JP2009180235A - Automatic self-aligning roller bearing - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To reduce heating and vibration caused by operation, and to restrain abrasion by suppressing abrasion when a cage 5 and a guide ring 6 relatively rotate, when operating an automatic self-aligning roller bearing 1a. <P>SOLUTION: A radial needle bearing 15 is incorporated between the cage 5 and the guide ring 6, and the cage 5 and the guide ring 6 are relatively rotated via the radial needle bearing 15. This constitution can solve the problem by preventing an inner peripheral surface of a rim 10 constituting the cage 5 and an outer peripheral surface of the guide ring 6 from slidingly contacting with each other. <P>COPYRIGHT: (C)2009,JPO&INPIT

Description

  The present invention relates to an improvement in a self-aligning roller bearing that is incorporated in various mechanical devices and supports a rotating shaft inside a housing, for example. Specifically, friction reduction is achieved when the guide wheel, the cage and the inner ring rotate relative to each other. In particular, the self-aligning roller bearing according to the present invention can be preferably used in a rotation support portion of a papermaking machine device that requires high-speed rotation while a vibration load or an impact load is applied.

  For example, in order to rotatably support a heavy shaft on the inside of a housing, a self-aligning roller bearing as described in Patent Documents 1 and 2 has been used. FIG. 5 shows a self-aligning roller bearing 1 that has been widely known so far, as described in Patent Documents 1 and 2, for example. The self-aligning roller bearing 1 includes a plurality of spherical rollers 4 and 4 arranged in a freely rollable manner between an outer ring 2 and an inner ring 3 that are concentrically combined with each other. The cage 5 and the guide wheel 6 regulate the position and posture of each of the spherical rollers 4 and 4.

  An outer ring raceway 7, which is a spherical concave surface having a single center, is formed on the inner peripheral surface of the outer ring 2. Further, on both sides of the outer peripheral surface of the inner ring 3 in the width direction (left and right direction in FIG. 5), each faces the outer ring raceway 7 (having a symmetric bus shape with respect to the rotation axis of each of the spherical rollers 4 and 4). A pair of inner ring raceways 8 and 8 are formed. The radius of curvature of the bus bar shape of the inner ring raceways 8 and 8 is equal to the radius of curvature of the bus bar shape of the outer ring raceway 7. In the case of the illustrated example, flange portions 9 and 9 having outward flange shapes are formed at both axial ends of the outer peripheral surface of the inner ring 3, respectively. The spherical rollers 4 and 4 have a beer barrel shape in which the maximum diameter portion exists in the middle portion in the axial direction of each spherical roller 4 and 4 (generally, a symmetrical shape in which the maximum diameter portion is in the axial center). Thus, the outer ring raceway 7 and the pair of inner ring raceways 8, 8 are arranged so as to roll freely in two rows. The radius of curvature of the bus bar shape of the outer peripheral surface of each of the spherical rollers 4 and 4 is slightly smaller than the radius of curvature of the bus bar shape of the outer ring raceway 7 and the inner ring raceways 8 and 8.

  The cage 5 was made as a whole by cutting a metal material having self-lubricating properties such as a copper-based alloy such as brass, or by injection molding a synthetic resin. In this configuration, the rim portion 10 includes an annular rim portion 10 and a plurality of column portions 11 and 11 projecting in opposite directions from both axial side surfaces of the rim portion 10. Then, pockets 12 and 12 for holding the respective spherical rollers 4 and 4 are respectively surrounded by three sides surrounded by the side surfaces of the column portions 11 and 11 adjacent in the circumferential direction and the axial side surface of the rim portion 10. It is said.

  Further, the guide wheel 6 is formed in an annular shape as a whole by a material having a low coefficient of friction, such as a metal having self-lubricating properties such as a copper alloy, an oil-impregnated metal, or a synthetic resin. The guide wheel 6 has a trapezoidal cross section with an axial width that is larger on the outer diameter side and smaller on the inner diameter side, and an inner diameter that is slightly larger than the outer diameter of the intermediate portion in the axial direction of the inner ring 3, and the rim portion of the cage 5 And an outer diameter that is slightly smaller than the inner diameter of 10. Such a guide wheel 6 is installed between the inner peripheral surface of the inner ring 3 and the inner peripheral surface of the rim portion 10 so as to be able to rotate relative to the inner ring 3 and the rim portion 10. In this way, the outer peripheral surface of the guide wheel 6 is opposed to the inner peripheral surface of the rim portion 10, and the inner peripheral surface of the guide wheel 6 is opposed to the outer peripheral surface of the intermediate portion in the axial direction of the inner ring 3. The retainer 5 is positioned in the radial direction (by inner ring guide). Further, in this state, both side surfaces 13 and 13 of the guide wheel 6 in the axial direction are the inner end surfaces in the axial direction of the spherical rollers 4 and 4 (end surfaces on the center side in the width direction of the self-aligning roller bearing 1. The same applies to the entire claims.) 14 and 14 are substantially parallel to each other (surfaces connecting the circumferential ends of the opposing portions).

  For example, when the rotating shaft is supported inside the housing by the self-aligning roller bearing 1 configured as described above, the outer ring 2 is fitted and fixed to the housing, and the inner ring 3 is fixed to the rotating shaft. When the inner ring 3 rotates together with the rotating shaft, the spherical rollers 4 and 4 roll to allow this rotation. When the shaft center of the housing and the shaft center of the rotary shaft do not match, the inner ring 3 is aligned inside the outer ring 2 (the central axis of the inner ring 3 is inclined with respect to the central axis of the outer ring 2). To compensate for this discrepancy. In this case, since the outer ring raceway 7 is formed in a single spherical shape, the rolling of the spherical rollers 4 and 4 is performed smoothly even after the mismatch compensation. The postures of the spherical rollers 4 and 4 are controlled based on the engagement between the axial inner end surfaces 14 and 14 and the axial side surfaces 13 and 13 of the guide wheel 6. That is, the skew in which the rotation center axes of the spherical rollers 4 and 4 are deviated from their original positions is suppressed, and the rolling surfaces of the spherical rollers 4 and 4 and the outer ring raceway 7 and the inner ring raceways 8 and 8 roll. Reduce friction at the contact area.

  In the case of the self-aligning roller bearing 1 having the conventional structure as described above, the positioning of the cage 5 in the radial direction may be caused by the inner ring guide using the guide wheel 6 to cause the following problems. is there. Hereinafter, description will be made with reference to FIG. 6 in addition to FIG. In FIG. 6, a gap is drawn between the side surface 13 in the axial direction of the guide wheel 6 and the inner end surface 14 in the axial direction of the spherical roller 4, but these surfaces 13, 14 are in sliding contact in actual use. .

  As is widely known in the field of rolling bearings, the relative speed between the inner peripheral surface of the rim portion 10 constituting the cage 5 and the outer peripheral surface of the inner ring 3 increases as the rotational speed of the rotary shaft increases. Become. For this reason, when the self-aligning roller bearing 1 is incorporated in a rotation support portion of a machine device that rotates at high speed, such as a papermaking machine device, the inner peripheral surface of the rim portion 10 and the outer peripheral surface of the guide wheel 6 The sliding friction acting on the engaging portion (sliding contact portion) and the engaging portion between the inner peripheral surface of the guide wheel 6 and the outer peripheral surface in the axial direction intermediate portion of the inner ring 3 is considerably increased. Therefore, heat generation (friction heat) and vibration (friction vibration) associated with the operation of the self-aligning roller bearing 1 are increased, which is disadvantageous for high speed operation.

  Furthermore, wear that occurs on the inner peripheral surface of the rim portion 10, the inner and outer peripheral surfaces of the guide wheel 6, and the axially intermediate portion outer peripheral surface of the inner ring 3, which become sliding contact surfaces, increases. For this reason, it is possible to deteriorate the bearing performance by deteriorating the grease filled in the bearing or causing wear on the rolling surfaces of the spherical rollers 4 and 4 and the outer ring raceway 7 and the inner ring raceways 8 and 8. There is sex. Therefore, it is difficult to ensure the reliability and durability of the self-aligning roller bearing 1 over a long period of time under severe use conditions in which vibration load or impact load is applied, such as a rotation support portion of a papermaking machine. .

Japanese Patent Laid-Open No. 11-2250 JP-A-2005-24026

  In view of the circumstances as described above, the present invention is intended to reduce friction when the guide wheel, the cage and the inner ring rotate relative to each other, reduce heat generation and vibration associated with operation, and reduce the occurrence of wear. The invention was invented to realize a spherical roller bearing.

The self-aligning roller bearing of the present invention includes an outer ring, an inner ring, a plurality of spherical rollers, a cage, and a guide wheel, as in the conventional self-aligning roller bearings.
Among these, the outer ring forms an outer ring raceway having a spherical concave surface on the inner peripheral surface thereof.
The inner ring has a pair of inner ring raceways opposed to the outer ring raceway formed on the outer peripheral surface thereof.
Each of the spherical rollers is provided in two rows between the outer ring raceway and the inner ring raceways so as to be freely rotatable in each row.
The retainer has an annular shape, and is provided with a plurality of pockets in the circumferential direction at a plurality of pockets for rotatably holding the spherical rollers.
Furthermore, the guide wheel is disposed between the inner peripheral surface of the cage and the outer peripheral surface in the axial intermediate portion of the inner ring, and between the axial inner end surfaces of the two rows of spherical rollers facing each other. Is sandwiched between.
As the cage, a so-called press cage formed by press-molding a metal plate is used in addition to an annular rim portion and a plurality of column portions as shown in FIG. You can also do things.

  In particular, in the self-aligning roller bearing of the present invention, a radial needle bearing (so-called cage and roller type, shell) is provided between the guide wheel and at least one member of the cage and the inner ring. Shape, solid, and full complement).

  According to the self-aligning roller bearing of the present invention having the above-described configuration, at the time of operation, the guide wheel and at least one member of the cage and the inner ring are relatively rotated via the radial needle bearing. I can do things. For this reason, it is possible to prevent sliding friction between the peripheral surface of the guide wheel and the peripheral surface (the inner peripheral surface of the cage and the outer peripheral surface in the axial direction of the inner ring) that is the peripheral surface of the at least one member. . Therefore, heat generation and vibration associated with the operation of the self-aligning roller bearing can be reduced, and wear can be suppressed.

[First example of embodiment]
1 and 2 show a first example of an embodiment of the present invention. The feature of this example is that a radial needle bearing 15 is incorporated between the cage 5 and the guide wheel 6. Since the configuration and operation of the other parts are the same as those of the conventional structure described above, overlapping illustrations and explanations are omitted or simplified, and the following description will focus on the characteristic parts of this example.

  In the self-aligning roller bearing 1 a of this example, the radial needle bearing 15 is incorporated between the inner peripheral surface of the rim portion 10 constituting the cage 5 and the outer peripheral surface of the guide wheel 6. As shown in FIG. 2, the radial needle bearing 15 includes a plurality of needles 16 and 16 and a holder 17 for holding the needles 16 and 16 so as to roll freely. The inner peripheral surface of the rim portion 10 is an outer ring raceway 18, the outer peripheral surface of the guide wheel 6 is an inner ring raceway 19, and the rolling surfaces of the needles 16, 16 are the outer ring raceway 18 and the inner ring raceway 19. Rolling contact.

  As described above, in the case of this example, a so-called cage and roller type is used as the radial needle 15. For this reason, it is not necessary to separately provide an outer ring and an inner ring for radial needle bearings, and accordingly, a reduction in thickness in the radial direction of the rim portion 10 and the guide wheel 6 is suppressed. In the case of this example, in order to directly form the outer ring raceway 18 on the inner peripheral surface of the rim portion 10, the cage 5 is made of a metal material such as an iron alloy such as a copper alloy or stainless steel. Yes. Further, the guide ring 6 is also made of a metal material such as a copper alloy or an iron alloy in order to directly form the inner ring raceway 19 on the outer peripheral surface thereof. Further, the radial needle bearing as described above is not provided between the inner peripheral surface of the guide wheel 6 and the outer peripheral surface in the axial direction intermediate portion of the inner ring 3, and both of these are provided in the same manner as in the conventional structure described above. The peripheral surfaces are close to each other.

  In the case of the self-aligning roller bearing 1a of the present example having the above-described configuration, the cage 5 and the guide wheel 6 can be relatively rotated via the radial needle bearing 15 during operation. For this reason, it is possible to prevent sliding friction between the inner peripheral surface of the rim portion 10 constituting the cage 5 and the outer peripheral surface of the guide wheel 6. In this example, the inner peripheral surface of the rim portion 10 and the outer peripheral surface of the guide wheel 6 are in rolling friction with the rolling surfaces of the needles 16 and 16. However, this rolling friction is sufficiently smaller than the sliding friction. Therefore, in the case of this example, heat generation and vibration generated between the inner peripheral surface of the rim portion 10 and the outer peripheral surface of the guide wheel 6 can be sufficiently suppressed, and the inner peripheral surface of the rim portion 10 and Wear of the outer peripheral surface of the guide wheel 6 can be suppressed.

  Further, since the friction acting between the inner peripheral surface of the rim portion 10 constituting the cage 5 and the outer peripheral surface of the guide wheel 6 can be reduced, the relative speed between the guide wheel 6 and the inner ring 3 can be reduced. Can be kept low. Therefore, the sliding friction acting on the engaging portion (sliding contact portion) between the inner peripheral surface of the guide wheel 6 and the outer peripheral surface in the axial direction of the inner ring 3 can be reduced as compared with the conventional structure described above. . Therefore, heat generation and vibration generated in the engaging portion can be suppressed, and wear generated on the inner peripheral surface of the guide wheel 6 and the outer peripheral surface in the axial intermediate portion of the inner ring 3 can be suppressed.

  As described above, according to the self-aligning roller bearing 1a of the present example, compared to the above-described self-aligning roller bearing 1 having a conventional structure (see FIG. 5), heat generation and vibration associated with operation can be reduced, and wear is reduced. Can be suppressed. Also, the dynamic torque can be reduced. For this reason, it becomes advantageous when performing high-speed driving | operation, and it can prevent that bearing performance falls. Therefore, the self-aligning roller bearing 1a of the present example can obtain sufficient durability even under severe use conditions such as a rotation support portion of a paper machine, and ensure sufficient reliability over a long period of time. it can.

  When assembling the self-aligning roller bearing 1a of the present example, for example, the radial needle bearing 15 is incorporated between the cage 5 and the guide wheel 6, and one intermediate component (subassembly). And Thereafter, this intermediate part is assembled between the inner peripheral surface of the outer ring 2 (see FIG. 5) and the outer peripheral surface of the inner ring 3. If such an assembling method is adopted, the assembly work of the radial needle bearing 15 can be performed in a wide space and the members 5, 6, 15 can be handled together, so that the work efficiency can be improved. Improvements can be made.

[Second Example of Embodiment]
FIG. 3 shows a second example of the embodiment of the present invention. The feature of this example is that a radial needle bearing 15 a is incorporated between the guide wheel 6 and the inner ring 3. Since the configuration and operation of the other parts are the same as those of the first example of the embodiment described above and the conventional structure described above, overlapping illustrations and descriptions are omitted or simplified, and the features of this example are described below. The explanation will focus on the part.

  Also in this example, as in the case of the first example of the above-described embodiment, the radial needle bearing 15a is held by a plurality of needles 16a and the needles 16a for holding the needles 16a in a rollable manner. And a container 17a. The inner peripheral surface of the guide wheel 6 is an outer ring raceway 18a, the outer peripheral surface in the axial direction of the inner ring 3 is an inner ring raceway 19a, and the rolling surface of each needle 16a is the outer ring raceway 18a and the inner ring raceway 19a. It is in contact with rolling. In the case of this example as well, the guide wheel 6 is made of a metal material such as a copper alloy or an iron alloy, but the cage 5 is made of a synthetic resin. Further, the radial needle bearing as described above is not provided between the outer peripheral surface of the guide wheel 6 and the inner peripheral surface of the rim portion 10 constituting the cage 5, and is the same as in the case of the conventional structure described above. In addition, these two peripheral surfaces are directly opposed to each other.

  In the case of the self-aligning roller bearing 1b of the present example having the above-described configuration, the guide wheel 6 and the inner ring 3 can be relatively rotated through the radial needle bearing 15a during operation. For this reason, it is possible to prevent sliding friction between the inner peripheral surface of the guide wheel 6 and the outer peripheral surface in the axial direction intermediate portion of the inner ring 3. The inner peripheral surface of the guide wheel 6 and the outer peripheral surface in the axial intermediate portion of the inner ring 3 are in rolling contact with the rolling surface of each needle 16a. The friction (rolling friction) associated with the rolling contact is the slip Small enough compared to friction. Therefore, heat generation and vibration generated between the inner peripheral surface of the guide wheel 6 and the outer peripheral surface in the axial intermediate portion of the inner ring 3 can be sufficiently suppressed, and the inner peripheral surface of the guide wheel 6 and the inner ring 3 can be prevented. Wear on the outer peripheral surface of the intermediate portion in the axial direction can be suppressed.

Further, as the friction acting between the inner peripheral surface of the guide wheel 6 and the outer peripheral surface of the axial intermediate portion of the inner ring 3 can be reduced, the rim portion 10 constituting the retainer 5 and the guide wheel 6 can be reduced. And the relative speed can be kept low. For this reason, the sliding friction which acts on the engaging part (sliding contact part) of the inner peripheral surface of these rim | limb parts 10 and the outer peripheral surface of the guide wheel 6 can be made small compared with the case of the conventional structure mentioned above. As a result, heat generation and vibration generated in the engaging portion can be suppressed, and wear generated on the inner peripheral surface of the rim portion 10 and the outer peripheral surface of the guide wheel 6 can be suppressed.
As described above, in the case of the self-aligning roller bearing 1b of this example, heat generation and vibration associated with operation can be reduced as compared with the self-aligning roller bearing 1 having the conventional structure (see FIG. 5). Wear can be suppressed.

[Third example of embodiment]
FIG. 4 shows a third example of the embodiment of the present invention. The feature of this example is that radial needle bearings 15 and 15a are incorporated in a portion between the rim portion 10 and the guide wheel 6 constituting the cage 5 and a portion between the guide wheel 6 and the inner ring 3, respectively. is there. Since the configuration and operation of other parts are the same as those in the first and second examples of the above-described embodiment and the conventional structure described above, overlapping illustrations and explanations are omitted or simplified. The description will focus on the features of

In the case of the self-aligning roller bearing 1c of the present example having the above-described configuration, the cage 5 and the guide wheel 6 can be relatively rotated through the radial needle bearing 15 during operation. The guide wheel 6 and the inner ring 3 can be rotated relative to each other via the radial needle bearing 15a. Therefore, it is possible to prevent sliding friction between the inner peripheral surface of the rim portion 10 constituting the cage 5 and the outer peripheral surface of the guide wheel 6, and the inner peripheral surface of the guide wheel 6 and the shaft of the inner ring 3. It is possible to prevent sliding friction with the outer circumferential surface of the direction intermediate portion.
Therefore, in the case of the self-aligning roller bearing 1c of this example, the heat generation and vibration associated with the operation can be reduced and the occurrence of wear as compared with the self-aligning roller bearing 1 having the conventional structure (see FIG. 5). Can be suppressed.

  In each example of the above-described embodiment, only the structure in which the spherical roller 4 in one row and the spherical roller 4 in the other row are held by an integrated cage 5 is shown. The spherical rollers 4 in one row and the spherical rollers 4 in the other row can be held by independent cages. That is, as shown in FIG. 7, the cage 5a for holding the spherical rollers 4 in one row and the cage 5a for holding the spherical rollers 4 in the other row can be rotated relative to each other. Can be independent. By adopting such a configuration, even when there is a difference in the revolution speed between the spherical rollers 4 and 4 in both rows, the cages 5a and 5a holding the spherical rollers 4 and 4 in both rows are independent. Rotate. That is, the self-aligning roller bearing is often operated while one row of the spherical rollers 4 and 4 in both rows bears a larger load than the other row. In this case, a difference occurs in the revolution speed of the spherical rollers 4 and 4 in both rows. In such a case, the cages 5a and 5a for holding the spherical rollers 4 and 4 in both rows rotate independently of each other, so that the spherical roller 4 in the row with the high revolution speed is replaced with the spherical roller in the slow row. The spherical roller 4 in the row with the slow revolving speed is not applied to the revolving motion of the spherical roller 4 in the same fast row. As a result, the dynamic torque and the heat generated by the operation can be kept low.

  As described above, when the spherical rollers 4 in one row and the spherical rollers 4 in the other row are held by independent cages 5a and 5a, they are arranged on the inner diameter side of these cages 5a and 5a. The number of radial needle bearings 15 (see FIGS. 1 and 4) may be one as in the case of the first and third examples of the embodiment described above, or one for each of the cages 5a and 5a. A total of two may be sufficient. In this way, if two radial needle bearings are arranged, when the cages 5a and 5a rotate independently of each other, the inner peripheral surface of the rim part constituting the cages 5a and 5a, and the above Friction at the rolling contact portion with the rolling surface of each needle 16 (see FIGS. 1 and 4) constituting each radial needle bearing can be kept low.

  In each example of the embodiment described above, the radial needle bearings 15 and 15a have been described as cage and roller type radial needle bearings in which the bearing rings are omitted, but the radial needles used in the present invention are described. The bearing is not limited to such a configuration. That is, in addition to the full roller bearing in which the cage is omitted, a shell-type or solid-type radial needle bearing provided with a bearing ring can be used. In addition, when using the radial needle bearing provided with the bearing ring, the cage and the guide ring may be made of a synthetic resin instead of a metal material such as a copper alloy or an iron alloy.

The figure equivalent to FIG. 6 which shows the 1st example of embodiment of this invention. Sectional drawing which similarly extracts and shows a radial needle bearing. The figure similar to FIG. 1 which shows the 2nd example of embodiment of this invention. The figure similar to FIG. 1 which shows the same 3 examples. The half part sectional view which shows an example of the self-aligning roller bearing known conventionally. FIG. 6 is an enlarged schematic view of the portion “a” in FIG. 5, omitting the outer ring and the spherical rollers in one row. The half part sectional view which shows another example of the self-aligning roller bearing used as the object of this invention.

Explanation of symbols

DESCRIPTION OF SYMBOLS 1, 1a-1c Self-aligning roller bearing 2 Outer ring 3 Inner ring 4 Spherical roller 5, 5a Cage 6 Guide wheel 7 Outer ring raceway 8 Inner ring raceway 9 Grow part 10 Rim part 11 Column part 12 Pocket 13 Axial side surface 14 Axial direction inside End face 15, 15a Radial needle bearing 16, 16a Needle 17, 17a Cage 18, 18a Outer ring race 19, 19a Inner ring race

Claims (1)

  An outer ring in which an outer ring raceway that is a spherical concave surface is formed on the inner peripheral surface, an inner ring in which a pair of inner ring races opposed to the outer ring raceway are formed on the outer peripheral surface, and the outer ring raceway and the inner ring raceway in two rows. Separately, an annular cage in which a plurality of spherical rollers are provided for each row, and a plurality of pockets for holding each of the spherical rollers is provided at a plurality of locations in the circumferential direction. And a guide wheel disposed between the inner peripheral surface of the cage and the outer peripheral surface in the axial direction intermediate portion of the inner ring and sandwiched between the axial inner end surfaces of the two rows of spherical rollers facing each other. A self-aligning roller bearing provided with a radial needle bearing is incorporated between the guide wheel and at least one member of the cage and the inner ring. Spherical roller bearing.

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