JP2006242284A - Cylindrical roller bearing with flange - Google Patents

Abstract

PROBLEM TO BE SOLVED: To realize a structure in which the manufacturing cost does not increase, the structure is easy to handle, and the biting phenomenon of cylindrical rollers 4 and 4 hardly occurs.
SOLUTION: A cage 5 is formed integrally, and pockets 8 and 8 are provided in a portion surrounded by a pair of circular ring portions 15 and column portions 16 and 16. The contact angle θc of the roller holding portion 13 formed in the inner diameter side opening of each of the pockets 8 and 8 is set to 25 to 35 °. Further, the cylindrical rollers 4, 4 are moved in the radial direction, and the rolling surfaces of the cylindrical rollers 4, 4 come into contact with the anti-skid part 10 formed in the outer diameter side opening of the pockets 8, 8. In this case, the diameter of the inscribed circle of each of these cylindrical rollers 4, 4 is IC, and each of these cylindrical rollers 4, 4 when the rolling surface of each of these cylindrical rollers 4, 4 comes into contact with the roller holding part 13 IC + CC-2DM> 0 is satisfied, where CC is the diameter of the circumscribed circle and DM is the pitch circle diameter of the cylindrical rollers 4 and 4.
[Selection] Figure 3

Description

  The flanged cylindrical roller bearing of the present invention is used to support a rotating body that operates at high speed, such as a spindle of a machine tool.

  Bearings for rotatably supporting the spindle of a machine tool are required to have characteristics such as high rigidity, high rotational accuracy, and low heat generation in order to improve the machining accuracy. In recent years, in order to improve processing efficiency, high-speed stability is required so that it can be used stably at a high rotational speed for a long time. Of these characteristics, in order to improve the rigidity in the radial direction, a flanged cylindrical roller bearing is often used as the bearing. In order to further improve the rigidity in the radial direction and improve the rotational accuracy, a so-called preload may be applied to make the internal clearance of the flanged cylindrical roller bearing zero or negative.

  As a cage for holding a cylindrical roller incorporated in a cylindrical roller bearing with a flange used as described above, for example, a cage having a detent portion as described in Patent Documents 1 and 2 has been conventionally used. ing. In order to hold a plurality of cylindrical rollers, this detent portion is elastically deformed when these cylindrical rollers are inserted into openings on the outer diameter side or inner diameter side of pockets formed at a plurality of locations in the circumferential direction of the cage. Thus, the cylindrical rollers can be inserted and the cylindrical rollers are prevented from falling off. In this way, the cage having the stopper portion is separated from one of the ring portions constituting the cage instead of providing the elastically deformable stopper portion of the structure described in Patent Document 2 above. The manufacturing cost can be reduced as compared with the separated type structure, and the assemblability of the flanged cylindrical roller bearing can be improved. In addition, by providing a stopper as described above and restricting the radial position of the cage by engagement with each cylindrical roller, so-called roller guide, the radial position of the cage can be adjusted with the outer ring. Like the outer ring guide regulated by engagement and the cage used in the inner ring guide regulated by engagement with the inner ring, the circumferential surface of the cage and the guide surface (outer ring inner circumferential surface or inner ring outer circumferential surface) It is possible to prevent wear between the two.

  However, as a result of research by the present inventor, it has been found that the following problems occur in the case of the cage having the anti-skid portion. That is, the flanged cylindrical roller bearing that supports a rotating body that rotates at a high speed, such as a main shaft of a machine tool, is used in a state in which a preload is applied with an internal gap of 0 or negative as described above. When used with a preload applied in this way, excessive force is applied to the cage that holds each cylindrical roller due to the skew generated in each cylindrical roller or the difference in rotational speed between these cylindrical rollers. There is a possibility that instrument sound (vibration) is generated or that the cage is easily damaged. According to the inventor's research, it has been found that such a problem is particularly likely to occur in the cage having the anti-skid portion as described above. The reason is as follows. That is, the cage having a detent portion is a roller retainer formed on the opposite side of the detent portion and the opening portion of each pocket opposite to the detent portion, during operation. By making contact, the amount of movement in the radial direction is regulated (positioning in the radial direction of the cage is achieved by roller guidance). When the preload is applied as described above and the rollers are operated in a state where the degree of freedom of the circumferential position of each roller is limited, when each of the cylindrical rollers comes into contact with the detent portion, these cylinders Since the rollers try to bite into these anti-slip portions, the above-described problems occur.

  That is, in order to prevent the cylindrical rollers from falling off, the retainer sets the interval in the circumferential direction of the detent portion present on the outer diameter side or inner diameter side opening of each pocket to the distance between the cylindrical rollers. It is slightly smaller than the diameter. For this reason, when the preload is applied as described above, when these cylindrical rollers come into contact with the detent portions during operation of the cylindrical roller bearing with a flange, these cylindrical rollers are placed between the detent portions. The biting phenomenon (wedge effect) is likely to occur. When such a biting phenomenon occurs, these cylindrical rollers are difficult to rotate, and skew and a difference in rotational speed between the cylindrical rollers are likely to occur. As a result, an excessive force is applied to the cage, and a cage sound may be generated or the cage may be easily damaged.

  In the case of the above-described separation type retainer, since it is not necessary to form a detent portion, it is difficult to cause the biting phenomenon of the cylindrical roller as described above, but there is a problem that the manufacturing cost is increased as described above. . On the other hand, in the case of the structure of the cage described in Patent Document 3, there is an annular portion only on one axial side of the cage, and by continuing the inner surface of the annular portion and a plurality of column portions, A portion surrounded by each of the pillar portions and the ring portion is a pocket. Even in such a structure, the biting phenomenon of the cylindrical roller as described above is unlikely to occur. However, when the cage is incorporated into a flanged cylindrical roller bearing with each cylindrical roller arranged in each pocket, these There is a problem that each cylindrical roller is easy to drop off and handling becomes troublesome.

JP 53-24940 A JP 2001-12477 A JP 11-166544 A

  The cylindrical roller bearing of the present invention was invented in order to realize a structure in which the manufacturing cost does not increase, the structure is easy to handle, and the biting phenomenon of the cylindrical roller hardly occurs in view of the circumstances as described above. Is.

The flanged cylindrical roller bearing of the present invention includes an outer ring, an inner ring, a plurality of cylindrical rollers, and a cage, as in the conventional structure.
Of these, the outer ring is provided with a cylindrical outer ring raceway on the inner peripheral surface.
The inner ring is provided with a cylindrical inner ring raceway on the outer peripheral surface.
Each of the cylindrical rollers is provided between the inner ring raceway and the outer ring raceway so as to roll freely.
The retainer is for retaining the cylindrical rollers. The cage is also arranged with a pair of annular portions arranged at both ends in the axial direction and at equal intervals along the circumferential direction, and both ends are connected to the inner side surfaces of the two annular portions. It consists of a plurality of pillars connected to each other. And, as a plurality of pockets that hold the respective cylindrical rollers in a freely rollable manner inside the respective portions surrounded by both sides in the circumferential direction of each column part and the inner side surfaces of the both ring parts, Is a ring formed integrally.
Further, flanges projecting in the radial direction toward the other raceway are formed over the entire circumference at both ends in the axial direction of the circumferential surface of one raceway of the inner ring and the outer ring. .
In addition, a protrusion that can be elastically deformed when each cylindrical roller is inserted is formed at the radial end on the other raceway side of both sides in the circumferential direction of each column of the cage. . These protrusions constitute a stopper for preventing the cylindrical rollers held in the pockets from slipping out to the other raceway. In addition, the cylindrical rollers held in the respective pockets are pulled out to the one raceway side on the radial end side on the one raceway side of both side surfaces in the circumferential direction of the pillars. The roller holding part is configured to prevent this. And the radial direction position of the said holder | retainer is controlled by engagement with each said cylindrical roller.

In particular, in the cylindrical roller bearing with a flange according to claim 1, when the cage is moved in the radial direction with the cylindrical rollers held in the pockets, Of these, the rolling surface of the cylindrical roller held in a pocket passing through the center of the flanged cylindrical roller bearing and existing on a straight line parallel to the moving direction, and a roller holding portion or a detent portion of the pocket. The contact angle θ, which is the contact angle, is 25 to 35 °.
The contact angle refers to the contact point in the imaginary plane perpendicular to the central axis of the cylindrical roller and the contact point when the rolling surface of the cylindrical roller is brought into contact with the retaining portion or the detent portion. An angle formed between a virtual line connecting a point on the central axis of the cylindrical roller and a second virtual line orthogonal to the radial direction of the cylindrical roller bearing with a flange and passing through the central axis of the cylindrical roller.

In the case of the cylindrical roller bearing with a flange described in claim 2, one of the race rings is an inner ring. For this reason, the collar part is formed in the axial direction both ends of the outer peripheral surface of the inner ring. Further, the roller holding portion is formed on the inner ring side of each pocket, and the anti-slip portion is formed on the outer ring side.
In particular, in the cylindrical roller bearing with a flange according to claim 2, in a state where the cylindrical rollers are held in the pockets, the cylindrical rollers are moved to the outer diameter side, and the cylinders are moved. Let IC be the diameter of the inscribed circle of each of these cylindrical rollers when the rolling contact surface of the roller is brought into contact with the anti-skid portion. The contact angle when the cylindrical rollers are moved to the inner diameter side and the rolling surfaces of the cylindrical rollers are brought into contact with the roller holding portions is defined as θc. In this case, the diameter of the circumscribed circle of each of these cylindrical rollers is CC. Further, the pitch circle diameter in a state where these cylindrical rollers are arranged between the inner ring raceway and the outer ring raceway is defined as DM. The contact angle θc is 25 ° or more and IC + CC−2DM> 0 is satisfied.

In the case of the flanged cylindrical roller bearing described in claim 3, one of the race rings is an outer ring. For this reason, the collar part is formed in the axial direction both ends of the internal peripheral surface of an outer ring | wheel. Further, the roller holding portion is formed on the outer ring side of each pocket, and the detent portion is formed on the inner ring side.
In particular, in the cylindrical roller bearing with a flange according to claim 3, in a state where the cylindrical rollers are held in the pockets, the cylindrical rollers are moved to the outer diameter side, and the cylinders are moved. Let θc be the contact angle when the rolling contact surface of the roller is brought into contact with the roller holding portion. In this case, the diameter of the inscribed circle of each of these cylindrical rollers is IC. Further, the diameter of the circumscribed circle of each cylindrical roller when the respective cylindrical rollers are moved to the inner diameter side and the rolling surfaces of the respective cylindrical rollers are brought into contact with the anti-skid portion is defined as CC. Further, the pitch circle diameter in a state where these cylindrical rollers are arranged between the inner ring raceway and the outer ring raceway is defined as DM. The contact angle θc is 25 ° or more and IC + CC−2DM <0.

  In the case of the present embodiment configured as described above, it is possible to realize a structure in which the manufacturing cost does not increase, the structure is easy to handle, and the biting phenomenon of the cylindrical roller does not occur. That is, unlike the separation type structure described in Patent Document 2 described above, since the cage is integrated, the manufacturing cost does not increase. Further, unlike the structure in which the annular portion is provided only on one side in the axial direction described in Patent Document 3 described above, when the cage is incorporated in a flanged cylindrical roller bearing in a state where each cylindrical roller is disposed in each pocket. These cylindrical rollers are hard to drop off and are easy to handle.

  Further, in the case of the structure described in claim 1, the contact angle θ when each cylindrical roller comes into contact with either one or both of the stopper portion and the holding portion is regulated to 25 to 35 °. Each of these cylindrical rollers can be made difficult to bite against these anti-slip portions or roller holding portions. In the case of the structure described in claim 2 and claim 3, since IC + CC-2DM> 0 (claim 2) or IC + CC-2DM <0 (claim 3), when the cage moves in the radial direction, The rolling surface of each cylindrical roller contacts the roller holding portion of the inner surface of each pocket of the cage, and does not contact the anti-skid portion. Since the contact angle θc with each cylindrical roller holding portion is 25 ° or more, each cylindrical roller can hardly bite against the roller holding portion. Further, since each of these cylindrical rollers does not contact the anti-skid part, each of these cylindrical rollers does not bite into the anti-skid part. As a result, even in the case of any one of claims 1 to 3, the biting phenomenon of the cylindrical roller can be made difficult to occur. In the case of the structures of claims 2 and 3, there is no need to particularly regulate the contact angle of the anti-skid part, which is the side for pushing the roller into the pocket. For this reason, it is sufficient that the interval between the projecting portions constituting the anti-skid portion is slightly larger than the outer diameter of the roller. As a result, a small force is required for assembling the rollers into the pockets.

In order to carry out the present invention, preferably, as described in claim 4, the cage is made of a synthetic resin containing carbon fiber or glass fiber.
If comprised in this way, it is the structure which is hard to generate | occur | produce damages, such as a seizure and remarkable abrasion, on a flanged cylindrical roller bearing, and can make it difficult to produce the biting phenomenon of a cylindrical roller. That is, when the cage is made of a relatively soft metal such as a copper alloy, it is easy to wear, so that wear powder is easily generated from the cage. When the wear powder is mixed with the grease, the grease is deteriorated, the lubricity is lowered, and the flanged cylindrical roller bearing incorporating the cage is likely to be seized or damaged. On the other hand, when the cage is made of synthetic resin, it is excellent in frictional characteristics, so that abrasion powder is hardly generated. For this reason, seizure and damage are unlikely to occur in the flanged cylindrical roller bearing incorporating this cage. However, since synthetic resin has lower rigidity than metal, it is easily deformed when a large load is applied. For this reason, the biting phenomenon of the cylindrical roller is likely to occur. Therefore, it is preferable that the cage is made difficult to deform by containing carbon fiber or glass fiber to increase the Young's modulus, and the biting phenomenon is hardly caused.

  1 to 6 show Embodiment 1 of the present invention corresponding to claims 2 and 4. The flanged cylindrical roller bearing 1 of the present embodiment includes an outer ring 2, an inner ring 3, a plurality of cylindrical rollers 4 and 4, and a cage 5. Among these, the outer ring 2 is provided with a cylindrical outer ring raceway 6 on the inner peripheral surface. The inner ring 3 is provided with a cylindrical inner ring raceway 7 on the outer peripheral surface. The cylindrical rollers 4 and 4 are provided between the inner ring raceway 7 and the outer ring raceway 6 so as to roll freely. The cage 5 is for holding the cylindrical rollers 4 and 4 and is formed in an annular shape that is integrally formed as a whole. That is, the cage 5 includes a pair of annular portions 15 and 15 and a plurality of column portions 16 and 16. Of these, the two annular portions 15, 15 are disposed at both ends in the axial direction. The column parts 16 and 16 are arranged at equal intervals in the circumferential direction, and both end parts thereof are connected to the inner side surfaces of the two ring parts 15 and 15, respectively. And the part enclosed by the circumferential direction both-sides surfaces 11 and 11 of these pillar parts 16 and 16 and the inner surface of both the said annular ring parts 15 and 15 is made into the pockets 8 and 8, respectively. The cylindrical rollers 4 and 4 are held inside the pockets 8 and 8 so as to roll freely. Further, this embodiment shows the case where the present invention is applied to an inner ring collar (N) type. For this purpose, flanges 9 and 9 projecting in the radial direction toward the outer ring 2 are formed on both ends of the inner ring raceway 7 at both axial ends of the outer peripheral surface of the inner ring 3 over the entire circumference. ing.

  In the case of the present embodiment, the cage 5 is made of a synthetic resin such as PPS (polyphenylene sulfide) resin, PEEK (polyethyl ether ketone) resin, PA (polyamide) resin or the like containing carbon fiber or glass fiber. Forming. Specifically, it is formed of any of the above resins (for example, PPS resin) containing 30% by weight of carbon fiber (or glass fiber). In the case of this example, it is preferable that the Young's modulus of the above-described fiber-reinforced synthetic resin constituting the cage 5 is 9 to 25 GPa. That is, the cylindrical roller bearing that supports the spindle of the machine tool incorporating the flanged cylindrical roller bearing 1 of this embodiment may be used at a high speed rotation with a dmN value of 1 million or more, for example, about 1.5 million. The centrifugal force acting on the cage 5 is increased. For this reason, it is necessary to ensure sufficient rigidity of the cage 5 to suppress deformation due to centrifugal force. On the other hand, when the rigidity of the cage 5 is excessively increased, it becomes difficult to elastically deform a detent portion 10 described later, and the work of assembling the cylindrical rollers 4 and 4 into the pockets 8 and 8 is troublesome. Become. For this reason, it is preferable that the Young's modulus of the cage 5 is 9 to 25 GPa.

  Further, in the case of the present embodiment, projecting portions 12a and 12b are formed at the axially central portions at both radial ends of the circumferential side surfaces 11 and 11 of the column portions 16 and 16 of the cage 5. . Among these, the roller holding portion 13 is constituted by the projecting portions 12a, 12a on the inner ring 3 side and the inner diameter side portions of the both side surfaces 11, 11. Further, the protrusions 12b and 12b on the outer ring 2 side constitute a detent portion 10 that can be elastically deformed when the cylindrical rollers 4 and 4 are inserted. The roller holding portion 13 and the anti-slip portion 10 allow the cylindrical rollers 4, 4 held in the pockets 8, 8 before the cage 5 is incorporated into the flanged cylindrical roller bearing 1. It prevents it from slipping out to the inner diameter side or outer diameter side. Further, in the state in which the cage 5 is incorporated in the cylindrical roller bearing 1 with a flange, a roller guide is provided that regulates the radial position of the cage 5 by engagement with the cylindrical rollers 4 and 4.

  The shape of the side surfaces 11 and 11 of the pillars 16 and 16 constituting the pockets 8 and 8 will be described more specifically. Of these side surfaces 11, 11, the roller holding portion 13 portion is a curved surface portion having a radius of curvature R slightly larger than the radius (DA / 2) of each cylindrical roller 4, 4. Further, of the side surfaces 11, 11, the inner diameter side portion of the protruding portions 12 b, 12 b constituting the detent portion 10 on the outer diameter side of the pitch circle P (diameter DM) of the cylindrical rollers 4, 4. Is a plane portion in which the surfaces facing each other are parallel to each other, and the circumferential interval (pocket width) between these surfaces is DP. The pitch circle diameter DM is a circle (pitch circle P) passing through the centers of the cylindrical rollers 4 and 4 when the cylindrical rollers 4 and 4 are arranged between the outer ring raceway 6 and the inner ring raceway 7. ). The position of the retainer 5 shown in FIG. 2 is not biased in the radial direction, in other words, the distance between the outer peripheral surface of the retainer 5 and the inner peripheral surface of the outer ring 2 (or the retainer 5 The distance between the inner circumferential surface of the inner ring 3 and the outer circumferential surface of the inner ring 3 is uniform in the circumferential direction. Further, the circumferential distance Dd between the projecting portions 12b and 12b of the anti-skid portion 10 constituting the outer diameter side opening portions of the side surfaces 11 and 11 is slightly smaller than the diameter DA of the cylindrical rollers 4 and 4. (Dd <DA).

  In particular, in the case of the flanged cylindrical roller bearing 1 of this embodiment, the anti-skid part 10 and the holding part 13 are formed so as to satisfy the following requirements. This requirement will be described with reference to FIG. With the cylindrical rollers 4 and 4 held in the pockets 8 and 8 (not incorporated in the flanged cylindrical roller bearing 1), the cylindrical rollers 4 and 4 are moved to the outer diameter side. The contact angle when the rolling surfaces of the cylindrical rollers 4 and 4 and the anti-skid portion 10 are brought into contact (in the case of the positional relationship between the left cylindrical roller 4 and the pocket 8 in FIG. 3) is expressed as θd. To do. The diameter of the inscribed circle of each of the cylindrical rollers 4 and 4 in this state is IC. Further, when the cylindrical rollers 4 and 4 are moved to the inner diameter side and the rolling surfaces of the cylindrical rollers 4 and 4 are brought into contact with the roller holding portion 13 (the cylindrical roller 4 on the right side in FIG. 3). And the contact angle of the pocket 8) is θc. The diameter of the circumscribed circle of each of the cylindrical rollers 4 and 4 in this state is CC.

In addition, the said contact angle means the following angles. That is, the cylindrical roller 4 and the cage 5 are moved relative to each other in the radial direction of the cage 5 to bring the rolling surface of the cylindrical roller 4 into contact with the detent portion 10 or the roller holding portion 13. In this case, if no force is applied to the contact portion (if no load is applied), the rolling surface of the cylindrical roller 4 and the anti-blocking portion 10 or the roller holding portion 13 are in line contact. In this case, the following two imaginary lines in the imaginary plane perpendicular to the central axis of the cylindrical roller 4 are defined. That is, a virtual line connecting a point (contact point) on the contact line and a point on the central axis of the cylindrical roller 4 in the virtual plane is defined as α ₁ or α ₂ . Further, a second imaginary line orthogonal to the radial direction of the flanged cylindrical roller bearing 1 and passing through the central axis of the cylindrical roller 4 is β ₁ or β ₂ . The angles formed by the imaginary line α ₁ or α ₂ defined in this way and the second imaginary line β ₁ or β ₂ are referred to as the contact angles θd and θc.

  In the case of the present embodiment, the contact angle θd on the anti-skid part 10 side is reduced to such an extent that the cylindrical rollers 4 can be inserted by elastically deforming the projecting parts 12b, 12b constituting the anti-skid part 10. . For this reason, if the rolling surface of the cylindrical roller 4 comes into contact with the anti-skid part 10 during operation, the cylindrical roller 4 tends to bite against the anti-skid part 10. On the other hand, the contact angle θc on the roller holding part 13 side is made larger than the contact angle θd on the anti-skid part 10 side (θc> θd) and within a range of 25 to 35 ° (25 ° ≦ θc ≦ 35).゜). Further, the pitch circle diameter in a state where the cylindrical rollers 4 and 4 are arranged between the inner ring raceway 7 and the outer ring raceway 6 (the positional relationship between the cylindrical roller 4 in the center of FIG. 3 and the pocket 8). When DM is set, IC + CC-2DM> 0 is satisfied. That is, in this embodiment, the contact angle θc on the roller holding portion 13 side is set to 25 to 35 °, and IC + CC−2DM> 0 is satisfied. The reason for this restriction will be explained.

  First, the contact angle θc on the roller holding portion 13 side is set to 25 ° or more. When θc is less than 25 °, the frictional force generated between the rolling surface of the cylindrical roller 4 and the holding portion 13 increases. This is because the biting phenomenon is likely to occur. That is, as shown by the positional relationship between the cylindrical roller 4 on the right side of FIG. 3 and the pocket 8, when a force F directed radially inward acts on the cylindrical roller 4, the rolling surface of the cylindrical roller 4 and the above-described The frictional force Fm generated between the roller holding portion 13 is expressed by Fm = μ · F / sin (θc), where μ is a friction coefficient. Since θc is in the range of 0 ° <θc <90 °, the value of the frictional force Fm decreases as the value of θc increases. For this reason, in the case of the present embodiment, this θc is set to 25 ° or more to suppress the increase of the frictional force Fm. Preferably, θc ≧ 30 °, where 1 / sin (θc) ≦ 2.

  On the other hand, the reason why the contact angle θc on the roller holding portion 13 side is set to 35 ° or less is that the inner diameter of the cage 5 becomes too small in order to secure a larger contact angle. If the inner diameter is too small, the cage 5 cannot be assembled. Even if the cage 5 is assembled, when the cage 5 is displaced in the axial direction, the flanges 9, 9 formed on the inner circumferential surface of the cage 5 and the outer circumferential surfaces of both end portions in the axial direction of the inner ring 3, or Depending on the shape of the inner peripheral surface of the cage 5, there is a possibility that the inner ring raceway 7 interferes. In other words, the maximum value of the contact angle θc is restricted due to the geometric reason that the inner diameter of the cage 5 cannot be further reduced due to the presence of the flanges 9 and 9 or the inner ring raceway 7. Therefore, if the contact angle θc can be increased in relation to the flanges 9 and 9 or the inner ring raceway 7, the angle θc may be larger than 35 °. Considering only the reduction of the frictional force between the roller holding portion 13 and the outer peripheral surface of the cylindrical roller 4, the inner diameter of the cage 5 is slightly smaller than the outer diameter of the flange portions 9 and 9 (holding) It is preferable to make θc as large as possible until the device 5 is elastically deformed and can be fitted on the inner ring 3. However, in the case of the cylindrical roller bearing 1 with a flange according to the present embodiment, since the cage 5 is used as a roller guide, it is necessary to secure a gap between the inner peripheral surface of the cage 5 and the flange portions 9 and 9. . For this reason, in the case of the present embodiment, the axially opposite end inner circumferential surfaces of the cage 5 are inclined in the direction facing the outer diameter side toward the end side toward the end portions 9 and 9. Escapes 20, 20 are formed.

  Next, the reason why IC + CC-2DM> 0 will be described. When it is assumed that the cage 5 can move in the radial direction until it comes into contact with the anti-skid portion 10, the amount of movement Md in the radial direction of the cage 5 is Md = IC− (DM−DA). . On the other hand, when it is assumed that the cage 5 can move in the radial direction until it comes into contact with the roller holding portion 13, the radial movement amount Mc of the cage 5 is Mc = (DM + DA) −CC. Become. If Md> Mc, when the cage 5 moves in the radial direction, the rolling surface of the cylindrical roller 4 is always in contact with the roller holding portion 13 and is in contact with the detent portion 10. There is no.

  That is, if Md> Mc, as shown in FIGS. 4 and 5, when the cage 5 moves upward in FIGS. 4 and 5, the center of the cylindrical roller bearing 1 with a flange is one of the pockets 8 and 8. And the roller holding portion 13 of the pocket 8 existing on the straight line L parallel to the moving direction of the cage 5 is in contact with the rolling surface of the cylindrical roller 4 held in the pocket 8 {FIG. (A)}. On the other hand, the detent portion 10 of the pocket 8 that exists on the straight line L and is symmetrical to the pocket 8 in FIG. 5A, and the rolling of the cylindrical roller 4 held in the pocket 8 It does not contact the surface {FIG. 5B}. For this reason, if Md> Mc, that is, IC− (DM−DA)> (DM + DA) −CC is satisfied, the rolling surface of the cylindrical roller 4 and the detent portion 10 are moved by the radial movement of the cage 5. Will not touch. Therefore, by arranging the above formula and satisfying IC + CC−2DM> 0, the amount of movement of the cage 5 in the radial direction is such that the roller holding portion 13 and the rolling surface of the cylindrical roller 4 are in contact with each other. Regulated by things.

  Since the roller holding portion 13 has a contact angle θc of 25 to 35 ° as described above, even if the cylindrical roller 4 and the roller holding portion 13 come into contact with each other, the cylindrical roller 4 has this roller. It becomes difficult to bite the settling portion 13. Even if the cage 5 moves in the radial direction, the amount of movement of the cage 5 is restricted by the roller holding portion 13 and the rolling surface of the cylindrical roller 4 coming into contact with each other. The detent part 10 and the rolling surface of the cylindrical roller 4 do not come into contact with each other. Therefore, the cylindrical rollers 4 and 4 do not bite against the stopper 10. When the cage cylindrical roller bearing 1 is operated at a high speed, if the cage is made of synthetic resin having low rigidity, the cage may be deformed by centrifugal force and the amount of movement of the cage may be restricted as described above. There is a possibility that the detent portion and the rolling surface of the cylindrical roller come into contact with each other. On the other hand, in the case of the present embodiment, the Young's modulus of the cage 5 is increased by fiber reinforcement, so that deformation due to centrifugal force is suppressed and the rolling surface of the cylindrical roller 4 comes into contact with the anti-separation portion 10. Can be prevented more reliably.

  In the case of the present embodiment, the circumference of the cage 5 is defined by a gap (pocket clearance) between the side surfaces 11 and 11 of the pockets 8 and 8 of the cage 5 and the rolling surfaces of the cylindrical rollers 4 and 4. In consideration of the amount of motion in the direction, it is preferable that IC + CC-2DM-4 (DP-DA)> 0 is satisfied. That is, the cage 5 is movable in the circumferential direction with respect to the cylindrical rollers 4 and 4 by the pocket gap. Then, due to the relative movement of the cage 5 in the circumferential direction, the rolling surfaces of the cylindrical rollers 4 and 4 may come into contact with one protruding portion 12b of the detent portion 10. In this way, when one projecting portion 12b of the anti-skid part 10 and the rolling surface of the cylindrical roller 4 come into contact with each other, there is a possibility that the rolling surface of this cylindrical roller 4 bites into this anti-skid part 10. . On the other hand, if the above-mentioned IC + CC-2DM-4 (DP-DA)> 0 is satisfied, the outer peripheral surface of the cylindrical roller 4 is the one protruding portion even if the cage 5 moves relative to the circumferential direction. The cylindrical roller 4 is prevented from coming into contact with the anti-slip portion 10 by preventing contact with 12b.

The reason for restricting IC + CC-2DM-4 (DP-DA)> 0 will be described. As shown by the positional relationship between the cylindrical roller 4 and the pocket 8 in the center of FIG. 6, the rolling surface of the cylindrical roller 4 comes into contact with the protruding portion 12b on one side (right side of FIG. 6) of the detent portion 10. _Let IC _a be the diameter of the inscribed circle of each cylindrical roller 4 when it is assumed. In addition, the contact angle at this time is θd _a. In order to prevent the rolling surface of each cylindrical roller 4 and the one protruding portion 12b from coming into contact with each other due to the relative movement of the cage 5 with respect to each cylindrical roller 4 in the circumferential direction, IC _a + CC− It is sufficient to satisfy 2DM> 0. That is, the radial movement of the cage 5 with respect to the relative movement amount of the cage 5 in the circumferential direction so that the rolling surfaces of the cylindrical rollers 4 do not come into contact with the one protruding portion 12b. What is necessary is just to regulate quantity. Specifically, as shown in the center of FIG. 6, the retainer 5 moves downward in FIG. 6, and the distance between the rolling surface of the cylindrical roller 4 and the anti-skid portion 10 is reduced. When the cage 5 is relatively moved in the circumferential direction by the pocket gap, the rolling surface of the cylindrical roller 4 and the one protruding portion 12b of the detent portion 10 are easily brought into contact with each other. Accordingly, the pocket gap, which is the maximum amount of movement relative to the cylindrical roller 4 in the circumferential direction of the cage 5, and the amount of movement of the cage 5 in the direction perpendicular to the central axis of the cage 5. If the relationship is restricted, it is possible to prevent the rolling surface of the cylindrical roller 4 and the one protruding portion 12b from contacting each other regardless of the relative movement of the cage 5 in the circumferential direction.

As is apparent from FIG. 6, the diameter IC (see the left side of FIG. 6) of the inscribed circle of each cylindrical roller 4 when each cylindrical roller 4 is moved to the outer diameter side and the outer peripheral surface is brought into contact with the detent portion 10. ) And the above IC _a is IC _a = IC−DA {sin (θd) −sin (θd _a )}. Further, sin (θd) = √ {1- (Dd / DA) ² }, sin (θd _a ) = √ [1- {Dd− (DP−DA)} ² / DA ² ]. Incidentally, Dd is a circumferential interval of the detent portion 10, DP is a circumferential interval between the flat portions of the side surfaces 11, 11 of the pocket 8, that is, an interval between these both side surfaces 11, 11. Each maximum value (pocket width) is shown. Therefore, (DP-DA) indicates a pocket gap. Here, (Dd / DA) ² normally needs 0.91 to 0.96 in order to insert the cylindrical roller 4 from the detent portion 10. When DA >> (DA-Dd), DA >> (DP-DA), and x≈15 / 16 = 0.9375, √ (1−x) ≈1 / 4−2 (x−15 / 16) ), When _ICa is approximated and organized, _ICa = IC-4 (DP-DA) is obtained. Accordingly, IC + CC-2DM-4 (DP-DA)> 0 is obtained by substituting into IC _a + CC-2DM> 0. If constituted in this way, regardless of the relative movement of the cage 5 in the circumferential direction, the rolling surface of the cylindrical roller 4 and the one protruding portion 12b of the detent portion 10 are prevented from coming into contact with each other, This cylindrical roller 4 can be made difficult to bite against the anti-slip portion 10.

  In the case of the present embodiment, the retainer 5 holding the cylindrical rollers 4 and 4 in the pockets 8 and 8 is arranged on the outer diameter side of the inner ring 3 and can be easily incorporated into the outer ring 2. Therefore, the size c of the chamfers 19 and 19 formed at both ends of the inner peripheral surface of the outer ring 2 is regulated as follows. That is, as shown in FIG. 1, the size c of the double-sided chamfers 19 and 19 is larger than (IC + 2DA-CC) / 2 {c> (IC + 2DA-CC) / 2}. The falling amount of each cylindrical roller 4, 4 in the state where each cylindrical roller 4, 4 is held in each pocket 8, 8 of the cage 5 (the maximum amount of movement of each cylindrical roller 4, 4 in the radial direction) is , (IC + 2DA-CC) / 2. Therefore, if the size c of the double-sided chamfering 19, 19 is made larger than the drop amount (IC + 2DA-CC) / 2, the cage 5 holding the cylindrical rollers 4, 4 is placed on the outer circumferential surface of the inner ring 3. Since it can be smoothly inserted from the axial direction into the inner diameter side of the outer ring 2 in the arranged state, the assemblability can be improved.

  FIG. 7 shows a second embodiment of the present invention corresponding to claims 1 and 2. In this embodiment, the cage 5a is formed of a copper alloy such as brass. In this way, when the cage 5a is made of a copper alloy, the pockets 8 and 8 need to be formed by shaving at a plurality of locations in the circumferential direction of the cage 5a. For this reason, in this embodiment, reliefs 14 and 14 are formed at the four corners of the pockets 8 and 8, respectively. Other configurations and operations are the same as those in the first embodiment.

  FIG. 8 shows Embodiment 3 of the present invention corresponding to claims 1, 2, and 4. In the case of the present embodiment, the cage 5b is made of a synthetic resin containing carbon fibers or glass fibers as in the first embodiment. However, in the case of the present embodiment, in order to form the retainer 5b by injection molding, the protrusions 12b and 12b constituting the detents 10 and 10 of the pockets 8 and 8 are arranged in the circumferential direction. V-shaped reliefs 14a and 14a are formed between adjacent protrusions 12b and 12b. That is, in the portion between the pockets 8 adjacent to each other in the circumferential direction, there are column portions 16 and 16 that connect the annular portions 15 and 15 constituting both axial ends of the cage 5b. . Each of the protrusions 12b and 12b is provided in a pair in the axial central portion of the retainer 5b on the outer peripheral surface of the pillars 16 and 16, and is opposite to each other toward the inside of the pockets 8 and 8. Protruding. In the case of the present embodiment, a V-shaped gap is formed between the projecting portions 12b, 12b provided in pairs as described above, and the distance between the protruding portions 12b increases toward the outer diameter side. The escapes 14a and 14a are set.

  In the case of this embodiment configured as described above, when the molds for forming the pockets 8 and 8 are pulled out in the radial direction during injection molding, the protrusions 14a and 14a cause the protrusions. The parts 12b and 12b are easily elastically deformed. For this reason, the removal work of this metal mold | die becomes easy, and work efficiency improves. In the case of the present embodiment, the projecting portions 12a, 12a constituting the roller holding portions 13, 13 formed on the inner diameter side of the pockets 8, 8 are separated at two locations in the axial direction of the cage 5b. Formed in position. Other configurations and operations are the same as those of the first embodiment.

  9 to 10 show a fourth embodiment of the present invention corresponding to claims 3 and 4. In the case of the present embodiment, unlike the first embodiment, the present invention is applied to an outer ring collar (NU) -type flanged cylindrical roller bearing 1a. That is, in the case of the present embodiment, the flanges 9 and 9 projecting toward the inner ring 3a are formed over the entire circumference at both axial ends of the inner circumferential surface of the outer ring 2a. In the case of this embodiment configured as described above, the side surfaces 11a and 11a of the column portions 16 and 16 constituting the pockets 8 and 8 formed at a plurality of circumferential positions of the cage 5c incorporated in the cylindrical roller bearing 1a with a flange are formed. The shape is configured as follows. That is, in the case of the present embodiment, out of the protrusions 12a and 12b formed at both ends in the radial direction of the respective side surfaces 11a and 11a, the protrusions 12a and 12a on the outer ring 2a side and the outer sides of the side surfaces 11a and 11a. The roller holding portion 13 is constituted by the radial side portion, and the anti-separation portion 10 is constituted by the projecting portions 12b and 12b on the inner ring 3a side. Further, in the case of the present embodiment, of the side surfaces 11a and 11a, the outer diameter side portion of the cylindrical roller 4 and 4 and the outer diameter side portion of the detent portion 10 on the inner diameter side of the pitch circle P (diameter DM). The pockets 8 and 8 are planes parallel to each other.

  In the case of the present embodiment, the cylindrical rollers 4, 4 are moved to the outer diameter side in the state where the cylindrical rollers 4, 4 are held in the pockets 8, 8, respectively. When the rolling surfaces 4 and 4 are brought into contact with the roller holding portion 13 (in the case of the positional relationship between the cylindrical roller 4 on the right side of FIG. 10 and the pocket 8), the contact angle is θc. The diameter of the inscribed circle of each of the cylindrical rollers 4 and 4 is IC. Further, when the cylindrical rollers 4 and 4 are moved to the inner diameter side and the rolling surfaces of the cylindrical rollers 4 and 4 are brought into contact with the detent portion 10 (with the cylindrical roller 4 on the left side in FIG. 10). The contact angle in the case of the positional relationship with the pocket 8 is θd, and the diameter of the circumscribed circle of the cylindrical rollers 4 and 4 in this state is CC. The contact angle θc on the roller holding part 13 side is made larger than the contact angle θd on the anti-skid part 10 side, and the contact angle θc on the roller holding part 13 side is set to 25 to 35 °.

  Furthermore, IC + CC−2DM <0 is satisfied when the pitch circle diameter in the state where the cylindrical rollers 4 and 4 are arranged between the inner ring raceway 7 and the outer ring raceway 6 is DM. That is, in this embodiment, the roller holding portion 13 is formed on the outer diameter side of each pocket 8, 8. For this reason, unlike the above-described first embodiment, the size, shape, etc. of each part are regulated so that IC + CC-2DM <0, and the rolling surface of each cylindrical roller 4, 4 and each of the above are moved by the movement of the cage 5c. It is made for the detent part 10 which exists in the internal diameter side of the pockets 8 and 8 not to contact. In consideration of relative movement of the cage 5c with respect to the cylindrical rollers 4 and 4 in the circumferential direction, it is preferable to satisfy CC + IC-2DM-4 (DP-DA) <0. Further, in order to improve the ease of assembling the cage 5c holding the cylindrical rollers 4 and 4 into the flanged cylindrical roller bearing 1a, the size c of the chamfers 19 and 19 formed at both ends of the outer peripheral surface of the inner ring 3a is set. , (IC + 2DA-CC) / 2. Other structures and operations are the same as those of the first embodiment.

  11 to 14 show a fifth embodiment of the present invention corresponding to claims 1 and 4. In the case of the present embodiment, the case where the present invention is applied to the inner ring collar (N) -type flanged cylindrical roller bearing 1 is shown, as in the first embodiment. Accordingly, the stoppers 10 are formed in the outer diameter side openings of the pockets 8 and 8, and the roller holding portions 13 are formed in the inner diameter side openings of the pockets 8 and 8. However, in this embodiment, IC + CC-2DM> 0 is not satisfied. For this reason, as shown in FIGS. 13 to 14, for example, when the cage 5d moves upward in the figure, the cylindrical rollers 4 held in the pockets 8 and 8 existing in the moving direction of the cage 5d, 4, one (upper side in FIG. 13) of the cylindrical roller 4 comes into contact with the roller holding part 13 (FIG. 14A), and the other (lower side in FIG. 13) of the cylindrical roller 4 comes into contact with the detent part 10. (FIG. 14B). That is, in the case of the structure of the present embodiment, the cylindrical rollers 4 and 4 can come into contact with any part of the roller holding portion 13 and the detent portion 10 by the movement of the cage 5d. For this reason, in the case of the present embodiment, the contact angle θd between the rolling surface of the cylindrical roller 4 and the detent portion 10 is similar to the contact angle θc with the rolling surface and the holding portion 13 of the cylindrical roller 4. Is also restricted to 25-35 °. As a result, even when the cylindrical roller 4 comes into contact with any part of the roller holding part 13 and the detent part 10 by the movement of the cage 5d, the cylindrical roller 4 has these roller holding parts 13. Or it becomes difficult to bite against the anti-separation part 10.

  In the case of this embodiment, in order to increase the contact angle θd on the anti-skid part 10 side, the circumferential distance Dd of the anti-skid part 10 is made small. Then, in order to prevent the cylindrical roller 4 from becoming difficult to insert as the distance Dd is reduced, the outer peripheral surfaces of the column parts 16 and 16 of the cage 5d are adjacent to each other in the circumferential direction, Groove portions 17 and 17 are formed between the protruding portions 12b and 12b constituting the detent portions 10 and 10, respectively. Further, taper portions 18 and 18 are formed on the outer diameter side of the anti-skid portions 10 and 10, which are inclined in a direction in which the distance between the circumferential directions increases toward the outer side in the radial direction. When the cylindrical rollers 4 and 4 are inserted into the pockets 8 and 8, the cylindrical rollers 4 and 4 are guided by the taper portions 18 and 18, so that the cylindrical rollers 4 and 4 are connected to the outer diameter sides of the pockets 8 and 8. It becomes easy to introduce into the opening. The presence of the groove portions 17 and 17 can increase the amount of elastic deformation of the anti-skid portions 10 and 10, so that the cylindrical rollers 4 and 4 can be easily inserted into the pockets 8 and 8. The structure of the present embodiment can also be applied to an outer ring collar (NU) -type flanged cylindrical roller bearing as shown in the above-described fourth embodiment. Of course, in this case, the groove portions 17 and 17 and the taper portions 18 and 18 are formed on the inner diameter side of the cage. Other structures and operations are the same as those in the first and fourth embodiments.

The fragmentary sectional view which shows Example 1 of this invention. II sectional drawing of FIG. The figure equivalent to the II cross section of FIG. 1 which shows three examples of the positional relationship of this cylindrical roller and a pocket when a cylindrical roller is moved to radial direction, taking out a cylindrical roller and a holder | retainer. Sectional drawing of the whole flanged cylindrical roller bearing of Example 1 which shows the case where a cage | basket is moved to the direction orthogonal to the central axis of this cage | basket. (A) is an enlarged view of the portion B in FIG. 4, and (B) is an enlarged view of the portion C in FIG. The same figure as FIG. 3 shown in order to demonstrate the case where the case where a holder | retainer moved to the circumferential direction is considered. The perspective view which shows the holder | retainer integrated in Example 2 of this invention. The perspective view which similarly shows the holder | retainer integrated in Example 3. FIG. Similarly, the fragmentary sectional view which shows Example 4. FIG. The figure similar to FIG. 3 corresponding to the knee cross section of FIG. The fragmentary sectional view which shows Example 5 of this invention. FIG. 12 is a sectional view of the hoe of FIG. 11. The figure similar to FIG. 4 which shows the cylindrical roller bearing with a flange of Example 5. FIG. FIG. 14A is an enlarged view of a portion F of FIG. 13, and FIG. 13B is an enlarged view of a portion G of FIG.

Explanation of symbols

DESCRIPTION OF SYMBOLS 1, 1a Cylindrical roller bearing 2, 2a Outer ring 3, 3a Inner ring 4 Cylindrical roller 5, 5a-5d Cage 6 Outer ring raceway 7 Inner ring raceway 8 Pocket 9 Gutter part 10 Detent part 11, 11a Side face 12a, 12b Protrusion part 13 Rolling part 14, 14a Escape 15 Annulus part 16 Column part 17 Groove part 18 Taper part 19 Chamfer 20 Escape

Claims (4)

  An outer ring provided with a cylindrical outer ring raceway on the inner peripheral surface, an inner ring provided with a cylindrical inner ring raceway on the outer peripheral surface, and a plurality of cylindrical rollers provided between the inner ring raceway and the outer ring raceway so as to be able to roll. And a retainer for retaining each of these cylindrical rollers, the retainer being disposed at equal intervals from each other in the circumferential direction with a pair of annular portions disposed at both axial ends. A plurality of column portions each having both end portions connected to the inner side surfaces of the two annular portions, and surrounded by both circumferential sides of the respective column portions and the inner surfaces of the two annular portions. The annular portion is formed as a plurality of pockets inside each of the cylindrical rollers so as to be able to roll freely, and the whole is integrally formed, and the circumference of one of the inner ring and the outer ring is At both ends in the axial direction of the surface, ridges projecting in the radial direction toward the other raceway ring over the entire circumference Protruding portions that can be elastically deformed when the cylindrical rollers are inserted are formed at the radial end portions on the other raceway side in the circumferential side surfaces of the pillar portions of the cage. The cylindrical rollers held in the pockets by the protruding portions constitute a detent portion for preventing the cylindrical rollers from coming out to the other raceway side, and the circumferential direction of the column portions A roller holding portion for preventing the cylindrical rollers held in the pockets from slipping out to the one raceway side on the radial end of the one raceway side on both side surfaces. In the flanged cylindrical roller bearing that restricts the radial position of the cage by engagement with the cylindrical rollers, the cylindrical rollers are held in the pockets. Move the container in the radial direction, and In a state where the rolling surface of the cylindrical roller held in a pocket passing through the center of the cylindrical roller bearing and on a straight line parallel to the moving direction is in contact with the roller holding portion or the detent portion of the pocket, A virtual line connecting the contact point and a point on the central axis of the cylindrical roller in a virtual plane orthogonal to the central axis of the cylindrical roller, and orthogonal to the radial direction of the flanged cylindrical roller bearing and the above A flanged cylindrical roller bearing characterized in that a contact angle θ, which is an angle formed with a second imaginary line passing through the central axis of the cylindrical roller, is 25 to 35 °.   An outer ring provided with a cylindrical outer ring raceway on the inner peripheral surface, an inner ring provided with a cylindrical inner ring raceway on the outer peripheral surface, and a plurality of cylindrical rollers provided between the inner ring raceway and the outer ring raceway so as to be able to roll. And a retainer for retaining each of these cylindrical rollers, the retainer being disposed at equal intervals from each other in the circumferential direction with a pair of annular portions disposed at both axial ends. A plurality of column portions each having both end portions connected to the inner side surfaces of the two annular portions, and surrounded by both circumferential sides of the respective column portions and the inner surfaces of the two annular portions. The outer ring is formed as a plurality of pockets that hold the cylindrical rollers on the inner side so as to be able to roll, and the outer ring is formed at both ends in the axial direction of the outer peripheral surface of the inner ring. Each of the pillars of the cage is formed with ridges projecting in the radial direction toward the entire circumference. Of the two circumferential side surfaces of the outer ring, the outer ring side radial end is formed with a protrusion that can be elastically deformed when the cylindrical rollers are inserted, and held by the protrusions in the pockets. The cylindrical roller constitutes a detent portion for preventing the cylindrical roller from slipping out to the outer ring side, and the radial end portion side on the inner ring side of the circumferential side surfaces of the column portions is A roller holding portion is provided to prevent the cylindrical rollers held in the pockets from slipping out toward the inner ring, and the radial position of the cage is restricted by engagement with the cylindrical rollers. In a cylindrical roller bearing with a flange, in a state where the cylindrical rollers are held in the pockets, the cylindrical rollers are moved to the outer diameter side so that the rolling surfaces of the cylindrical rollers and the detent portions Of these cylindrical rollers in contact with The virtual plane perpendicular to the central axis of each cylindrical roller when the diameter of each of the cylindrical rollers is moved to the inner diameter side and the rolling surface of each cylindrical roller is in contact with the roller holding portion Imaginary lines connecting the respective contact points and the points on the central axes of the cylindrical rollers, and a first line perpendicular to the radial direction of the flanged cylindrical roller bearing and passing through the central axes of the cylindrical rollers. The contact angle, which is the angle formed by the two imaginary lines, is θc, the circumscribed circle diameter of each cylindrical roller in this case is CC, and each cylindrical roller is arranged between the inner ring raceway and the outer ring raceway. A cylindrical roller bearing with a flange, wherein the contact angle θc is 25 ° or more and IC + CC−2DM> 0 when the pitch circle diameter is DM.   An outer ring provided with a cylindrical outer ring raceway on the inner peripheral surface, an inner ring provided with a cylindrical inner ring raceway on the outer peripheral surface, and a plurality of cylindrical rollers provided between the inner ring raceway and the outer ring raceway so as to be able to roll. And a retainer for retaining each of these cylindrical rollers, the retainer being disposed at equal intervals from each other in the circumferential direction with a pair of annular portions disposed at both axial ends. A plurality of column portions each having both end portions connected to the inner side surfaces of the two annular portions, and surrounded by both circumferential sides of the respective column portions and the inner surfaces of the two annular portions. The annular portion is formed as a whole as a plurality of pockets holding the respective cylindrical rollers in a rollable manner inside each of the portions, and the axial portions at both ends in the axial direction of the inner peripheral surface of the outer ring. Each flange of the cage is formed with a flange projecting radially toward the inner ring over the entire circumference. Of the two circumferential side surfaces of the inner ring, the inner ring side radial end is formed with a protrusion that can be elastically deformed when the cylindrical rollers are inserted, and held by the protrusions in the pockets. The cylindrical roller constitutes a detent portion for preventing the cylindrical roller from slipping out to the inner ring side, and the radial end portion side of the outer ring side, on both sides in the circumferential direction of the column portion, A roller holding portion is provided to prevent each cylindrical roller held in each pocket from coming out to the outer ring side, and the radial position of the cage is restricted by engagement with each cylindrical roller. In the cylindrical roller bearing, the cylindrical rollers are held in the pockets, the cylindrical rollers are moved to the outer diameter side, and the rolling surfaces of the cylindrical rollers and the roller holding portions are moved. To the central axis of each of these cylindrical rollers An imaginary line connecting these contact points and a point on the central axis of each cylindrical roller in an intersecting virtual plane, and perpendicular to the radial direction of the flanged cylindrical roller bearing and the center of each cylindrical roller The contact angle, which is the angle formed with the second imaginary line passing through the axis, is θc, and the diameter of the inscribed circle of each cylindrical roller in this case is IC, and each cylindrical roller is moved to the inner diameter side, The diameter of the circumscribed circle of each cylindrical roller when the rolling contact surface of the cylindrical roller is in contact with the anti-skid part is CC, and each cylindrical roller is disposed between the inner ring raceway and the outer ring raceway. A cylindrical roller bearing with a flange, wherein the contact angle θc is 25 ° or more and IC + CC−2DM <0, where DM is a pitch circle diameter.   The flanged cylindrical roller bearing according to any one of claims 1 to 3, wherein the cage is made of a synthetic resin containing carbon fiber or glass fiber.

Images