element and the circumference L of the pitch circle of the cage is 0 <H ≦ 0.001L at normal temperature. A rolling bearing with a retainer according to claim 1, wherein the rolling bearing has a cage.   The radial clearance which accept | permits the displacement regarding the radial direction of a holder | retainer of each rolling element in each pocket is provided between the inner surface of each of these pockets, and the rolling surface of each of these rolling elements. The rolling bearing with a cage described in any one of ˜2.   By positioning the cage circumferential surface and the guide circumferential surface, which is one of the inner circumferential surface of the outer ring and the outer circumferential surface of the inner ring, in close proximity to each other, positioning in the radial direction of the cage is achieved. The rolling bearing with a retainer according to any one of claims 1 to 3.   The peripheral surface of the cage that is in close proximity to the guide peripheral surface is a guide portion provided in a part of each column portion, and a notch portion for holding or supplying the lubricant is formed in a part of the guide portion. The rolling bearing with a retainer according to claim 4.   A guide surface that restricts the radial position of the cage based on the engagement with the rolling surface of each rolling element is provided in a portion close to the guide circumferential surface side in both circumferential side surfaces of each column portion. A rolling bearing with a retainer according to any one of claims 1 to 5.   A part of the circumferential side surface of each pillar part is formed with a locking protrusion at a position opposite to the guide peripheral surface in the radial direction, and a circle between the leading edges of the locking protrusions facing each other in the pocket The rolling bearing with a retainer according to any one of claims 4 to 6, wherein a distance in the circumferential direction is made smaller than an outer diameter of each rolling element.   The rolling bearing with a retainer according to any one of claims 1 to 7, wherein a circumferential end face of each retainer element has a convex shape in which a central portion in the axial direction protrudes.   The rolling bearing with a retainer according to any one of claims 1 to 8, wherein the rolling element is a roller.   The rolling bearing with a cage according to any one of claims 1 to 9, wherein the cage is made of a synthetic resin of any one of aromatic nylon, polyetheretherketone, and polyphenylene sulfide.

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