JP2013064461A - Roller bearing - Google Patents

Abstract

PROBLEM TO BE SOLVED: To provide a roller bearing supplying oil to both ends in the axial direction, suppressing local stress concentration of an outer ring, and suppressing chipping of the outer ring in polishing the outer ring outer peripheral surface.SOLUTION: In the roller bearing 40 including the outer ring 42 formed to a cylindrical shape and having an outer ring raceway surface 42a on the inner peripheral surface, an inner ring 48 formed to a cylindrical shape and having an inner ring raceway surface 48a on the outer peripheral surface, a plurality of rollers 44 arranged so as to roll between the outer ring and the inner ring 48, and a retainer 46 including pockets accommodating the rollers 44, a plurality of oil grooves 43 inclining relative to the axial direction and making both ends in the axial direction communicate with each other are arranged adjacently on the outer ring outer peripheral surface 42b, and oil supplied from an oil pressure supply source by the oil grooves 43 is led to both ends in the axial direction of the roller bearing 40.

Description

  The present invention relates to a roller bearing.

2. Description of the Related Art Conventionally, as an example of a bearing configuration for supporting a rotating shaft member, for example, as shown in Patent Document 1, a balancer shaft device that supports rotation of a crankshaft of an engine is supported by a shaft through a slide bearing. Are known. In this sliding bearing, a cylindrical member made of a metal member is disposed around a balancer shaft and is axially supported by sliding contact.
On the balancer shaft, hook-shaped portions are erected so as to sandwich both axial ends of the slide bearing. This hook-shaped part is configured to restrict relative movement of the balancer shaft and the sliding bearing in the axial direction.
On the other hand, in a sliding bearing, an annular groove cut in the circumferential direction (the annular groove may be provided on the housing side), and a through-hole penetrating the outer circumferential surface and the inner circumferential surface at a plurality of circumferential positions on the annular groove Is formed. The lubricating oil supplied from the housing through the annular groove and the through-hole lubricates the sliding contact surfaces of the balancer shaft and the sliding bearing, and the lubricating oil that has flowed out to both ends in the axial direction is centrifuged along with the rotation of the balancer shaft. The force flows into the contact part of the flanged part of the housing and the balancer shaft, and the part is lubricated.

By the way, since this slide bearing supports the balancer shaft by sliding contact, there is a concern about engine torque. For this reason, as shown in FIGS. 6 and 7, a roller bearing 140 may be provided instead of the sliding bearing. The roller bearing 140 includes a cylindrical outer ring 142 having an outer ring raceway surface on an inner peripheral surface, an inner ring 148 formed in a cylindrical shape having an inner ring raceway surface, and the outer ring 142 and the inner ring 148 between the outer ring 142 and the inner ring 148. A plurality of rollers 144 arranged so as to be able to roll, and a cage 146 having a pocket for accommodating the rollers 144 are provided.
By adopting this roller bearing 140, it is possible to expect a reduction in frictional resistance when the balancer shaft 130 rotates. However, if the outer ring 142 configured in the roller bearing 140 is simply cylindrical, a new problem arises in that the cylindrical outer ring 142 blocks the hydraulic pressure supply hole 107 of the housing 104. Here, the lubrication in the roller bearing 140 is maintained by the mist-like oil in the engine, but the lubricating oil is cut off at the contact portion between the housing 104 and the flanged portion 138 of the balancer shaft 130. There is a risk of seizing.
Therefore, as shown in FIGS. 6 and 7, the outer ring 142 of the roller bearing 140 is formed with an axial groove 147 that communicates with the annular groove 145 in the axial direction, whereby lubricating oil is supplied to both ends in the axial direction. It is conceivable to lubricate the contact portion of the flanged portion 138 of the balancer shaft 130.

JP 2003-129814 A

However, there is a space-like restriction at the site where the roller bearing is disposed instead of the slide bearing. Therefore, it is necessary to form the inner ring 148 and the outer ring 142 in a thin cylinder.
When the axial groove 147 is formed on the outer peripheral surface of the outer wall of the thin cylinder, the portion is further thinned. Then, a load generated by the rotational force of the balancer shaft 130 is exerted on the outer ring 142 via the rollers 144, and stress may concentrate on the portion of the axial groove, and the outer ring itself may be cracked. Further, when polishing the outer peripheral surface of the outer ring, there is a possibility that the corner portion at the step portion of the axial groove is missing.

  Thus, the present invention was devised in view of such points, and the problem to be solved by the present invention is that oil can be supplied to both ends in the axial direction, and the outer ring An object of the present invention is to provide a roller bearing capable of suppressing local stress concentration and suppressing the outer ring chipping during polishing of the outer peripheral surface of the outer ring.

In order to solve the above problems, the roller bearing of the present invention takes the following means.
First, a roller bearing according to a first aspect of the present invention includes an outer ring formed in a cylindrical shape and having an outer ring raceway surface on an inner peripheral surface, an inner ring formed in a cylindrical shape and having an inner ring raceway surface on the outer peripheral surface, the outer ring and the inner ring, A roller bearing comprising a plurality of rollers arranged to be able to roll between and a cage having a pocket for accommodating the rollers, wherein the outer peripheral surface of the outer ring is inclined with respect to the axial direction. In addition, a plurality of oil grooves communicating at both ends in the axial direction are provided adjacent to each other, and oil supplied from a hydraulic pressure supply source is guided to both ends in the axial direction of the roller bearing by the oil grooves. .

According to the first aspect of the present invention, the oil groove is formed to be inclined with respect to the axial direction on the outer peripheral surface of the outer ring, and a plurality of the oil grooves are provided adjacent to each other, so that the oil groove is not parallel to the roller arrangement direction. Therefore, local stress concentration can be suppressed in the outer ring. Further, it is possible to suppress the outer ring from being chipped when the outer ring outer peripheral surface is polished. In addition, since the oil groove is formed by communicating both axial ends, oil is supplied from a hydraulic pressure supply source to both axial ends of the roller bearing.
Therefore, a roller bearing that can supply oil to both ends in the axial direction, suppresses local stress concentration of the outer ring, and suppresses chipping of the outer ring when polishing the outer peripheral surface of the outer ring. Can be provided.

  Next, in the roller bearing according to a second aspect of the present invention, in the first aspect described above, the oil groove is formed in a trapezoidal uneven shape when viewed in an orthogonal cross section of the oil groove, and the adjacent unevenness The shape interval is smaller than the oil hole supplied from the hydraulic pressure supply source.

According to the second aspect of the invention, the oil groove is formed in a trapezoidal concavo-convex shape when viewed in an orthogonal cross section of the oil groove. For this reason, the corners of the convex portions forming the grooves are obtuse, so that the oil grooves are formed to be inclined with respect to the axial direction as described above, and in the polishing of the outer peripheral surface of the outer ring. Further, chipping of the outer ring can be further suppressed.
Further, since the interval between adjacent concave and convex shapes is formed smaller than the oil holes supplied from the hydraulic pressure supply source, the plurality of grooves are formed without the hydraulic supply holes being blocked by the convex portions forming the grooves. The oil can be supplied across

  In the present invention, oil can be supplied to both ends in the axial direction by taking the means of each of the above inventions, and the local stress concentration of the outer ring is suppressed and the outer ring outer peripheral surface is polished. A roller bearing capable of suppressing chipping of the outer ring can be provided.

It is an axial sectional view showing typically the state where the balancer shaft device to which the roller bearing concerning Embodiment 1 of the present invention is applied is arranged in the engine. It is a disassembled perspective view of the roller bearing which concerns on Embodiment 1 of this invention. It is sectional drawing of the roller bearing which concerns on Embodiment 1 of this invention. It is a side view of the roller bearing which concerns on Embodiment 1 of this invention. It is the VV sectional view taken on the line of FIG. It is an axial direction sectional view showing typically the state where the balancer shaft device to which the conventional roller bearing is applied is arranged in the engine. It is a disassembled perspective view of the conventional roller bearing.

A first embodiment for carrying out the present invention will be described with reference to FIGS. In view of facilitating the understanding of the configuration contents in each drawing for explaining the present invention, the configuration that does not affect the present invention is a schematic illustration in which the detailed structure is omitted, and such a location is shown. The description of may be omitted.
Here, a balancer shaft device 10 that reduces rotational vibration of the crankshaft 2 of the engine 1 will be described as an example of a bearing configuration that supports a rotating shaft member.
As shown in FIG. 1, in order to suppress the rotational vibration of the engine 1, a balancer shaft device 10 that rotates in conjunction with the crankshaft 2 with a period that is offset with respect to the periodic rotation of the crankshaft 2 is a housing. 4 is rotatably supported by the shaft support recess 5.

  The balancer shaft device 10 includes a balancer shaft 30 and a bearing 40. Here, the balancer shaft 30 rotates in conjunction with the crankshaft 2 at an offset period with respect to the periodic rotation of the crankshaft 2 in order to suppress rotational vibration of the engine 1. . The roller bearing 40 is configured to rotatably support the shaft portion 32 of the balancer shaft 30 with respect to the housing 4 of the engine 1 body. Below, the structure of this balancer shaft 30 and the roller bearing 40 is demonstrated.

First, the balancer shaft 30 will be described.
As shown in FIG. 2, the balancer shaft 30 is disposed at a position offset from the axis of the shaft 32, which is configured parallel to the crankshaft 2 of the engine 1 (see FIG. 1). The balancer weight 34 is integrally formed. Here, the balancer weight 34 is formed with a shaft portion 32 having a predetermined diameter, and the balancer weight 34 having a substantially semicircular cross section when viewed in the radial direction at a position eccentric from the shaft center of the shaft portion 32. Are integrally formed.
Further, the balancer shaft 30 is provided with a rib 36 extending outward in the radial direction opposite to the position where the balancer weight 34 is formed from the axial center. The rib 36 is configured to improve the bending rigidity of the balancer shaft 30. The cross-sectional shape of the balancer shaft 30 configured in this way as viewed in the radial cross-section is formed as a non-circular shape uniformly in the axial direction with the position side where the ribs 36 are formed as a thin wall. In addition, the balancer shaft 30 includes a cylindrical portion 37 in which the roller bearings 40 are arranged at a predetermined interval in the axial direction.
The cylindrical portion 37 is formed in a cylinder having a relatively larger diameter than the shaft portion 32. A roller bearing 40 is disposed on the outer peripheral surface of the cylindrical portion 37.
In addition, on the both ends in the axial direction of the cylindrical portion 37, eaves portions 38 that are radially extended in the radial direction are provided upright. The roller-shaped bearing 40 is sandwiched from both ends in the axial direction by the flange-shaped portion 38, and relative movement of the balancer shaft, ie, the bearing 40 in the axial direction is restricted.
As shown in FIG. 1, a driven gear 31 that meshes with the drive gear 3 disposed on the crankshaft 2 is disposed on the balancer shaft 30.

Next, the roller bearing 40 will be described.
As shown in FIG. 2, the roller bearing 40 includes an outer ring 42, an inner ring 48, rollers 44, and a cage 46.
The outer ring 42 is a split type in which a metal cylindrical member is divided into a semicircular shape when viewed in a radial cross section, and two are paired. This cylindrical inner peripheral surface is configured as an outer ring raceway surface 42a.
The inner ring 48 is a split type in which a metal cylindrical member is divided into a semicircular shape when viewed in a radial cross section, and two are paired. This cylindrical outer peripheral surface is configured as an inner ring raceway surface 48a.
The roller 44 is disposed between the outer ring 42 and the inner ring 48 so as to be able to roll. The roller 44 is a needle roller made of a metal cylindrical member.
The cage 46 is made of a synthetic resin, and is formed in an annular shape having a diameter that covers the outer periphery of the inner ring raceway surface 48 a of the inner ring 48. In the retainer 46, a plurality of pockets 46a into which the rollers 44 are fitted side by side in the circumferential direction are formed at equal intervals in the circumferential direction.
The retainer 46 is formed so as to be separated at one circumferential direction. The retainer 46 is elastically deformed in the radial direction and opened to be mounted from the radial direction of the balancer shaft 30.

The outer ring 42 will be described in more detail.
As shown in FIGS. 2 to 5, the oil groove 43 guides the lubricating oil (oil supplied from the hydraulic supply source) supplied from the oil passage 7 of the housing 4 to both ends in the axial direction of the roller bearing 40. Configured. As shown in FIGS. 2 and 4, the outer ring outer peripheral surface 42 b of the outer ring 42 is adjacent to a plurality of oil grooves 43 that are inclined with respect to the axial direction and communicate with both ends of the axial direction in parallel at equal intervals. Is provided. As shown in FIG. 5, the oil groove 43 is formed in a concavo-convex shape including an oil groove concave portion 43 a and an oil groove convex portion 43 b when viewed in an orthogonal cross section. In addition, the oil groove convex portion 43b has an obtuse angle formed on an upper surface when viewed in an orthogonal cross section and a corner portion 43c formed on a surface from both ends of the upper surface toward the oil groove concave portion 43a. Thereby, the oil groove convex part 43b is formed in trapezoid shape. As shown in FIGS. 4 and 5, the gap 43 d between the adjacent oil groove concave portions 43 a and the oil groove convex portions 43 b is formed to be smaller than the diameter 7 a of the oil passage 7 of the housing 4.
The oil groove 43 is formed by subjecting the outer ring outer peripheral surface 42b of the outer ring 42 to a shallow cutting process. For example, it is formed by knurling.

As shown in FIG. 2, in the balancer shaft device 10 in which the roller bearing 40 is mounted on the balancer shaft 30, first, an inner ring 48 is fitted into the cylindrical portion 37 of the balancer shaft 30 from the outside in the radial direction. Then, the cage 46 fitted with the rollers 44 is mounted on the inner ring raceway surface 48 a of the inner ring 48. Then, the outer ring 42 is attached. Thus, the balancer shaft device 10 is obtained.
As shown in FIG. 1, the housing 4 is provided with a shaft support recess 5 that supports the balancer shaft at a predetermined interval in the axial direction. Although not shown, the shaft support recess 5 is formed in a semicircular arc shape corresponding to the outer peripheral surface of the outer ring 42 of the roller bearing 40. In addition, an oil passage 7 (hydraulic supply source) for lubricating oil is formed in the housing 4 to the position of the shaft support recess 5. And the balancer shaft apparatus 10 with which the roller bearing 40 was mounted | worn is installed in each shaft support recessed part 5. FIG. Then, the cover member 6 is covered so as to cover the roller bearing 40 and then tightened with bolts. In this way, the balancer shaft device 10 is assembled in the housing 4 of the engine 1 body.

According to the roller bearing 40 configured as described above, the oil groove 43 is formed to be inclined with respect to the axial direction on the outer peripheral surface 42b of the outer ring, and a plurality of the oil grooves 43 are provided adjacent to each other. Therefore, local stress concentration in the outer ring 42 can be suppressed. Further, the outer ring 42 can be prevented from being chipped when the outer ring outer peripheral surface 42b is polished. Further, since the oil groove 43 is formed by communicating both axial ends, the lubricating oil supplied from the oil passage 7 of the housing 4 is guided to both axial ends of the roller bearing 40.
Therefore, oil can be supplied to both ends in the axial direction, and local stress concentration on the outer ring 42 can be suppressed, and chipping of the outer ring 42 can be suppressed when the outer ring outer peripheral surface 42b is polished. The roller bearing 40 which can be provided can be provided.

Further, the oil groove 43 is formed in a trapezoidal shape by an uneven shape including an oil groove concave portion 43 a and an oil groove convex portion 43 b when viewed in a cross section orthogonal to the oil groove 43. Therefore, the corners 43c formed by the upper surface and the inclined surface of the oil groove convex portion 43b forming the oil groove 43 have an obtuse angle, which is in contrast to the oil groove 43 being inclined with respect to the axial direction as described above. Accordingly, the outer ring 42 can be further prevented from being chipped in the polishing of the outer ring outer peripheral surface 42b.
In addition, since the gap 43d between the adjacent oil groove concave portion 43a and the oil groove convex portion 43b is formed to be smaller than the diameter 7a of the oil passage 7 of the housing 4, the oil groove convex portion 43b forming the oil groove 43 is used. Lubricating oil can be supplied across the plurality of oil grooves 43 without the oil passage 7 being blocked.

As mentioned above, although Embodiment 1 of this invention was demonstrated, the roller bearing of this invention is not limited to this Embodiment, It can implement with other various forms.
For example, in the first embodiment, the roller bearing is described as applied to a balancer shaft device. However, the present invention is not limited to this, and the roller bearing of the present invention is a roller bearing disposed in a portion that supports the rotating shaft, and the oil supplied from an external hydraulic supply source is used as the roller bearing. Any structure that can be guided to both ends in the axial direction is applicable to various rotating shafts. For example, it can be applied to a camshaft, a crankshaft and the like.

  Moreover, although the balancer shaft 30 has been described as constituting the ribs 36, the ribs need not be constructed if the bending rigidity is sufficiently satisfied. Further, the cage may be a split type in which two semicircular cages are paired when viewed in the radial cross section.

DESCRIPTION OF SYMBOLS 1 Engine 2 Crankshaft 3 Drive gear 4 Housing 5 Shaft support recessed part 6 Cover member 7 Oil path 7a Oil hole diameter 10 Balancer shaft device 30 Balancer shaft 31 Driven gear 32 Shaft part 34 Balancer weight 36 Rib 37 Cylindrical part 38 Saddle-shaped part 40 Roller bearing 42 Outer ring 42a Outer ring raceway surface 42b Outer ring outer peripheral surface 43 Oil groove 43a Oil groove concave portion 43b Oil groove convex portion 43c Corner portion 43d Space between oil groove concave portion and oil groove convex portion 44 Roller 46 Cage 46a Pocket 46b Separation portion 48 Inner ring 48a Inner ring raceway surface

Claims (2)

An outer ring formed in a cylindrical shape and having an outer ring raceway surface on the inner peripheral surface;
An inner ring formed in a cylindrical shape and having an inner ring raceway surface on the outer peripheral surface;
A plurality of rollers arranged to roll between the outer ring and the inner ring;
A roller bearing having a pocket for accommodating the roller,
A plurality of oil grooves that are inclined with respect to the axial direction and communicate with both ends in the axial direction are provided adjacent to the outer peripheral surface of the outer ring,
A roller bearing characterized in that oil supplied from a hydraulic pressure supply source is guided to both axial ends of the roller bearing by the oil groove. The roller bearing according to claim 1,
The oil groove is formed in a trapezoidal concavo-convex shape when viewed in an orthogonal cross section of the oil groove,
The roller bearing characterized in that an interval between the adjacent concave and convex shapes is smaller than an oil hole supplied from a hydraulic pressure supply source.

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