JP2017110765A - Slide bearing - Google Patents

Abstract

PROBLEM TO BE SOLVED: To provide a slide bearing capable of obtaining a friction reduction effect, and suppressing a total flow-out oil amount.SOLUTION: A slide bearing 1 is configured such that a cylinder is divided into two members in parallel with an axial direction and halved members 2, 2 are arranged vertically. On an inner peripheral surface of the lower halved member 2, two upstream side narrow grooves 3a, 3a are formed at an axial end part on an upstream side in a rotational direction, and on the inner peripheral surface of the lower halved member 2, two downstream side narrow grooves 3b, 3b are formed at an axial end part on a downstream side in the rotational direction.SELECTED DRAWING: Figure 2

Description

  The present invention relates to a slide bearing technique, and more particularly to a slide bearing technique in which a half member in which a cylinder is divided into two in parallel with an axial direction is vertically arranged.

  2. Description of the Related Art Conventionally, a bearing for supporting an engine crankshaft and having a half crack structure in which two members divided into two cylindrical shapes are combined is known. Further, in order to reduce the sliding area of the bearing and obtain a friction reduction effect, there is a structure in which the width of the bearing is narrowed. However, when the bearing width was narrowed, the amount of spilled oil increased. Therefore, a bearing in which relief portions (narrow grooves) are formed on the entire circumference at both ends in the axial direction of the bearing is known (for example, see Patent Document 1).

Japanese translation of PCT publication No. 2003-532036

  However, in conventional bearings with narrow grooves on the entire circumference, the load capacity decreases due to the reduction in sliding area, the oil film thickness necessary for good lubrication cannot be secured, and the total spilled oil The amount was large. Further, in the conventional bearing, foreign matter may flow into the downstream side of the bearing, which causes a decrease in sliding performance.

  In view of the above problems, the present invention provides a plain bearing that can obtain a friction reduction effect, suppress the total amount of oil spilled, and avoid foreign matter inflow to the downstream side of the bearing.

  The problem to be solved by the present invention is as described above. Next, means for solving the problem will be described.

  That is, according to the first aspect, the half member in which the cylinder is divided into two in parallel with the axial direction is arranged on the upper and lower sides in contact with each other, and the inner peripheral surface of the half member is in contact with the shaft. An upstream narrow groove formed at an axial end on the upstream side in the rotational direction on the inner peripheral surface of the lower half member, and an inner peripheral surface of the lower half member, A downstream narrow groove formed without communicating with the upstream narrow groove is provided at an axial end on the downstream side in the rotation direction.

  According to a second aspect of the present invention, the downstream narrow groove is formed to have a circumferential length longer than that of the upstream narrow groove.

  In the present invention, the upstream narrow groove and the downstream narrow groove are not communicated with the mating surface of the half member.

  According to a fourth aspect of the present invention, a peripheral edge portion is formed on the axially outer side of the upstream narrow groove and the downstream narrow groove, and a height of the peripheral edge portion from the bottom surface of the upstream narrow groove and the downstream narrow groove is increased. The height is higher than 0 mm and lower than the contact surface of the slide bearing with the shaft.

  As effects of the present invention, the following effects can be obtained.

  That is, by providing a narrow groove that does not hinder the generation of oil film pressure, it is possible to obtain a friction reduction effect while reducing the sliding area, and to suppress the total amount of oil spilled.

The front view which shows the slide bearing which concerns on embodiment of this invention. (A) The top view which shows the half member which comprises the slide bearing which concerns on 1st embodiment of this invention. (B) A1-A1 line sectional view of (a). (C) A2-A2 line sectional view of (a). (A) The top view which shows the half member which comprises the slide bearing which concerns on 2nd embodiment of this invention. (B) B1-B1 line sectional drawing of (a). (C) B2-B2 line sectional drawing of (a).

  Next, embodiments of the invention will be described. FIG. 1 is a front view of the sliding bearing 1, where the top and bottom of the screen is the vertical direction, and the front and back directions of the screen are the axial directions (front and back directions).

First, the half member 2 which comprises the slide bearing 1 which concerns on 1st embodiment is demonstrated using FIG.1 and FIG.2.
The slide bearing 1 is a cylindrical member, and as shown in FIG. 1, is applied to a slide bearing structure in which an inner peripheral surface thereof abuts on an engine crankshaft 11 (the shaft in the present invention). The plain bearing 1 is composed of two half members 2 and 2 (specifically, an upper half member 2U and a lower half member 2D). The two halved members 2 and 2 have a shape obtained by dividing a cylinder into two in parallel to the axial direction, and are formed so that the cross section is a semicircular shape. In the present embodiment, the half members 2 and 2 are arranged in contact with each other at the mating surfaces 2c to 2f and arranged vertically, and the mating surfaces 2c to 2f are arranged on the left and right. When the crankshaft 11 is pivotally supported by the slide bearing 1, a predetermined gap is formed, and lubricating oil is supplied to the gap from an oil passage (not shown).

  In FIG. 2A, the upper and lower half members 2 are shown. In the present embodiment, the rotation direction of the crankshaft 11 is the clockwise direction when viewed from the front as indicated by the arrow in FIG. In addition, the bearing angle is 0 degree at the right end position in FIG. 2B, and the counterclockwise direction in FIG. 2B is positive. That is, in FIG. 2B, the bearing angle at the left end position is defined as 180 degrees and the bearing angle at the lower end position is defined as 270 degrees.

  In the present embodiment, the upstream side and the downstream side are defined in the rotation direction of the crankshaft 11. For example, in the lower half member 2, the right mating surface in FIG. 2B is the upstream mating surface 2c in the rotational direction, and the left mating surface in FIG. 2B is the downstream mating surface 2d in the rotational direction. It becomes.

  A groove is provided in the circumferential direction in the center portion in the front-rear direction on the inner periphery of the upper half member 2, and a circular hole is provided in the center. In addition, mating surfaces 2e and 2f are arranged on the left and right of the upper half member 2, respectively. That is, when assembling the upper half member 2U and the lower half member 2D, the mating surfaces 2e and 2d and 2f and 2c are assembled so as to contact each other.

  Upstream narrow grooves 3a and 3a are formed at the axial end of the inner circumferential surface of the lower half member 2 on the upstream side in the rotational direction. In the present embodiment, two upstream narrow grooves 3a and 3a are provided in parallel in the axial direction.

  Specifically, the upstream narrow grooves 3a and 3a are circumferentially directed toward the direction (clockwise direction) in which the bearing angle is negative from the upstream mating surface 2c in the rotation direction of the crankshaft 11 (bearing angle is 0 degree). Is provided. That is, the upstream narrow grooves 3a and 3a communicate with the upstream mating surface 2c in the rotation direction of the crankshaft 11.

  In addition, downstream narrow grooves 3b and 3b are formed at the axial end of the inner circumferential surface of the lower half member 2 on the downstream side in the rotational direction. In this embodiment, two downstream narrow grooves 3b and 3b are provided in parallel in the axial direction.

  Specifically, the downstream narrow grooves 3b and 3b are circumferentially directed from the downstream facing surface 2d (the bearing angle is 180 degrees) in the rotation direction of the crankshaft 11 toward the direction in which the bearing angle is positive (counterclockwise direction). Provided in the direction. That is, the downstream narrow grooves 3b and 3b communicate with the downstream mating surface 2d of the crankshaft 11 in the rotation direction. Further, the downstream narrow grooves 3b and 3b do not communicate with the upstream narrow grooves 3a and 3a, respectively. Further, as shown by the arrow L2 in FIG. 2B, the downstream narrow grooves 3b and 3b are formed to have the same circumferential length as the upstream narrow grooves 3a and 3a indicated by the arrow L1.

  As described above, in the half member 2 constituting the plain bearing 1 according to the present embodiment, the upstream narrow grooves 3a and 3a and the downstream narrow grooves 3b and 3b that do not communicate with the upstream narrow grooves 3a and 3a are provided. , Is formed. Thereby, a sliding area can be increased compared with the conventional bearing which formed the narrow groove in the perimeter. That is, according to the present embodiment, it is possible to prevent the load capacity from decreasing and to secure the oil film thickness necessary for good lubrication. That is, in this embodiment, a friction reduction effect can be obtained, and the total amount of oil spilled can be suppressed.

  Moreover, in the half member 2 which comprises the slide bearing 1 which concerns on this embodiment, upstream narrow groove 3a * 3a and downstream narrow groove 3b * 3b are each formed in both upstream and downstream. Yes. Thereby, even when the upstream side and the downstream side of the half member 2 are assembled in reverse, it is possible to prevent the influence of erroneous assembly.

The widths of the upstream narrow grooves 3a and 3a and the downstream narrow grooves 3b and 3b (hereinafter simply referred to as narrow grooves 3a and 3b) are formed to be w as shown in FIG. Yes.
Further, the height d from the bottom surface of the narrow grooves 3a and 3b to the contact surface is formed to be shorter than the height D from the outer peripheral surface of the half member 2 to the contact surface.
Further, the peripheral edges 2a and 2b forming the axially outer surfaces of the narrow grooves 3a and 3b are such that the height h from the bottom surface of the narrow groove 3 is high from the bottom surface of the narrow grooves 3a and 3b to the contact surface. It is formed to be lower than the height d. That is, the outer peripheral edges 2a and 2b on the outer side in the axial direction are formed so as to be one step lower than the contact surface with the surrounding crankshaft 11.

  The peripheral edge portions 2a and 2b are formed so as to be one step lower than the contact surface with the surrounding crankshaft 11, so that the crankshaft 11 is tilted and is in contact with only one end portion in the axial direction The state of contact) between the peripheral portions 2a and 2b and the crankshaft 11 can be reduced, so that the peripheral portions 2a and 2b can be prevented from being damaged.

  Further, since the peripheral edge portions 2a and 2b are formed so as to be one step lower than the surrounding contact surfaces, a gap at the axial end portion of the slide bearing 1 is widened, and the amount of sucked-back oil is increased, resulting in a total outflow. The amount of oil is reduced.

  Next, the half member 2 which comprises the slide bearing 1 which concerns on 2nd embodiment is demonstrated using FIG. About the slide bearing 1 which concerns on this embodiment, since the structure is substantially the same as the slide bearing 1 which concerns on 1st embodiment, it attaches | subjects the same code | symbol about a common structure, and abbreviate | omits detailed description.

  In the plain bearing 1 according to the present embodiment, as shown in FIG. 3A, the upstream narrow grooves 3 c and 3 c are formed at the axial end portion on the upstream side in the rotational direction on the inner peripheral surface of the lower half member 2. Is formed. In the present embodiment, two upstream narrow grooves 3c and 3c are provided in parallel in the axial direction.

  Specifically, the upstream narrow grooves 3c and 3c are in a direction in which the bearing angle becomes negative from a portion (the bearing angle is about 15 degrees) where the bearing angle is more negative than the upstream mating surface 2c in the rotational direction of the crankshaft 11. It is provided in the circumferential direction toward (clockwise direction). That is, the upstream narrow grooves 3c and 3c do not communicate with the upstream mating surface 2c in the rotation direction of the crankshaft 11.

  In addition, downstream narrow grooves 3d and 3d are formed at axial ends of the inner peripheral surface of the lower half member 2 on the downstream side in the rotational direction. In the present embodiment, two downstream narrow grooves 3d and 3d are provided in parallel in the axial direction.

  More specifically, the downstream narrow grooves 3d and 3d are in a direction in which the bearing angle is positive from a location (bearing angle is about 195 degrees) where the bearing angle is more positive than the downstream mating surface 2d in the rotation direction of the crankshaft 11. It is provided in the circumferential direction toward (counterclockwise direction). That is, the downstream narrow grooves 3d and 3d do not communicate with the downstream mating surface 2d in the rotation direction of the crankshaft 11. Further, the downstream narrow grooves 3d and 3d do not communicate with the upstream narrow grooves 3c and 3c, respectively. Further, as shown by an arrow L4 in FIG. 3B, the downstream narrow grooves 3d and 3d are formed to have a longer circumferential length than the upstream narrow grooves 3c and 3c indicated by the arrow L3. .

  As described above, in the half member 2 constituting the plain bearing 1 according to the present embodiment, the upstream narrow grooves 3c and 3c and the downstream narrow grooves 3d and 3d that do not communicate with the upstream narrow grooves 3c and 3c are provided. , Is formed. Thereby, a sliding area can be increased compared with the conventional bearing which formed the narrow groove in the perimeter. That is, according to the present embodiment, it is possible to prevent the load capacity from decreasing and to secure the oil film thickness necessary for good lubrication. That is, in this embodiment, a friction reduction effect can be obtained, and the total amount of oil spilled can be suppressed.

  In the half member 2 constituting the plain bearing 1 according to the present embodiment, the downstream narrow grooves 3d and 3d are formed longer in the circumferential direction than the upstream narrow grooves 3c and 3c. By comprising in this way, the fall of the load capacity of an upstream can be suppressed rather than the downstream. For this reason, as compared with the configuration in which the downstream narrow grooves 3d and 3d and the upstream narrow grooves 3c and 3c have the same length as in the first embodiment, a friction reduction effect can be obtained while suppressing a decrease in load capacity. And the total amount of oil spilled can be reduced.

  In addition, in the half member 2 constituting the plain bearing 1 according to the present embodiment, the upstream narrow grooves 3c and 3c and the downstream narrow grooves 3d and 3d communicate with the mating surfaces 2c and 2d of the half member 2. Not. As a result, the amount of oil spilled through the mating surfaces 2c and 2d can be reduced, so that the narrow grooves 3a and 3b communicate with the mating surfaces 2c and 2d of the half member 2 as in the first embodiment. Thus, it is possible to obtain a friction reduction effect while suppressing a decrease in load capacity, and it is possible to suppress the total amount of spilled oil.

The widths of the upstream narrow grooves 3c and 3c and the downstream narrow grooves 3d and 3d (hereinafter simply referred to as narrow grooves 3c and 3d) are formed to be w as shown in FIG. Yes.
Further, the height d from the bottom surface of the narrow grooves 3c and 3d to the contact surface is formed to be shorter than the height D from the outer peripheral surface of the half member 2 to the contact surface.
Each of the peripheral portions 2a and 2b forming the axially outer surfaces 3c and 3d has a height h from the bottom surface of the narrow groove 3 and a height d from the bottom surface of the narrow grooves 3a and 3b to the contact surface. It is formed to be lower. That is, the outer peripheral edges 2a and 2b on the outer side in the axial direction are formed so as to be one step lower than the contact surface with the surrounding crankshaft 11.

  The peripheral edge portions 2a and 2b are formed so as to be one step lower than the contact surface with the surrounding crankshaft 11, so that the crankshaft 11 is tilted and is in contact with only one end portion in the axial direction The state of contact) between the peripheral portions 2a and 2b and the crankshaft 11 can be reduced, so that the peripheral portions 2a and 2b can be prevented from being damaged.

  Further, since the peripheral edge portions 2a and 2b are formed so as to be one step lower than the surrounding contact surfaces, a gap at the axial end portion of the slide bearing 1 is widened, and the amount of sucked-back oil is increased, resulting in a total outflow. The amount of oil is reduced.

DESCRIPTION OF SYMBOLS 1 Slide bearing 2 Half member 2a Peripheral part 3a Upstream narrow groove 3b Downstream narrow groove 11 Crankshaft

Claims (4)

A halved member obtained by dividing the cylinder into two parallel to the axial direction is a sliding bearing in which the halved members are placed in contact with each other on the upper and lower sides, and the inner peripheral surface of the halved member is in contact with the shaft,
An upstream narrow groove formed at an axial end on the upstream side in the rotational direction on the inner peripheral surface of the lower half member,
On the inner peripheral surface of the lower half member, a downstream narrow groove formed without communicating with the upstream narrow groove on the axial end on the downstream side in the rotational direction,
A plain bearing characterized by that. The downstream narrow groove is formed to have a longer circumferential length than the upstream narrow groove.
The plain bearing according to claim 1, wherein: The upstream narrow groove and the downstream narrow groove are not in communication with the mating surface of the half member.
The plain bearing according to claim 1 or 2, characterized by the above-mentioned. A peripheral edge is formed on the axially outer side of the upstream narrow groove and the downstream narrow groove, and the height of the peripheral edge from the bottom surface of the upstream narrow groove and the downstream narrow groove is higher than 0 mm, Formed to be lower than the contact surface with the shaft in the slide bearing,
The plain bearing according to any one of claims 1 to 3, wherein the plain bearing is provided.

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