JP2007057076A - Roller bearing for steering device - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To provide a roller bearing for a steering device having an increased load capacity and improved durability, preventing a feel of stiffness and rattling while achieving improved assembling efficiency and improved accuracy. <P>SOLUTION: The roller bearing for a steering device comprises two ring-shaped inner and outer cages 3, 13 each having a plurality of pockets 4 arranged side by side in the circumferential direction, and a plurality of rolls 2 held over the pockets 4 of the two cages 3, 13. The inside cage 3 holds the rolls 2 at their inner diameter sides and its columnar portions 5 each have an outer diameter d3o smaller than a pitch circle diameter PCD of a roller array. The outside cage 13 holds the rolls 2 at their outer diameter sides and its columnar portions 5 each have an inner diameter d13i larger than the pitch circle diameter PCD of the roll array. The inside and outside cages 3, 13 have slits 7, 7A provided at a plurality of positions in the circumferential direction and cut out from one-side edges of the cages 3, 13 near the other-side edges. <P>COPYRIGHT: (C)2007,JPO&INPIT

Description

  The present invention relates to a roller bearing used in a clutch for automatic / manual switching of steering provided in a steering operation transmission system of a steering device.

2. Description of the Related Art In recent years, automatic driving control technology for automobiles has been advanced so as to recognize not only the center line but also the positional relationship with other vehicles to control speed and steering. The automatic steering system is required to have a function of switching to manual driving so that the driver can operate as necessary even during automatic driving. For example, in order to cope with an emergency situation, it is required that the driver can switch from an automatic steering mode to a manual operation mode in which a steering force is generated.
In response to this demand, various steering devices having a function of switching to manual driving so that the driver can steer as necessary even during automatic driving have been proposed (for example, Patent Documents 1 to 3). Various clutch mechanisms are used for automatic / manual switching of steering of the steering device.

  An example of a clutch mechanism used for automatic / manual switching of steering of such a steering device is shown in FIG. In this clutch mechanism, a plurality of cams 32 are arranged on the outer periphery of a center shaft 34 serving as a shaft on the clutch output side, and a sliding bearing 33 is interposed between the cam 32 and the inner diameter surface of the housing 35. The cams 32 are wedge-shaped, and a pair of the center shafts 34 facing each other in the opposite direction of the circumferential direction form a pair, and one or a plurality of sets are arranged in the circumferential direction. Each of the cams 32 is held for each group so as to be swingable within a plane perpendicular to the axis of the center shaft 34. These cams are engaged with the slide bearing 33 by rotating the handle. A preload is applied between the pair of cams 32 of each group by a spring 36 in order to suppress backlash. A drive system (not shown) for automatic steering is connected to the center shaft 34.

  In the clutch mechanism, the center shaft 34 is always free to rotate, and the center shaft 34 is rotated by a drive system for automatic steering. When the handle is rotated, the cam 32 is engaged with the slide bearing 33, and the clutch is locked by the wedge effect. Therefore, the slide bearing 33, the center shaft 34, and the housing 35 rotate together. Since the cams 32 are provided in opposite directions as a pair, the cam 32 is locked when the handle is rotated in both the forward and reverse rotation directions.

  For this reason, when an interference force is generated due to a manual operation of the driver's handle in an emergency in which a danger such as a collision due to a slip is likely to occur during automatic steering, the clutch cam 32 is actuated to restrain the slide bearing 33. Thus, the clutch is locked, and manual steering is given priority regardless of the automatic steering movement.

FIG. 12 shows an example in which a conventional roller bearing (rolling bearing) 43 is used in place of the sliding bearing 33 in the clutch mechanism of FIG. The clutch operation is the same as in the example of FIG.
JP-A-10-226354 JP-A-10-258756 JP 2000-203436 A JP-A-6-307456 JP-A-7-238940

  The functions required of the slide bearing 33 and the roller bearing 43 used in the clutch mechanism described above are such that the rotational torque is small during idling and that there is no feeling deficiency such as a sense of stickiness or rattling, and the cam 32 is necessary in an emergency or the like. Therefore, the clutch is reliably locked and the locking function of the clutch is not impaired.

However, when the sliding bearing 33 is used in the clutch mechanism as shown in FIG. 11, the rotational torque during idling increases. Moreover, since durability is also inferior and wear occurs, there is a problem that locking does not occur.
When the roller bearing 43 is used as shown in FIG. 12, the rotational torque during idling is reduced. However, in the conventional roller bearing 43, since the roller pitch is large, the roller intermittently rides on the cam 32. For this reason, a feeling of rattling and rattling occurs during operation, and the steering feeling of the driver is worse than that of the slide bearing 33.

  In addition, as a roller bearing with a small roller pitch, there is a full roller bearing without a cage, but a general full roller bearing is a cage drop-off type. In the above clutch mechanism, the roller uses the cam surface of the cam 33 as the rolling surface, so that the cage drop-off type full roller bearing has a problem that the roller that does not get on the cam surface falls off.

Although it is conceivable to use a non-drop-off type full-roller bearing, the keystone type is difficult to design when the number of rollers is 20 or more.
Non-drop-off type full complement roller bearings with a C end face (for example, Patent Document 4) have a problem that the width dimension is large, the effective contact length is also short, and the roller end face and the contact portion with the roller end face are worn. There is. Specifically, the C end roller type is a type in which a pointed portion is provided on the roller end surface, and falling off is prevented by holding the pointed portion with a scissors provided on a press outer ring. Thus, since the roller end face is pointed, it is more expensive than end faces of flat and round faces (F and A faces). In addition, since the roller end face is pointed, the wear of the roller end face becomes noticeable in a usage form with a large induced thrust. Further, the effective length of the roller is shortened by the size of the pointed shape of the roller end face.
In addition to these, there is a full-roller bearing (for example, Patent Document 5) which is filled with a heat-solidifying grease to be a non-drop-off type, but this type has a large rotational torque. Furthermore, the service temperature of the bearing is limited within the service temperature range of the thermosetting grease. And the kind of grease, the kind of oil, etc. which are means for bearing lubrication are limited.

  The object of the present invention is to make it possible to increase the number of rollers to be incorporated, increase the load capacity and improve durability, and eliminate the feeling of stickiness and rattling, improving assembly and improving accuracy, while maintaining a non-drop-off type. It is an object of the present invention to provide a steering roller bearing capable of achieving the above. Another object of the present invention is that the clutch has a plurality of cams arranged at intervals in the circumferential direction, and the rollers roll on an intermittent circumferential surface formed on the outer circumference of the plurality of cams. Even when the vehicle is to run, it is possible to avoid the occurrence of a sense of harshness or rattling.

  A steering roller bearing according to the present invention is a steering roller bearing used in a clutch provided in a steering operation transmission system of a steering device, and is formed in a ring shape having a plurality of pockets arranged in the circumferential direction. It has two cages and a plurality of rollers that are held across the pockets of these two cages, and the inner cage holds the rollers from the inner diameter side between the rollers by the pillars between the pockets. The outer diameter of the column portion is smaller than the pitch circle diameter of the roller arrangement, and the outer cage holds the roller from the outer diameter side between the rollers, with the column portion between the pockets. The inner diameter of the part is larger than the pitch circle diameter of the roller arrangement, and the inner and outer cages are cut out from one side edge of each cage to the vicinity of the other side edge at a plurality of locations in the circumferential direction. It has a slit of shape The features.

According to this configuration, since the inner and outer two cages are provided, the roller can be a non-drop-off type roller bearing in a state where it is not assembled into the device, although it is a roller bearing with a cage that does not have a bearing ring. In this case, the inner and outer cage pillars hold the roller from the inner diameter side and the outer diameter side, the outer diameter of the inner cage pillar part is smaller than the pitch circle diameter of the roller arrangement, and the outer side Since the inner diameter of the retainer column portion is larger than the pitch circle diameter of the roller array, the retainer column portion may not exist on the pitch circle diameter of the roller array. For this reason, the roller arrangement interval is not widened by the column part, and it can be made to have the same number of rollers as the full roller type while using a cage to make the roller non-dropping type. A larger load capacity can be applied compared to the bearing. Therefore, it is possible to solve various problems of the full-roller type, such as assembling with less man-hours without using a drop-off prevention sleeve.
Therefore, when used in a steering device, particularly when used in a clutch provided in a steering operation transmission system of the steering device, the number of rollers incorporated can be increased, so that the load capacity can be increased and the durability can be improved. Moreover, it can eliminate the feeling of harshness and rattling.
In addition, since the inner and outer cages have slits in a shape cut out from one side edge of each cage to the vicinity of the other side edge at a plurality of locations in the circumferential direction, the outer cage is held during assembly. The cage can be inserted into and out of the roller array while expanding the insertion side portion of the slit of the cage and reducing the diameter of the insertion side portion of the inner cage. Thereafter, the rollers are naturally returned to the original diameter by the elasticity of the material of the cage, so that each roller enters the pocket and the bearing is assembled. In inserting the retainer, since the slit is provided, the retainer can be deformed within the elastic region of the material, and therefore, the retainer is less deformed by deformation and can prevent deterioration in accuracy due to deformation. As a result, the assembling property and accuracy can be improved, and the assembly can be automated.

In this invention, the clutch has a plurality of cams arranged at intervals in a circumferential direction, and the plurality of rollers have intermittent circumferential surfaces formed on an outer periphery of the arrangement of the plurality of cams. You may roll.
In the case of this configuration, the rollers move intermittently to the cam surface. However, the steering roller bearing of the present invention is a roller non-dropping type using a cage and can increase the number of rollers. Can smoothly move between the cam surfaces, and it is possible to avoid the occurrence of a sense of harshness or rattling.

  In this invention, it is preferable that the circumferential positions of the slits of the inner and outer cages are shifted from each other. Thereby, it is possible to sufficiently secure the holding strength of the rollers by the inner and outer cages while providing the slits.

In this invention, either one of the inner and outer cages has slits in a shape cut out from one side edge of each cage to the vicinity of the other side edge at a plurality of locations in the circumferential direction. Also good.
For example, when only the outer cage has a slit, when assembling the bearing, after the rollers are arranged on the outer circumference of the inner cage, the outer cage is held from the opening end side of the slit to the outside of the roller array. It can be inserted while expanding the diameter of the insertion side of the container. Thereafter, the cage is naturally restored to its original diameter by the elasticity of the material, so that each roller enters the pocket and the bearing can be easily assembled. When only the inner cage has a slit, after the rollers are arranged in the pocket of the outer cage, the inner cage is inserted in the axial direction from the opening end side of the slit to the inside of the roller array. At this time, the inner cage is inserted while reducing the diameter, and after insertion, the inner cage is restored to its original diameter by the elasticity of the material. Even when a slit is provided only in one of these cages, the cage can be deformed within the elastic region of the material because of the slit in the insertion of the cage, so that the cage is deformed flexibly. Therefore, it is possible to prevent a decrease in accuracy due to deformation. As a result, the assembling property and accuracy can be improved, and the assembly can be automated.

In this invention, the slit may also serve as a pocket for holding rollers. In other words, a removal portion may be provided at the pocket portion on the ring-shaped portion on the side edge of the cage, and the slit may be configured by the removal portion and the pocket.
By disposing the rollers also in the slit, the number of rollers can be increased while providing the slit, and the load capacity of the roller bearing can be increased.

  Further, the edge in the width direction on the inner diameter surface of the outer cage or the edge in the width direction on the outer diameter surface of the inner cage may be tapered or tapered in a tapered arc shape. By configuring in a tapered shape, the cage can be more smoothly inserted inside or outside the roller array at the time of assembly, and assemblability is further improved.

In this invention, either one or both of the inner and outer cages have slits in a shape cut out from one side edge of each cage to the vicinity of the other side edge at one place in the circumferential direction. There may be.
In the present invention, the inner cage and the outer cage may be integrated with each other. Thereby, assemblability improves.

A steering roller bearing according to the present invention is a steering roller bearing used in a clutch provided in a steering operation transmission system of a steering device, and is formed in a ring shape having a plurality of pockets arranged in the circumferential direction. It has two cages and a plurality of rollers that are held across the pockets of these two cages, and the inner cage holds the rollers from the inner diameter side between the rollers by the pillars between the pockets. The outer diameter of the column portion is smaller than the pitch circle diameter of the roller arrangement, and the outer cage holds the roller from the outer diameter side between the rollers, with the column portion between the pockets. The inner diameter of the part is larger than the pitch circle diameter of the roller arrangement, and the inner and outer cages are cut out from one side edge of each cage to the vicinity of the other side edge at a plurality of locations in the circumferential direction. It was supposed to have a slit of shape Although it is a bearing that does not have inner and outer races, it can be made into a non-drop-off type roller, and the number of incorporated rollers can be increased to increase the load capacity and durability, and to eliminate the feeling of stickiness and rattling. As a result, it is possible to improve assemblability and accuracy.
In particular, the clutch has a plurality of cams arranged at intervals in the circumferential direction, and the plurality of rollers roll on an intermittent circumferential surface formed on the outer periphery of the plurality of cams. In some cases, this roller bearing for steering is a roller non-dropping type using a cage, and the number of rollers can be increased, so that the rollers can smoothly move between the cam surfaces, causing a sense of stickiness and rattling. Can be avoided.

  A first embodiment of the present invention will be described with reference to FIGS. This steering roller bearing is used in a steering apparatus 20 for an automobile shown in FIG. The steering device 20 constitutes a part of an automatic steering system, and the automatic steering system has a function of switching from an automatic steering mode to a manual operation mode in which a driver generates a steering force. For this switching, the clutch mechanism 21 shown in FIG. 5B is provided in the steering operation transmission system 30 from the handle 27 to the center shaft 24 in the steering device 20.

  In the clutch mechanism 21, a plurality of cams 22 are arranged on the outer periphery of a center shaft 24 that serves as a shaft on the clutch output side, and the steering roller bearing 23 is interposed between the cam 22 and the inner diameter surface of the housing 25. Is. The cams 22 have a wedge shape, and each pair of the center shafts 24 facing each other in the opposite direction of the circumferential direction is a set, and one set or a plurality of sets are arranged in the circumferential direction. Each of these cams 22 is held for each group so as to be swingable within a plane perpendicular to the axis of the center shaft 24. These cams are engaged with the roller bearings 23 by rotating the handle. A preload is applied between the pair of cams 32 of each set by a spring 26 in order to suppress backlash at the time of free rotation in an unlocked state. The drive system 30 for automatic steering is connected to the center shaft 34. The handle shaft 28 and the center shaft 24 are rotatably supported by the support member 29 via other bearings (not shown).

  In the clutch mechanism 21, the center shaft 24 is normally free to rotate, and the center shaft 24 is rotated by a drive system 31 for automatic steering. When the handle 27 is rotated, the cam 22 is engaged with the roller bearing 23, and the clutch is locked by the wedge effect. Therefore, the roller bearing 23, the center shaft 24, and the housing 25 rotate together. Since the cams 22 are provided in pairs opposite to each other, locking occurs when the handle 27 is rotated in both the forward and reverse rotation directions.

  For this reason, when an interference force due to manual operation of the driver's handle 27 occurs in an emergency where a collision such as a slip is likely to occur during automatic steering, the clutch cam 22 is activated and the roller bearing 32 is restrained. By doing so, the clutch is locked, and manual steering is given priority regardless of the automatic steering movement.

  As shown in FIG. 2, the roller bearing 23 is a roller bearing having no inner and outer races, and is held across the inner and outer cages 3 and 13 and the pockets 4 of these two cages 3 and 13. The plurality of rollers 2 are provided. Both the inner and outer cages 3 and 13 are formed in a ring shape having a plurality of pockets 4 arranged in the circumferential direction. The inner cage 3 is configured such that the column portion 5 between the pockets 4 holds the roller 2 from the outer diameter side between the rollers 2. It is assumed that the outer cage 13 holds the rollers 2 from the inner diameter side between the rollers 2 by the column portions 5 between the pockets 4. These inner and outer cages 3 and 13 have ring-shaped portions 6 at both ends in the width direction, and a plurality of column portions 5 are provided at equal intervals in the circumferential direction between the ring-shaped portions 6 on both sides. A space between the pillars 5 becomes a pocket 4 in which the roller 2 is inserted.

  The inner and outer two cages 3 and 13 are made of a synthetic resin that can be elastically deformed, such as polyamide (for example, PA66, PA46) or polyacetal. The cages 3 and 13 use these synthetic resins in a non-reinforced state or in a state in which a reinforcing fiber such as carbon fiber or glass fiber is added in an amount of 30% or less. Appropriate strength and flexibility are given.

As shown in FIG. 2B, the inner diameter d3i of the cage 3 is set to be 0.1 mm or more larger than the maximum diameter d2i of the inscribed circle diameter of the roller arrangement. The 0.1 mm dimension is preferably equal to or greater than this value regardless of the bearing size. The outer diameter dimension d3o of the column portions 5 of the cage 3 is set to be smaller than the pitch circle diameter PCD of the roller arrangement. For example, it is smaller than the pitch circle diameter PCD by 0.1 mm or more. The dimension that is smaller than the pitch circle diameter PCD may be a predetermined ratio or more that is designed according to the bearing dimensions and the like. The thickness B of the column portion 5 of the cage 3 is preferably 15 to 30% of the roller diameter.
The outer diameter dimension d13o of the outer cage 13 is set to be 0.1 mm or more smaller than the minimum diameter d2o of the circumscribed circle diameter of the roller arrangement. The 0.1 mm dimension is preferably equal to or greater than this value regardless of the bearing size. The inner diameter dimension d13i of the columns 5 of the cage 13 is set larger than the pitch circle diameter PCD of the roller arrangement. For example, it is larger than the pitch circle diameter PCD by 0.1 mm or more. The dimension larger than the pitch circle diameter PCD may be a predetermined ratio or more designed according to the bearing dimension or the like.

  The cross-sectional shape of the column portion 5 of the inner cage 3 is, for example, that the innermost diameter portion 5c is a portion having a substantially constant width, and a portion 5d on the outer diameter side of the innermost diameter portion is tapered toward the outer diameter side. Shaped. The tip of the outer diameter side portion 5d has, for example, a shape in which a corner or the whole is rounded into an arc shape. The cross-sectional shape of the column portion 5 of the outer cage 13 is a quadrangular or pentagonal shape.

  Each example of the cages 3 and 13 is shown in FIGS. At a plurality of locations in the circumferential direction of the cages 3 and 13, slits 7 and 7 </ b> A having a shape cut out from one side edge of the cages 3 and 13 to the vicinity of the other side edge are provided.

FIG. 3A shows an example of the cages 3 and 13 in which the slit 7 is only cut out from one side edge (left side in the drawing).
In FIG. 3B, there are slits 7 cut out from one side edge and slits 7 cut out from the other side edge so that the slits 7 on both sides are arranged in a staggered pattern in the circumferential direction. An example of the cages 3 and 13 provided in FIG.
The cages 3 and 13 in the examples of FIGS. 3 (A) and 3 (B) both have a portion in which the entire portion between the adjacent column portions 5 in the ring-shaped portion 6 is removed and between the adjacent column portions 5. The slit 7 is composed of a portion that also serves as a pocket.

The slits 7 and 7A in FIG. 3C are examples of cutout shapes. The cutout shape may leave a part of the ring-shaped part like the slit 7A. In the case of the slit 7 that does not leave the ring-shaped portion, the corner portion may be R or tapered. Thereby, even if the width surface of the holder | retainer 3 and 13 contacts other members, such as a side plate, it can make it hard to catch.
FIG. 3 (D), like FIG. 3 (B), holds the slits 7 cut out from one side edge and the slits 7 cut out from the other side edge arranged in a staggered manner in the circumferential direction. In this case, the dedicated pocket 4 is omitted, and the slit 7 cut out from one side edge and the slit 7 cut out from the other side edge are in the circumferential direction. Are arranged alternately.

3A, 3B, and 3D, the retainers 3 and 13 each have a portion in which the substantially entire portion between the adjacent column portions 5 in the ring-shaped portion 6 is removed and the adjacent columns. A slit 7 is formed by a portion that also serves as a pocket between the portions 5.
3A and 3B, the pockets 4 and the slits 7 are alternately formed in each example, and the column portion 5 is interposed between the pocket 4 and the slit 7 that also serves as a pocket. It is supposed to be provided.
3A and 3B, the pockets 4 and the slits 7 are not alternating, and the slits 7 may be provided by arranging a plurality of pockets 4 in an array.
The cross-sectional shape of the column portion 5 is the shape described above for both the space between the pocket 4 and the slit 7 and the space between the adjacent dedicated pockets 4.
3A to 3C, the slits 7 and 7A may be provided only at one place in the circumferential direction.

  FIG. 4 shows a state in which the rollers 2 are held by the cages 3 and 13. FIG. 4 (A) shows the case where the cages 3 and 13 (example of FIG. 3 (A)) having the slit 7 only on one side are used. Here, the roller 2 is not only in the pocket 4 but also in the slit 7. Has been placed. Thereby, the load capacity of the roller bearing can be increased. FIG. 4B shows a case where the cage 3 having the slits 7 on both sides (example of FIG. 3B) is used. In this case, the rollers 2 are arranged not only in the pocket 4 but also in the slit 7. ing. FIG. 4C shows a case where the cages 3 and 13 having only the slit 7 (example of FIG. 3D) are used. In this case, the rollers 2 are arranged in all the slits 7.

According to the roller bearing 23 having this configuration, since the roller 2 is held by the inner and outer cages 3 and 13, the roller 2 is not assembled in the apparatus while being a roller bearing with a cage that does not have a bearing ring. It can be a non-drop-off type roller bearing that does not drop off. The inner and outer cages 3 and 13 are those in which the column portion 5 holds the roller 2 from the inner diameter side and the outer diameter side, and the outer diameter d3o of the column portion 5 of the inner cage 3 is set to the pitch circle diameter of the roller arrangement. Since the diameter is smaller than that of the PCD and the inner diameter d13i of the column portion 5 of the outer cage 13 is larger than the pitch circle diameter PCD of the roller arrangement, each column portion 5 of the cage 3 and 13 has a pitch circle diameter of the roller arrangement. It may not be present on the PCD. Therefore, the arrangement interval of the rollers 2 is not widened by the column portion 5, and the rollers 3 and 13 can be used to make the roller non-dropping type, while having the same number of rollers as the full roller type, and having the same cross-sectional height. Compared with a conventional roller bearing with an outer ring, a larger load capacity can be provided. Therefore, it is possible to solve various problems of the full-roller type, such as assembling with less man-hours without using a drop-off prevention sleeve. Further, the strength of the column portion 5 is ensured.
When the roller bearing 23 having this configuration is used for the clutch mechanism 21 of the steering device 20, the roller 2 is transferred to the cam surface intermittently arranged on the cam surface 22 (FIG. 1B). Since it is small and does not drop off, it can be transferred smoothly, and a feeling of harshness and rattling can be reduced, thereby improving the steering feeling. Further, the vibration is reduced by improving the steering feeling.

In the case of the roller bearing of this embodiment, the following advantages are further obtained. For example, since the outer diameter dimension d13o of the outer cage 13 is made 0.1 mm or more smaller than the minimum diameter of the circumscribed circle diameter d2o of the roller arrangement, there is a gap of 0.1 mm or more between the bearing box and the cage 13. Arise. Therefore, the cage 13 does not come into strong contact with the bearing box, and an increase in friction torque due to the cage 13 is avoided.
Further, since the inner diameter d3i of the inner cage 3 is set to be 0.1 mm or more larger than the maximum diameter of the inscribed circle diameter d2i of the roller arrangement, a gap of 0.1 mm or more is generated between the shaft and the cage 3. . Therefore, the cage 3 does not come into strong contact with the shaft, and it is avoided that the friction torque is increased by the cage 3.

Further, the outer diameter dimension d3o of the arrangement of the column portions 5 of the inner cage 3 is made smaller than the pitch circle diameter PCD of the roller arrangement, and the degree of the reduction is, for example, 0.1 mm or more than the pitch circle diameter PCD. Therefore, it is not necessary to widen the interval between the roller arrangements, and it is avoided that the width of the outermost diameter portion in the cross section of the column portion 5 becomes too thin and the strength becomes insufficient.
Further, the inner diameter dimension d13i of the column portions 5 of the outer cage 13 is made larger than the pitch circle diameter PCD of the roller arrangement, and the degree of the increase is, for example, 0.1 mm or more than the pitch circle diameter PCD. Therefore, it is not necessary to increase the interval between the roller arrangements, and it is avoided that the innermost diameter portion in the cross section of the column portion 5 becomes too thin and the strength is insufficient.

  Further, the cross-sectional shape of the column portion 5 of the inner cage 3 is such that the innermost diameter portion 5c is a portion having a substantially constant width, and a portion 5d on the outer diameter side of the innermost diameter portion 5c is tapered toward the outer diameter side. Therefore, the cross-sectional area of the column portion 5 can be increased without increasing the interval between the rollers 2, and the lubricity is excellent. That is, since the gap between the adjacent rollers 2 in the roller arrangement becomes a triangular gap whose inner diameter side gradually increases, in order to increase the cross-sectional area of the column portion 5 without increasing the interval between the rollers 2, It is preferable that the portion 5 has a triangular cross-sectional shape that is tapered toward the outer diameter side. However, the innermost diameter portion 5c in which the width of the column portion 5 is widest is not widened along the roller surface, and the gap between the roller surface and the column portion surface is widened to avoid obstruction of the flow of the lubricating oil. It is possible to prevent a decrease in lubricity. In addition, no waste portion is generated in the column portion 5, and the resin material is saved.

  In addition, since the slits 7 and 7A having a shape notched from one side edge of the cages 3 and 13 to the vicinity of the other side edges are provided at a plurality of locations in the circumferential direction of the cages 3 and 13, The insertion side portions of the containers 3 and 13 can be inserted while being expanded or contracted. The same applies when the slits 7 and 7A are provided at one place in the circumferential direction. Therefore, the cages 3 and 13 can be deformed within the elastic region of the material, the cages 3 and 13 are less bent and deformed, accuracy deterioration due to the deformation can be prevented, and assemblability and accuracy are improved. be able to.

FIG. 5 shows another embodiment of the present invention. In the roller bearing 23 in the embodiment shown in FIG. 2, the left and right edges 3a of the outer diameter surface of the inner cage 3 and the left and right edges 13a of the inner diameter surface of the outer cage 13 are tapered. Narrow shape. Other configurations are the same as those of the embodiment of FIG.
As described above, the inner edge 3a of the inner retainer 3 and the inner edge 13a of the inner retainer 13 are tapered so that the inner side of the roller arrangement during assembly is increased. The cage 3 can be smoothly inserted and the cage 13 can be smoothly inserted to the outside, and the assemblability is further improved. In addition, since both edge portions 3a and 13a of the cages 3 and 13 are tapered and tapered, even if the cages 3 and 13 are inserted from either side edge into and out of the roller arrangement, the insertion is smooth. Can be done.
The left and right edge portions 3a and 13a may have only one of the inner and outer cages 3 and 13 to have a tapered tapered shape.

FIG. 6 shows still another embodiment of the present invention. In the embodiment of FIG. 2, the roller bearing 23 is configured so that the inner cage 3 has a shape in which the ring-shaped portions 6 on both sides are thicker toward the outer diameter side than the column portion 5, and the outer cage 13 is The ring-shaped parts 6 on both sides are formed to be thicker toward the inner diameter side than the column part 5. Other configurations are the same as those of the embodiment of FIG. Also in this configuration, each operation and effect shown in the embodiment of FIG. 2 can be obtained.
The ring-shaped portions 6 on both sides may be thicker than the column portion 5, and only one of the inner and outer cages 3 and 13 may be used.

  In the embodiment of FIG. 2, the case where the slits 7 are provided in both the inner and outer cages 3 and 13 has been shown, but even if the slit 7 is provided only in the inner cage 3 as shown in FIG. As shown in FIG. 8, a slit 7 may be provided only in the outer cage 13. In these cases as well, the cages 3 and 13 can be easily inserted into and out of the roller array by reducing or expanding the diameter of the cage with the slit 7 as the insertion side. That is, for example, in the case of the embodiment in which the slit 7 is provided only in the inner cage 3 as shown in FIG. 7, after the rollers 2 are arranged in the pockets 4 of the outer cage 13, the inner cage 3 is moved. The diameter of the slit 7 formation side is reduced as the insertion side, and the slit 7 is inserted into the roller array in the axial direction. After the insertion, the original diameter is naturally restored by the elasticity of the material of the cage 3. In the case of the embodiment in which the slit 7 is provided only in the outer cage 13 as shown in FIG. 8, after the rollers 2 are arranged in the pocket 4 of the inner cage 3, the outer cage 13 is inserted into the slit. 7 Increase the diameter of the forming side as the insertion side and insert it axially outside the roller array. After the insertion, the original diameter is naturally restored by the elasticity of the material of the cage 13.

  FIG. 9 shows still another embodiment of the present invention. In the embodiment shown in FIG. 2, this roller bearing is formed by connecting inner and outer cages 3 and 13 at one side thereof and integrating them with each other. Here, the connecting portions 10 of the inner and outer cages 3 and 13 are provided at intervals of three rollers 2 arranged in the circumferential direction, and the connecting portion 10 and the ring-shaped portions 6 of the inner and outer cages 3 and 13 are provided. The enclosed window is an oval shape. In addition, the side edge parts 3a and 13a on the opposite side to the connection part 10 of the inner and outer cages 3 and 13 have a tapered tapered shape. That is, both the side edge 3a on the opposite side to the connecting portion 10 on the outer diameter surface of the inner cage 3 and the side edge 13a on the opposite side to the connecting portion 10 on the inner diameter surface of the outer cage 13 are tapered. It has a tapered shape.

  In this way, by connecting the inner and outer cages 3 and 13 at one side of them and integrating them with each other, it is easy to insert the inner and outer cages 3 and 13 into and out of the roller array during assembly. This can be done and the assembly is improved. Further, since the side edges 3a and 13a opposite to the connecting portion 10 of the inner and outer cages 3 and 13 are tapered and tapered, the both cages 3 and 13 are arranged in a roller arrangement from the opposite side to the connecting portion 10. The insertion can be performed smoothly when inserted to the outside.

  FIGS. 10A and 10B show still another embodiment of the present invention. In the embodiment of FIG. 9, the roller bearing 23 in FIG. 10 (A) is provided with a connecting portion 10 for each interval in which one roller 2 is arranged in the circumferential direction, and the connecting portion 10 and the inner and outer cages 3 are provided. , 13 is a rectangular window. Further, the roller bearing of FIG. 10 (B) is provided with a connecting portion 10 at intervals of two rollers 2 arranged in the circumferential direction in the embodiment of FIG. 9, and the connecting portion 10 is an inner cage. It is formed in a fan shape that tapers from the ring-shaped part 6 toward the outer cage ring-shaped part 6. Moreover, it is good also as a fan shape used as an expansion.

(A) is a partial side view of a steering apparatus provided with the steering roller bearing concerning 1st Embodiment in this invention, (B) is the elements on larger scale of the clutch mechanism in the same steering apparatus. (A) is the partial longitudinal cross-sectional view of the roller bearing, (B) is the partial cross-sectional view. It is a partial front view which shows each example of a holder | retainer. It is a partial front view which shows each example of the roller arrangement | sequence state to the holder | retainer. It is a fragmentary sectional view of the roller bearing of further another embodiment in this invention. It is a fragmentary sectional view of the roller bearing of further another embodiment in this invention. It is a fragmentary sectional view of the roller bearing of further another embodiment in this invention. It is a fragmentary sectional view of the roller bearing of further another embodiment in this invention. (A) is the fragmentary longitudinal cross-sectional view of the roller bearing of further another embodiment in this invention, (B) is the partial side view. (A) is the partial side view of the roller bearing of further another embodiment in this invention, (B) is the partial side view of the roller bearing of further another embodiment in this invention. It is a fragmentary sectional view of the prior art example of the clutch mechanism in steering. It is a fragmentary sectional view of the other conventional example of the clutch mechanism in steering.

Explanation of symbols

DESCRIPTION OF SYMBOLS 2 ... Roller 3, 13 ... Cage 4 ... Pocket 5 ... Column part 7, 7A ... Slit 10 ... Connecting part 20 ... Steering device 21 ... Clutch mechanism 22 ... Cam 23 ... Steering roller bearing 30 ... Steering motion transmission system

Claims (7)

  Steering roller bearings used in a clutch provided in a steering operation transmission system of a steering apparatus, each having two inner and outer cages formed in a ring shape having a plurality of pockets arranged in the circumferential direction, and the two A plurality of rollers that are held across the pockets of the cage, and the inner cage holds the rollers from the inner diameter side between the rollers, and the outer diameter of the pillars is between the rollers. The outer cage has a smaller diameter than the pitch circle diameter of the roller arrangement, and the column portion between the pockets holds the rollers from the outer diameter side between the rollers, and the inner diameter of the column portion is a pitch circle of the roller arrangement. It has a diameter larger than the diameter, and the inner and outer cages have slits in a shape cut out from one side edge of each cage to the vicinity of the other side edge at a plurality of locations in the circumferential direction. Steering roller bearing characterized by   2. The intermittent circumferential surface according to claim 1, wherein the clutch has a plurality of cams arranged at intervals in a circumferential direction, and the plurality of rollers are formed on an outer periphery of the arrangement of the plurality of cams. Roller bearings for steering that are rolling.   3. The steering roller bearing according to claim 1, wherein the circumferential positions of the slits of the inner and outer cages are shifted from each other.   In any one of Claims 1 thru | or 3, instead of the structure which both the inside and outside retainer makes the shape which has the said slit, either one of the inside and outside retainer is in the several places of the circumferential direction, A steering roller bearing having a slit cut out from one side edge of each cage to the vicinity of the other side edge.   The roller bearing for steering according to any one of claims 1 to 4, wherein the slit also serves as a pocket for holding the roller.   6. The method according to claim 1, wherein one or both of the inner and outer cages are cut at one place in the circumferential direction from one side edge of each cage to the vicinity of the other side edge. A steering roller bearing having a notched slit. 7. The steering roller bearing according to claim 1, wherein the inner cage and the outer cage are integrated with each other.

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