JP2004108486A - Roller bearing - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To prevent seizure of rollers and reduce torque of inside of a bearing in using a shell type needle roller bearing or a cylindrical roller bearing with oil lubrication. <P>SOLUTION: In this roller bearing, a plurality of needle rollers 20 are arranged on an inner circumference of the shell 10 in a circumference direction, an end surface of the needle roller 20 is a flat surface 22 and has an attachment part formed on an outer circumference, the shell 10 is composed of a cylindrical part 13 having a raceway surface 14 of the needle rollers 20 on an inner circumference surface thereof and a pair of flange parts 11, 12 sagging in an inner diameter direction at an axial direction both ends of the cylindrical part 13, and an inner surface of the flange parts 11, 12 become flat guide surface 11a, 12a directly opposing the flat surface 22 of the end surface of the needle roller 20. A flange diameter of at least one of flange parts 11, 12 of the shell 10 is larger than PCD of the needle rollers 20. <P>COPYRIGHT: (C)2004,JPO

Description

[0001]
TECHNICAL FIELD OF THE INVENTION
The present invention relates to a roller bearing such as a needle needle roller bearing or a cylindrical roller bearing.
[0002]
[Prior art]
2. Description of the Related Art Conventionally, among shell-type needle roller bearings with a retainer, there is one in which a flange diameter of one flange portion of a shell is increased (for example, see Patent Document 1). With this configuration, when used under conditions of oil lubrication, lubricating oil can be prevented from entering the inside of the bearing from the flange portion having the large flange diameter and seizing the needle rollers onto the raceway surface.
[0003]
There are shell type needle roller bearings as well as types with cages and full roller types. FIG. 8 shows an example of a conventional full-roller type needle roller bearing.
[0004]
In FIG. 8, reference numeral 10 denotes a shell serving as an outer ring, and reference numeral 20 denotes a plurality of needle rollers arranged side by side along the inner periphery of the shell 10. The shell 10 is formed by hanging flanges 11 and 12 in the inner diameter direction at both axial ends of the cylindrical portion 13 in order to prevent the needle rollers 20 from coming apart. The inner circumference of the cylindrical portion 13 becomes a raceway surface 14, and the needle rollers 20 roll along the raceway surface 14.
[0005]
The end surface 21 of the needle roller 20 is a flat surface 22, and a chamfered portion 23 is formed on the outer periphery. The inner surfaces of the flanges 11 and 12 are guide surfaces 11 a and 12 a directly facing the flat surface 22 of the end surface 21 of the needle roller 20.
[0006]
This type of needle-type needle roller bearing is mainly used with grease sealed therein. In order to prevent grease from leaking and to prevent foreign matter from entering from outside, the flanges 11 and 12 of the shell 10 have a radial direction. The length was set large enough.
[0007]
That is, the inner diameter (hereinafter, referred to as a flange diameter) E at the inner diameter ends 15, 16 of the flange portions 11, 12 and the PCD of the needle rollers 20 (the diameter of a circle C connecting the centers of the needle rollers 20). The relationship is
PCD> E
Was satisfied, and the flange diameter E was set small.
[0008]
[Patent Document 1]
JP 2001-65575 A
[Problems to be solved by the invention]
When the shell-type needle roller bearing shown in FIG. 8 is used under the condition of oil lubrication in which lubricating oil is supplied from the outside, the flange portions 11 and 12 having a large radial length hinder the lubricating oil. Difficult to penetrate inside.
[0010]
As a result, the amount of lubricating oil inside the bearing becomes insufficient, causing poor lubrication. In the case of a full-roller type needle needle roller bearing, the guide surfaces 11a and 12a of the flanges 11 and 12 directly face the flat surface 22 of the end surface 21 of the needle roller 20 and receive an axial load. If a failure occurs, the needle rollers 20 may seize on the raceway surface 14, and the frictional resistance between the end surface 21 of the needle rollers 20 and the guide surfaces 11a and 12a of the flanges 11 and 12 may increase. And the torque inside the bearing increases.
[0011]
[Means for Solving the Problems]
The roller bearing of the present invention has a plurality of rollers arranged in the circumferential direction on the inner peripheral surface of the outer ring, the end surfaces of the rollers are flat surfaces, and a chamfer is formed on the outer periphery, and the outer ring has A cylindrical portion having a raceway surface of the roller on an inner peripheral surface thereof, and a pair of flange portions respectively suspended in an inner diameter direction at both axial ends of the cylindrical portion, and the inner surface of the flange portion has a flat end face of the roller. It is a flat guide surface directly facing the surface, and the flange diameter of at least one flange of the outer ring is larger than the PCD of the roller.
[0012]
Roller bearings need only be those in which the inner surface of the flange portion is a flat guide surface that directly opposes the flat surface of the end surface of the roller.Including shell-type needle roller bearings and cylindrical roller bearings, full-roller type Alternatively, any of the type with a retainer may be used.
[0013]
The flange part whose flange diameter is larger than the roller PCD may be one or both of a pair of flange parts at both axial ends of the outer ring.
[0014]
The shape of the inner diameter end of the flange portion whose flange diameter is larger than that of the roller PCD is not particularly limited, such as a perfect circle, one having irregularities formed in the circumferential direction, and an ellipse. It just needs to be bigger.
[0015]
According to the roller bearing of the present invention, since the flange diameter of at least one flange of the outer ring is made larger than the PCD of the rollers, the gap area between adjacent rollers exposed from the flange is increased. Therefore, when used in oil lubrication, the lubricating oil flows from the gap between the large rollers exposed from the flange, the amount of lubricating oil supplied to the inside of the bearing increases, and seizure of the rollers can be prevented, The torque inside the bearing can be reduced.
[0016]
BEST MODE FOR CARRYING OUT THE INVENTION
An embodiment of the present invention will be described with reference to FIGS.
[0017]
1 is a sectional view of a full-roller type needle needle roller bearing, FIG. 2 is a side view of an outer ring of the roller bearing, FIG. 3 is a partial side view of the roller bearing, and FIG. 4 is a side view of a rocker arm using the roller bearing. FIG. 5 shows a plan view of the rocker arm.
[0018]
In FIG. 1, reference numeral 10 denotes a shell serving as an outer ring, and reference numeral 20 denotes a plurality of needle rollers arranged side by side along the inner periphery of the shell 10. The shell 10 is formed by hanging flanges 11 and 12 in the inner diameter direction at both axial ends of the cylindrical portion 13 in order to prevent the needle rollers 20 from coming apart. The inner circumference of the cylindrical portion 13 becomes a raceway surface 14, and the needle rollers 20 roll along the raceway surface 14.
[0019]
The end surface 21 of the needle roller 20 is a flat surface 22, and an R-shaped chamfered portion 23 is formed on the outer periphery. Further, the inner surfaces of the flange portions 11 and 12 are guide surfaces 11a and 12a directly facing the flat surface 22 of the end surface 21 of the needle roller 20, and the axial load of the needle roller 20 at the guide surfaces 11a and 12a. Is receiving.
[0020]
The shell 10 is formed by bending a thin steel plate. That is, the flange 11 is bent and formed on one side of a thin steel plate by a press, the inner periphery on the other side is thinned by trimming, the needle rollers 20 are assembled, and the flange 12 is bent by a press.
[0021]
The inner diameter end 15 of the flange portion 11 has a petal shape in which convex portions 17 and concave portions 18 are alternately formed in the circumferential direction.
[0022]
Assuming that the flange diameter between the opposing convex portions 17 is A, the flange diameter between the opposing concave portions 18 is B, and the PCD of the needle roller 20 is:
PCD <A <B
Meet the relationship.
[0023]
In addition, since the guide surfaces 11a and 12a of the flange portions 11 and 12 directly oppose the flat surface 22 of the end surface 21 of the needle roller 20, the outer diameter of the flat surface 22 of the end surface 21 of each needle roller 20 is adjusted. If the diameter of the circle connecting the ends is F,
A <B <F
Meet the relationship.
[0024]
The inner diameter end 16 of the flange portion 12 is also formed in a petal shape with irregularities in the circumferential direction, similarly to the inner diameter end 15 of the flange portion 11.
[0025]
FIGS. 4 and 5 show an example of a rocker arm 30 as an application example in which the shell needle roller bearing of the present invention is used for oil lubrication. That is, the shell-shaped needle roller bearing functions as a roller of the rocker arm 30.
[0026]
The rocker arm 30 is an end pivot type, and has a main body 31, a support shaft 32, and a shell-shaped needle roller bearing rotatably supported by the support shaft 32.
[0027]
The main body 31 includes a pair of opposing side wall portions 33, 33 arranged substantially parallel to each other, a pivot portion 34 provided between lower sides at one longitudinal end of the opposing side wall portions 33, 33, and a pair of opposing side wall portions 33. , 33 and a valve stem guide portion 35 provided between the other ends in the longitudinal direction.
[0028]
A through hole 36 penetrating coaxially perpendicular to the wall surfaces of the opposed side wall portions 33, 33 is provided at a longitudinally intermediate position between the opposed side wall portions 33, 33. By inserting and caulking the both ends, the support shaft 32 is attached in a state of being bridged between the opposed side wall portions 33, 33.
[0029]
The shell 10 is rotatably attached to the outer periphery of the support shaft 32 via the plurality of needle rollers 20 between the opposed side wall portions 33, 33, and the cam 39 abuts on the outer peripheral surface of the shell 10.
[0030]
In such a rocker arm 30, the pivot portion 34 of the main body 31 is engaged with the upper end of a lash adjuster 37 installed on a cylinder head (not shown), and the valve stem guide portion 35 is connected to a valve operating mechanism installed on the cylinder head. It abuts on the stem end 38 of the valve. By rotating the cam 39, the pivot portion 34 becomes a fulcrum and the main body 2 is tilted, and the valve stem guide portion 35 is repeatedly displaced up and down by a predetermined stroke, thereby opening and closing the valve. Let it. As described above, the rocker arm 30 is configured to be swung about the one end in the longitudinal direction of the main body 2 to operate the valve.
[0031]
In the case of a shell type needle roller bearing used as a roller of the rocker arm 30, as shown in FIG. 1, the roller diameter of both the flange portions 11 and 12 of the shell 10 is larger than the PCD of the needle roller 20. , Sufficient lubricating oil is supplied into the bearing.
[0032]
According to the roller bearing configured as described above, the minimum flange diameter A of the flange portions 11 and 12 of the shell 10 is made larger than the PCD of the needle roller 20, so that the inner diameter ends 15 and 16 of the flange portions 11 and 12 are circumferential. It becomes larger than the PCD of the needle roller 20 over the entire length in the direction. Therefore, on the outer diameter side from the circle C connecting the centers of the needle rollers 20, a gap S (see FIG. 3) between the adjacent needle rollers 20 is newly exposed, and the adjacent needle rollers 20 exposed from the flange portions 11 and 12 are newly exposed. The area of the gap S between the matching needle rollers 20 increases. As a result, when used in oil lubrication, lubricating oil flows from the gap S between the large needle rollers 20 exposed from the flanges 11 and 12, and the amount of lubricating oil supplied to the inside of the bearing increases. Therefore, the needle rollers 20 can be prevented from seizing on the raceway surface 14, and the frictional resistance between the end surface 21 of the needle rollers 20 and the guide surfaces 11 a, 12 a of the flange portions 11, 12 can be reduced, and seizure can be prevented, and a high axial force can be prevented. The load capacity is guaranteed, and the torque inside the bearing can be reduced.
[0033]
Further, since the convex portions 17 having a small flange diameter are formed at the inner diameter ends 15 and 16 of the flange portions 11 and 12, the amount of lubricating oil flowing into the concave portion 18 having a large flange diameter is increased, and the convex portion having a small flange diameter is formed. The portion 17 can prevent the needle rollers 20 from coming apart and receive an axial load.
[0034]
The flange diameters of the flange portions 11 and 12 may be at least those in which the maximum flange diameter B is larger than the PCD of the needle roller 20. As described above, even if a part of the inner diameter ends 15 and 16 of the flange portions 11 and 12 in the circumferential direction is larger than the PCD of the needle rollers 20, the gap between the needle rollers 20 adjacent to the enlarged portion is increased. The gap S is exposed, and the amount of lubricating oil supplied inside the bearing increases.
[0035]
Further, in one of the flanges 11 (or the flange 12), the maximum flange diameter may be larger than the PCD of the needle roller 20. That is, lubricating oil flows into the bearing from the flange portion 11 (or flange portion 12) having a flange diameter larger than the PCD of the needle roller 20, and the flange portion 12 (or flange) having a flange diameter smaller than the PCD of the needle roller 20. It is possible to prevent the lubricating oil that has flowed in at the part 11) from flowing out, and the present invention can be applied to a device used in a place where such a lubricating oil flows. In this case, the thickness of the flange 11 is thicker than the thickness of the flange 12, and when the flange diameter of the flange 11 is larger than the PCD of the needle roller 20, the strength of the shell 10 is less likely to be reduced. preferable.
[0036]
Another embodiment of the present invention will be described with reference to FIGS.
[0037]
This embodiment is characterized in that the inner diameter ends 15, 16 of the flange portions 11, 12 are formed as perfect circles having a flange diameter D larger than the PCD of the needle roller 20.
[0038]
Even with such a configuration, the area of the gap S between the adjacent needle rollers 20 exposed from the flange portions 11 and 12 increases, and when used in oil lubrication, the lubricating oil supplied to the inside of the bearing is reduced. The amount increases.
[0039]
The shape of the inner diameter ends 15 and 16 of the flanges 11 and 12 of the outer ring 10 may be any shape as long as the maximum flange diameter is larger than the PCD of the needle roller 20. The shape is not limited. In addition, the inner ends 15, 16 of the flanges 11, 12 may have different shapes.
[0040]
The rocker arm 30 described as an application example in which the shell-type needle roller bearing of the present invention is used for oil lubrication is an example, and may be used for other oil lubrication parts.
[0041]
Further, as the roller bearing to which the configuration of the present invention is applied, any bearing may be used as long as the inner surface of the flange portion is a flat guide surface directly opposed to the flat surface of the end surface of the roller. May be a cylindrical roller bearing composed of a plurality of rollers rolling along the raceway surface of the inner peripheral surface of an outer ring such as a forged product, and a type with a retainer, which is held by the retainer. A roller bearing in which a flat guide surface of a flange directly faces the end surface of the roller may be used.
[0042]
【The invention's effect】
According to the roller bearing of the present invention, when used in oil lubrication, the lubricating oil flows from the large gap between the rollers exposed from the flange, the amount of lubricating oil supplied to the inside of the bearing increases, and the roller burns. It is possible to obtain the effect that the attachment can be prevented and the torque inside the bearing can be reduced.
[Brief description of the drawings]
FIG. 1 is a cross-sectional view of a shell-type needle roller bearing according to an embodiment of the present invention.
FIG. 2 is a side view of an outer ring of the roller bearing of FIG.
FIG. 3 is a partial side view of the roller bearing of FIG. 1;
FIG. 4 is a side view of a rocker arm using the roller bearing of FIG. 1;
FIG. 5 is a plan view of the rocker arm of FIG. 4;
FIG. 6 is a cross-sectional view of a shell needle roller bearing according to another embodiment of the present invention.
FIG. 7 is a partial side view of the roller bearing of FIG. 6;
FIG. 8 is a cross-sectional view of a conventional needle needle roller bearing.
[Explanation of symbols]
10 shell (outer ring)
11, 12 Flanges 11a, 12a Guide surface 13 Cylindrical portion 14 Track surface 20 Needle roller (roller)
21 end face 22 flat face 23 chamfer

Claims (2)

A plurality of rollers are arranged in the circumferential direction on the inner peripheral surface of the outer ring, the end surfaces of the rollers are flat surfaces, and a chamfer is formed on the outer periphery, and the outer ring has the inner peripheral surface of the rollers. A cylindrical portion having a raceway surface, and a pair of flange portions each hanging in the radial direction at both axial ends of the cylindrical portion, the inner surface of the flange portion is a flat surface directly facing the flat surface of the end face of the roller. For roller bearings that serve as guide surfaces,
A roller bearing, wherein a flange diameter of at least one flange of the outer ring is larger than a PCD of the roller. A plurality of rollers are arranged in the circumferential direction on the inner peripheral surface of the outer ring, the end surfaces of the rollers are flat surfaces, and a chamfer is formed on the outer periphery, and the outer ring has the inner peripheral surface of the rollers. A cylindrical portion having a raceway surface, and a pair of flange portions each hanging in the radial direction at both axial ends of the cylindrical portion, the inner surface of the flange portion is a flat surface directly facing the flat surface of the end face of the roller. For roller bearings that serve as guide surfaces,
An inner diameter end of at least one flange portion of the outer ring has a shape in which a flange diameter changes in a circumferential direction of the one flange portion, and at least a maximum flange diameter is larger than a PCD of the roller. Roller bearing.

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