JP2019086063A - Cylindrical roller bearing - Google Patents

Abstract

To prevent frictional heat from occurring at an inner ring and an outer ring contacting with a spacer even in a case where a roller bearing with the spacer rotates at high speed or in a high load state, and also to prevent contact surfaces therebetween from being worn.SOLUTION: A spacer 4 of a cylindrical roller bearing has, at both axial ends, a pair of circular flanges 4b swollen radially from an outer peripheral surface of a spacer body 4a. The spacer body 4a rotatably contacts with an outer peripheral surface 1a of an inner ring 1, and rotatably externally contacts with both outer peripheral surfaces of adjacent cylindrical rollers 3. When the inner ring 1 rotates, the spacer 4 rotates with rotational force received in the same direction from the opposite outer peripheral surfaces of the two rollers 3, so that the roller 3 and the spacer 4 can contact with each other in a rolling friction state.SELECTED DRAWING: Figure 1

Description

  The present invention relates to cylindrical roller bearings.

In general, cylindrical roller bearings are known that use parts also referred to as spacers or separators or spacers.
For example, as shown in FIGS. 9 and 10, a plurality of cylindrical rollers (hereinafter simply referred to as "rollers") 3 are arranged in the circumferential direction in the raceway space between the inner ring 1 and the outer ring 2 of the cylindrical roller bearing. A spacer 20 of a predetermined shape is attached so that a gap is formed at a predetermined interval between all the adjacent rollers 3, and axial movement of the bearing is suppressed by the side plate 21.

  Spacer 20 has a generally bowl-like shape extending in the radial direction from the outer diameter side to the inner diameter side of pitch circle C of roller 3, and it is known that both sides have a drum shape recessed in a circular curved shape. (Patent Document 1).

  Such a spacer 20 keeps the opposing outer peripheral surfaces of the adjacent rollers 3, 3 in contact with both sides to maintain a space, while the rollers 3 rotate in opposite directions on such both sides. Contact in sliding condition.

  Both side surfaces of the spacer 20 in contact with the cylindrical roller 3 are formed to be smooth so as to have a coefficient of friction as low as possible, and a liquid lubricant such as a solid lubricant or lubricating grease is supplied. Are lubricated.

  Further, as shown by a chain line in FIG. 9, there is also known a structure in which the bottom surface 22 of the wedge-shaped spacer 20 provided in the cylindrical roller bearing is in contact with the raceway surface of the inner ring 1 (Patent Document 2). Therefore, it is considered possible to stabilize the posture of the spacer 20.

JP 2005-344854 A Japanese Patent Application Laid-Open No. 60-263726 (see FIGS. 4 to 10)

  However, in the above-mentioned prior art, since the spacer is in frictional contact with the spacer in sliding condition, even when the lubricant is supplied, when using the roller bearing under high load condition or high speed rotation condition, In some cases, it may be in a state of poor lubrication, and the spacer has the disadvantage of being easily worn out.

  Further, when the cylindrical roller bearing is rotated at high speed, frictional heat is generated in the roller and the inner ring in frictional contact with the spacer, and the roller bearing and its periphery are heated, causing problems such as heating of the peripheral equipment and thermal degradation of the lubricant. May also occur.

  Then, the subject of this invention solves the above-mentioned problem, and even if the roller bearing provided with a spacer rotates in high speed rotation and a high load state, it contacts with a spacer, and friction heat is applied to the inner ring or the outer ring. Is less likely to occur, and these contact surfaces are less susceptible to wear.

  In order to solve the above problems, in the present invention, the inner ring, the outer ring, the plurality of cylindrical rollers arranged in the circumferential direction between the inner and outer rings, and the cylindrical rollers are adjacent to each other in a non-contact state. A cylindrical roller bearing provided with a spacer interposed between the cylindrical rollers is improved, and the spacer is rotatably in contact with the outer peripheral surface of the inner ring or the inner peripheral surface of the outer ring, and both outer peripheral surfaces of adjacent cylindrical rollers It has a cylindrical or cylindrical shape that is disposed so as to circumscribe rotatably.

  In the cylindrical roller bearing according to the present invention configured as described above, the spacer interposed between the plurality of cylindrical rollers is cylindrical or cylindrical, and can freely rotate on the outer peripheral surface of the inner ring or the inner peripheral surface of the outer ring It arrange | positions so that it may contact rotatably and it circumscribes | wears freely on the outer peripheral surfaces of the adjacent cylindrical rollers, and, thereby, the cylindrical rollers adjoin in a non-contacting state.

  Since the spacer of the predetermined shape is arranged at the predetermined position in this manner, the cylindrical or cylindrical spacer receives rotational force in the same direction from both opposing outer peripheral surfaces of the two cylindrical rollers and rotates. The sliding friction with the cylindrical roller can be avoided, and the rolling contact can be made in contact.

In addition, since the rotating spacer is in contact with only one of the outer peripheral surface of the inner ring or the inner peripheral surface of the outer ring, the bearing load between the inner and outer rings is not loaded.
While rotating in this manner, the spacer is pushed by the moving roller and moves in the circumferential direction on the outer peripheral surface of the inner ring or the inner peripheral surface of the outer ring, but the rotation of the rollers is in the opposite direction to this moving direction. Since it is rotation, sliding friction resistance occurs on the contact surface of the inner or outer ring that the spacer contacts.

  However, since the bearing load does not act on the spacer as described above, the sliding friction resistance becomes very small, and the frictional heat generated on the contact surface with the spacer is extremely small in the roller, inner ring and outer ring, It hardly affects the rotational torque resistance of the bearing. In particular, since the lubricant sealed or supplied in the cylindrical roller bearing is also supplied to the surface of the spacer, the sliding friction resistance is smaller.

  Further, in the above-described frictional resistance, the amount of wear of the spacer is also very small, so as described above, the contact surfaces with the roller, the inner ring, and the outer ring which are in contact with the spacer do not easily wear.

  In addition, the above-mentioned spacer should just be interposed between the said cylindrical rollers, and when not having a flange mentioned later in particular, a well-known structure may be adopted for the position. For example, the axial movement of the roller bearing can be suppressed by an annular rim formed on the outer circumferential surface of the inner ring or the inner circumferential surface of the outer ring, or an annular side plate integrally provided with the outer ring or the inner ring.

  Also, in order to make the rotation of the cylindrical or cylindrical spacer smoother and to be in a stable rotation state, the spacer radially from the outer circumferential surface at both axial ends of the cylindrical or cylindrical spacer body. If it is a cylindrical roller bearing provided with a projecting circular flange and providing a circumferential groove or rim for guiding the circular flange in the circumferential direction on the outer circumferential surface of the inner ring or the inner circumferential surface of the outer ring, the axial direction of the spacer You can regulate movement.

  That is, since the spacer is attached in a state where the outer periphery of the circular flange is fitted in the circumferential groove or along the inner side of the rim, the amount of movement of the roller bearing in the axial direction becomes extremely small. Stable rotation can be achieved without any directional deflection.

  By the way, since the spacer needs to be sequentially installed between the rollers at the time of the assembly operation of the roller bearing, at least the spacer to be installed last needs to be inserted from the axial direction of the cylindrical roller bearing.

  Therefore, the circular flange is a circular flange comprising a removable ring or disk at least at one end of the spacer body, while the spacer body is incorporated at the time of assembly of the roller bearing. Since it can be removed, the process of assembling and removing the spacer becomes easy.

  In the same manner as described above, the circular flange is provided on the divided pieces that can be divided in the axial direction or the radial direction of the spacer main body and can be united so that the assembling operation of the spacer and the removing operation at the required time such as maintenance become easy. Preferably it is a rounded flange.

  Also, in order to minimize the sliding friction resistance of the contact surface between the spacer main body and the inner ring or the outer ring, the outer peripheral surface can be used efficiently so that the lubricant enclosed or supplied in the normal cylindrical roller bearing can be used efficiently. It is preferable that the spacer body has an oil groove or a dimpled oil reservoir.

  As a form of the above-mentioned oil groove, if a spiral groove which goes around the outer peripheral surface of the spacer main body or an oil groove extending in the axial direction is adopted, the main part or the whole of the outer peripheral surface of the spacer main body can be efficiently The required amount of lubricant can be supplied.

  The spacer main body can be made of one or more kinds of materials selected from metal, synthetic resin and ceramics, whereby it is possible to selectively provide electrical conductivity and insulation as needed.

  According to the present invention, the spacer of the cylindrical roller bearing is disposed so as to rotatably contact the outer peripheral surface of the inner ring or the inner peripheral surface of the outer ring, and to rotatably contact the outer peripheral surfaces of adjacent cylindrical rollers. The spacer can prevent frictional contact in a sliding state with adjacent cylindrical rollers that rotate and circumscribe. In addition, since the rotating spacer rotates without being loaded with the bearing load, frictional heat is generated on the contact surfaces of the inner ring, the outer ring, and the rollers that contact the spacer even when the roller bearing rotates at high speed or high load. It has the advantage that it is difficult and that these contact surfaces are less susceptible to wear.

Principal part sectional view of a roller bearing showing a first embodiment of the present invention II-II sectional view taken on the line of FIG. 1 which shows 1st Embodiment of this invention Principal part sectional view of a roller bearing showing a second embodiment of the present invention Parts exploded perspective view of spacer used in the second embodiment of the present invention Front view of spacer used for 3rd Embodiment of this invention Cross-sectional view of spacer used in the fourth embodiment of the present invention (A) A perspective view of a spacer used in the fifth embodiment of the present invention, (b) a sectional view of the spacer used in the fifth embodiment of the present invention A perspective view for explaining an example (a), (b) and (c) of a spacer main body used in an embodiment of the present invention Principal part sectional view of roller bearing showing prior art example XX sectional drawing of FIG. 9 which shows a prior art example

Embodiments of the present invention will be described below based on the attached drawings.
In the first embodiment shown in FIGS. 1 and 2, in the cylindrical roller bearing, a plurality of cylindrical rollers arranged in the circumferential direction between the inner ring 1, the outer ring 2 and the inner and outer rings (hereinafter may be simply referred to as rollers). 3) and a spacer 4 interposed between the cylindrical rollers 3 so that the cylindrical rollers 3 are adjacent to each other in a non-contact state.

  The spacer 4 in this embodiment is a pitch circle (PCD) C of a cylindrical roller which is a locus of the center of the cylindrical roller 3 when the cylindrical roller 3 moves while rotating on the outer peripheral surface 1a of the inner ring 1 , Located radially inwards.

  Spacer 4 has a pair of circular flanges 4b protruding in the radial direction from the outer peripheral surface of spacer main body 4a at both ends in the axial direction. The spacer main body 4a is in a cylindrical shape that is rotatably in contact with the outer peripheral surface 1a of the inner ring 1 and rotatably circumscribed with both outer peripheral surfaces of the adjacent cylindrical rollers 3. The spacer body 4a and the circular flange 4b can be formed of a material such as a metal such as steel, a synthetic resin such as an engineering plastic and a ceramic, or a composite material of these.

  The inner ring 1 is provided with a circumferential groove 5 for guiding a portion of the outer peripheral edge including the outer peripheral surface of the circular flange 4b of the spacer 4 described above so as to circumferentially rotate on the outer peripheral surface 1a.

  The illustrated spacer 4 transfers a lubricant such as lubricating grease (not shown) filled in cylindrical roller bearings from the outer peripheral surface 1a of the inner ring 1 to the surface of the roller 3, and the spacer main body 4a A plurality of oil grooves 6 linearly extending in the axial direction are formed at equal intervals on the outer peripheral surface of the spacer main body 4a so that the surface can be supplied as abundantly as possible.

  The cylindrical roller bearing configured in this manner is applicable to a use state in which the outer ring 2 is fixed and the inner ring 1 is rotated. When the inner ring 1 is rotated, the spacer 4 faces the two rollers 3 The rollers 3 and the spacer 4 can be brought into contact with each other in the state of rolling friction since they rotate in the same direction from the outer peripheral surfaces in the same direction (illustrated by arrows in FIG. 1).

  The spacer 4 rotating in this manner is pushed by the roller 3 and moves on the track of the outer peripheral surface 1a of the inner ring 1, but as described above, the roller 3 is rotating in the opposite direction to this movement direction . Therefore, the spacer 4 receives sliding friction resistance from the contact surface with the outer peripheral surface 1a of the inner ring 1 in contact.

  However, since lubricating grease is supplied to the spacer 4 and the bearing load applied to the roller 3 does not act, the sliding friction resistance becomes very small and the contact surface between the roller 3 and the inner ring 1 is The frictional heat generated is extremely small and hardly affects the rotational torque of the cylindrical roller bearing.

  In this manner, the spacer 4 can avoid frictional contact in a sliding state with the adjacent rollers 3 that rotate and circumscribe. Further, since the rotating spacer 4 rotates without being loaded with a bearing load, the contact surfaces of the roller 3 and the inner ring 1 contact with the spacer 4 even if the cylindrical roller bearing rotates in high speed rotation or high load condition. Heat is less likely to occur, and these contact surfaces are less likely to wear.

  Although the arrangement of the spacer 4 in the first embodiment exemplifies a cylindrical roller bearing for rotating the inner ring 1 in an appropriate arrangement, the cylindrical roller bearing for fixing the inner ring 1 and rotating the outer ring 2 is exemplified as follows: As shown by a dot-and-dash line in FIG. 1, it can be arranged radially outward with respect to the pitch circle (PCD) C of the roller 3. When the spacer 4 is thus arranged, the circumferential groove 5 for guiding the circular flange 4 b of the spacer 4 may be formed on the inner peripheral surface of the outer ring 2.

  Further, as shown by the alternate long and short dash line in FIG. 2, instead of the circumferential groove 5 for guiding the circular flange 4b in the first embodiment, an annular rim r formed on the outer peripheral surface 1a of the inner ring 1 is provided The spacer 4 can also be assembled in a state where the circular flange 4b is placed along the inside of the rim r.

  The cylindrical roller bearing of the second embodiment shown in FIG. 3 and FIG. 4 is one of the spacers 7 of the spacer main body 7a of the spacer 7 in place of the circular flange 4b provided integrally with the spacer main body 4a in the first embodiment. The removable ring 7 b is provided at the end, and the other structure is the same as that of the first embodiment.

  That is, in the circular flange 7b of the second embodiment, the small diameter portions 7c are formed at both ends of the spacer main body 7a, and the ring 7b having a diameter larger than the outer diameter of the spacer main body 7a is inserted into this. It fixes using the washer 7d which has a notch, and provides a structure similar to a circular flange.

  Further, in the third embodiment shown in FIG. 5, instead of the circular flange 4b provided integrally with the spacer main body 4a in the first embodiment, the spacer 8 is detachably attachable to one end of the spacer main body 8a. The screw type ring 8b is provided, and the other structure is the same as that of the first embodiment.

  Furthermore, instead of the spacer 4 in the first embodiment, the fourth embodiment shown in FIG. 6 is a male that can be coupled and separated by a fitting structure in the axial direction of the main body of the spacer 9. It is what provided division | segmentation piece 9a, 9b which has a part and a female part, and other than that is the same structure as 1st Embodiment. The circular flange 9c is integrally provided on one end of the divided pieces 9a and 9b which can be divided in the axial direction of the spacer 9 and can be combined.

  The male part and the female part described above are provided in the form of a truncated cone with a diameter difference that allows coupling due to the dimensional difference between thermal expansion and thermal contraction of the metal material, or a part is formed of resin etc. It is possible to adopt one that is removable.

  Further, in the fifth embodiment shown in FIG. 7, instead of the spacer 4 in the first embodiment, the disk-shaped circular flange 10 c of the spacer 10 is halved in the radial direction of the main portion of the spacer 10. It is integrally provided in the end of a pair of divided pieces 10a and 10b which can be divided and united, respectively.

  The pair of divided pieces 10a and 10b in this embodiment is integrally provided with a columnar pin 10d for insertion at the end opposite to the formation side of each circular flange 10c, and a through hole into which this can be inserted Are formed at the essential points of the circular flange 10c.

Such a pair of divided pieces 10a and 10b can be inserted so as to axially face each other from both sides of the bearing at the time of assembling the cylindrical roller bearing, and the pin 10d and the through hole can be fitted and coupled. The connection state can adopt a known fixing means such as crimping, crimping, welding, adhesion and the like like a rivet connection.
In this way, it is possible to easily perform the operation of removing the spacer at the required time such as the assembling operation of the spacer and the maintenance.

  Moreover, the spacer main body 4a used for the above-mentioned embodiment shown to FIG. 8 (a) is a cylindrical thing, A lighter-weight spacer is comprised using this, The rotation can be made smooth more. it can.

  The spacer used in the above-described embodiment shown in FIG. 8 (b) is enclosed in a normal roller bearing in order to minimize the sliding friction resistance of the contact surface between the spacer main body 4a and the inner ring 1 or the outer ring 2. Alternatively, the oil groove 11 is formed on the outer peripheral surface so that a lubricant such as lubricating grease to be supplied can be used efficiently. The illustrated oil groove 11 is formed in a spiral groove shape that goes around the outer peripheral surface of the spacer main body 4a, and is excellent in functionality capable of efficiently supplying the supplied lubricant to the entire outer peripheral surface.

  The spacer main body 4a used in the above-described embodiment shown in FIG. 8C has a dimple-like oil reservoir 12 disposed on the entire outer peripheral surface, instead of the above-described oil groove 11 having a spiral groove shape.

  Thus, by providing the uneven structure for holding the lubricant on the outer peripheral surface of the spacer main body, a solid lubricant such as lubricating grease, lubricating oil, fluorine resin or the like enclosed or supplied in the bearing is used. The required amount of lubricant can be efficiently supplied to the main part or the whole of the outer peripheral surface of the seat body.

DESCRIPTION OF SYMBOLS 1 inner ring 1a outer diameter surface 2 outer ring 3 cylindrical roller 4, 7, 8, 9, 10, 20 spacer 4a, 7a, 8a spacer main body 4b, 9c, 10c circular flange 7b, 8b ring 7c narrow diameter part 7d washer 5 Circumferential groove 6, 11 oil groove 9a, 9b, 10a, 10b split piece 10d pin 12 dimpled oil reservoir 21 side plate 22 bottom surface C pitch circle r rim

Claims (7)

Inner ring, outer ring,
A plurality of cylindrical rollers arranged in the circumferential direction between the inner and outer rings;
A spacer interposed between the cylindrical rollers such that the cylindrical rollers are adjacent to each other in a non-contact state,
Consists of cylindrical roller bearings equipped with
The spacer is rotatably in contact with the outer peripheral surface of the inner ring or the inner peripheral surface of the outer ring, and is disposed between a cylindrical or a cylindrical shape so as to rotatably contact both outer peripheral surfaces of adjacent cylindrical rollers. Cylindrical roller bearings that are seats.   The spacer has a circular flange projecting radially from the outer peripheral surface at both axial ends of the cylinder or cylinder spacer body, and the circular flange is circumferentially formed on the outer peripheral surface of the inner ring or the inner peripheral surface of the outer ring The cylindrical roller bearing according to claim 1, further comprising a circumferential groove or a rim for guiding.   The cylindrical roller bearing according to claim 2, wherein the circular flange is a circular flange formed of a ring or a disk which is detachable to at least one end of the spacer main body.   The cylindrical roller bearing according to claim 2, wherein the circular flange is a circular flange provided on an axially or radially divided and united split piece of the spacer main body.   The cylindrical roller bearing according to any one of claims 2 to 4, wherein the spacer main body is a spacer main body having oil grooves or dimpled oil reservoirs on the outer peripheral surface.   The cylindrical roller bearing according to claim 5, wherein the oil groove is a helical groove which goes around the outer peripheral surface of the spacer main body or a groove which extends in the axial direction of the outer peripheral surface.   The cylindrical roller bearing according to any one of claims 1 to 6, wherein the spacer is made of at least one material selected from metals, synthetic resins and ceramics.

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