JP2015197215A - 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 outflow oil amount.SOLUTION: In a slide bearing 1 in which halved members 2 obtained by dividing a cylinder into two parts in parallel with an axial direction are arranged vertically, step parts 3 recessed radially outside with respect to the inner peripheral surface of the halved member 2 are provided in the lower-side halved member 2 with a circumferential direction as a longitudinal direction, and groove parts 4 recessed radially outside with respect to the step parts 3 are provided on the axial direction central side of the step parts 3 with the circumferential direction as the longitudinal direction. The sum of widths W3 in the axial direction of the groove parts 4 is formed so as to be equal to or longer than 0 mm and smaller than a length obtained by subtracting the sum of widths W2 in the axial direction of the step parts 3 from a width W1 in the axial direction of the halved member 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 (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, with conventional bearings with grooves on the entire circumference, the load capacity decreases due to the reduction of the sliding area, the oil film thickness required for good lubrication cannot be secured, and the total amount of oil spilled There were many.

  Then, in view of the subject which concerns, this invention provides the bearing which can acquire the friction reduction effect and can suppress the total oil spill amount.

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

  That is, in claim 1, a sliding bearing in which a halved member obtained by dividing a cylinder into two in parallel with the axial direction is arranged vertically, and the circumferential direction of the lower half member is a longitudinal direction, A stepped portion that is recessed radially outward from the inner peripheral surface of the half member is provided.

  In claim 2, on the axially central side of the stepped portion, a circumferential groove direction is provided as a longitudinal direction, a groove portion recessed radially outward from the stepped portion is provided, and the sum of the axial widths of the groove portions is It is formed to be less than the length obtained by subtracting the sum of the axial widths of the stepped portions from the axial width of the half member that is larger than 0 mm.

  According to a third aspect of the present invention, the ratio of the sum of the axial widths of the groove portions to the axial width of the halved member is formed to be greater than 0% and 60% or less.

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

That is, by providing a groove portion 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.
Further, by providing the stepped portion at the peripheral edge portion of the groove portion, it is possible to effectively obtain a friction reducing effect 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 plane enlarged view which shows the half member which concerns on embodiment of this invention. (B) AA line cross-sectional enlarged view. (C) Similarly, the BB line cross-section enlarged view. Similarly, the graph which shows the relationship between the ratio with respect to the width | variety of the half member of the sum of the width | variety of a groove part, and the amount of leaking oil. (A) The plane enlarged view which shows the half member which concerns on 2nd embodiment of this invention. (B) AA line cross-sectional enlarged view. (C) Similarly, the BB line cross-section enlarged view. (A) The plane enlarged view which shows the half member which concerns on 3rd embodiment of this invention. (B) AA line cross-sectional enlarged view. (C) Similarly, the BB line cross-section enlarged view.

  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 front and rear 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 is applied to a slide bearing structure of an engine crankshaft 11 as shown in FIG. The plain bearing 1 is composed of two halved members 2. The two halved members 2 have a shape obtained by dividing a cylinder into two in parallel with the axial direction, and are formed so that the cross section is a semicircular shape. In this embodiment, the half member 2 is arrange | positioned up and down, and the mating surface is arrange | positioned at right and left. 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). Here, the central axis direction of the cylinder forming the slide bearing 1 is defined as an axial direction (front-rear direction). In addition, a direction along the circumference of the bottom surface of the cylinder forming the slide bearing 1 is defined as a circumferential direction. In addition, a direction perpendicular to the central axis and the side surface of the cylinder forming the slide bearing 1, that is, the thickness direction of the side wall is defined as the radial direction.

  In FIG. 2, 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. Further, the bearing angle ω is 0 degree at the right end position in FIG. 1, and the counterclockwise direction in FIG. 1 is positive. That is, in FIG. 1, the bearing angle ω at the left end position is defined as 180 degrees, and the bearing angle ω at the lower end position is defined as 270 degrees.

  As shown in FIG. 2C, the axial width of the half member 2 is W1. The bearing thickness (radial length) of the half member 2 is H1. Further, in the lower half member 2, the left mating surface in FIG. 1 is the rotation direction downstream mating surface 2a, and the right mating surface in FIG. 1 is the rotation direction upstream mating surface 2b.

On the inner periphery of the upper half member 2, a groove is provided in the circumferential direction, and a circular hole is provided in the center. In addition, mating surfaces are arranged on the left and right of the upper half member 2.
On the sliding surface on the inner periphery of the lower half member 2, a stepped portion 3 is formed which communicates with both axial end surfaces. In addition, a groove portion 4 is provided on the center side in the axial direction of the step portion 3 so that the circumferential direction is the longitudinal direction and the groove portion 4 is recessed radially outward from the step portion 3. In the present embodiment, two step portions 3 and two groove portions 4 are provided.

  Next, a detailed configuration of the step portion 3 will be described with reference to FIG.

The circumferential length l of the stepped portion 3 is formed from the downstream end 3a in the rotational direction (bearing angle is 180 degrees) to the upstream end 3b in the rotational direction (bearing angle is ω1). is there. The downstream end 3a in the rotational direction of the step portion 3 is provided so as to communicate with the downstream mating surface 2a in the rotational direction of the half member 2. The bearing angle ω1 is greater than 180 degrees and equal to or less than 270 degrees. More specifically, the bearing angle ω1 is present in a region that is usually greater than 225 degrees and less than or equal to 270 degrees.
The length H2 from the inner peripheral surface 3c of the stepped portion 3 to the outer peripheral surface of the half member 2 is formed to be equal to or less than the bearing thickness H1 of the half member 2.
The sum of the axial width W2 of the stepped portion 3 is configured to be shorter than the axial width W1 of the half member 2 as shown in FIG.

  Next, the detailed structure of the groove part 4 is demonstrated using FIG.

  The groove 4 is provided in the lower half member 2. In the present embodiment, two groove portions 4 are provided in parallel in the axial direction. The downstream end 4a in the rotational direction of the groove 4 is provided so as to communicate with the downstream mating surface 2a in the rotational direction of the half member 2.

  As shown in FIG. 2B, the circumferential length l of the groove 4 is provided to be the same as the circumferential length l of the stepped portion 3.

The radial depth H3 of the groove 4 is formed to be shorter than the bearing thickness H1, as shown in FIG. 2 (c).
Further, the radial length H4 from the inner peripheral surface 3c of the step portion 3 to the bottom surface 4c of the groove portion 4 is equal to or less than the depth H3 in the radial direction of the groove portion 4 as shown in FIG. Is formed. That is, the groove portion 4 is recessed outward in the radial direction from the step portion 3.

  The sum of the axial widths W3 of the two grooves 4 is configured to be shorter than the axial width W1 of the half member 2, as shown in FIG.

Next, the axial width W3 of the groove 4 will be described in detail.
The sum of the axial widths W3 of the two groove portions 4 is 0 mm or more and is equal to or less than the length obtained by subtracting the sum of the axial widths W2 of the stepped portions 3 from the axial width W1 of the half member 2. It is configured as follows.
In the present embodiment, the sum of the axial widths W3 of the groove portions 4 is shorter than the length obtained by subtracting the sum of the axial widths W2 of the stepped portions 3 from the axial width W1 of the half member 2. Is formed.
By comprising in this way, the friction reduction effect and the leakage oil amount reduction effect can be acquired.

  The ratio of the sum of the axial widths W3 of the grooves 4 to the axial width W1 of the half member 2 is 0% or more and 60% or less. In the present embodiment, the ratio of the sum of the axial widths W3 of the grooves 4 to the axial width W1 of the half member 2 is formed to be approximately 40%.

  By comprising in this way, a friction reduction effect and a leakage oil amount reduction effect can be acquired effectively. For example, as shown in FIG. 3, when the ratio of the sum of the axial widths W3 of the grooves 4 to the axial width W1 of the halved member 2 exceeds 60%, the load capacity decreases and good lubrication is achieved. The required oil film thickness cannot be ensured and friction increases. Therefore, the oil leakage reduction effect increases until the ratio of the sum of the axial widths W3 of the grooves 4 to the axial width W1 of the half member 2 is 60%, and the subsequent oil leakage reduction effect. Is constant.

Next, the half member 2 according to the second embodiment will be described. In addition, about the member of the same name as 1st embodiment, the same code | symbol is attached | subjected.
FIGS. 4A to 4C show the half member 2 according to the second embodiment. In the present embodiment, no groove is provided, and the side surface on the axial end surface side of the stepped portion 3 communicates with the axial end surface of the half member 2.
That is, in this embodiment, the length of the groove part 4 in the axial direction is 0 mm, and the ratio of the half member 2 to the axial width W1 is 0%.
Even in such a configuration, a friction reduction effect and a leakage oil amount reduction effect can be effectively obtained.

Next, the half member 2 according to the third embodiment will be described. In addition, about the member of the same name as 1st embodiment, the same code | symbol is attached | subjected.
5A to 5C show the half member 2 according to the third embodiment. In the present embodiment, two step portions 3 are provided at both axial ends of the half member 2, and one groove portion 4 is provided between the two step portions 3.

  Next, a detailed configuration of the step portion 3 will be described with reference to FIG.

The circumferential length l of the stepped portion 3 is formed from the downstream end 3a in the rotational direction (bearing angle is 180 degrees) to the upstream end 3b in the rotational direction (bearing angle is ω1). is there. The downstream end 3a in the rotational direction of the step portion 3 is provided so as to communicate with the downstream mating surface 2a in the rotational direction of the half member 2. The bearing angle ω1 is greater than 180 degrees and equal to or less than 270 degrees. More specifically, the bearing angle ω1 is present in a region that is usually greater than 225 degrees and less than or equal to 270 degrees.
The length H2 from the inner peripheral surface 3c of the stepped portion 3 to the outer peripheral surface of the half member 2 is formed to be equal to or less than the bearing thickness H1 of the half member 2.
The sum of the axial widths W2 of the stepped portions 3 is configured to be shorter than the axial width W1 of the half member 2, as shown in FIG.
In the present embodiment, the sum of the axial width W2 of the stepped portion 3 is a length obtained by subtracting the axial width W3 of the groove portion 4 from the axial width W1 of the half member 2.

  Next, the detailed structure of the groove part 4 is demonstrated using FIG.

  As shown in FIG. 5B, the circumferential length l of the groove 4 is provided to be the same length as the circumferential length l of the stepped portion 3.

The depth H3 in the radial direction of the groove portion 4 is formed to be shorter than the bearing thickness H1, as shown in FIG.
The axial width W3 of the groove 4 is configured to be shorter than the axial width W1 of the half member 2, as shown in FIG. In the present embodiment, the axial width W3 of the groove portion 4 is a length obtained by subtracting the sum of the axial width W2 of the stepped portion 3 from the axial width W1 of the half member 2.

In the present embodiment, the ratio of the axial width W3 of the groove 4 to the axial width W1 of the half member 2 is approximately 60%.
By comprising in this way, the friction reduction effect and the leakage oil amount reduction effect can be acquired.

  In the slide bearing according to the first to third embodiments, the groove portion is constituted by two or one, but is not limited to this, and may be constituted by three or more.

As described above, it is a plain bearing 1 in which the half member 2 obtained by dividing the cylinder into two parallel to the axial direction is arranged vertically, and the lower half member 2 has the circumferential direction as the longitudinal direction, A stepped portion 3 that is recessed radially outward from the inner peripheral surface of the member 2 is provided.
By comprising in this way, by providing the level | step-difference part 3, it can adjust so that the amount of sucking back of oil may be increased.

Further, a groove portion 4 is provided on the center side in the axial direction of the step portion 3 so that the circumferential direction is the longitudinal direction and is recessed outward in the radial direction from the step portion 3, and the sum of the axial widths W3 of the groove portion 4 is less than 0 mm. It is formed so as to be less than or equal to a length obtained by subtracting the sum of the axial width W2 of the stepped portion 3 from the axial width W1 of the half member 2.
With this configuration, by providing the groove 4 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. Can do.

Further, the ratio of the sum of the axial widths W3 of the grooves 4 to the axial width W1 of the half member 2 is formed to be greater than 0% and 60% or less.
By comprising in this way, the leakage oil amount reduction effect and the friction reduction effect can be obtained more effectively.

DESCRIPTION OF SYMBOLS 1 Sliding bearing 2 Half member 2a Rotating direction downstream mating surface 2b Rotating direction upstream mating surface 3 Step part 3a Rotating direction downstream end 3b Rotating direction upstream end 4 Groove 4a Rotating direction downstream end 4b Rotating direction Upstream end 11 Crankshaft

Claims (3)

A slide bearing in which a half member divided into two in parallel with the axial direction is arranged vertically,
A slide bearing characterized in that a stepped portion having a circumferential direction as a longitudinal direction and recessed outward in the radial direction from the inner peripheral surface of the half member is provided. On the center side in the axial direction of the stepped portion, the circumferential direction is the longitudinal direction, and a groove portion that is recessed radially outward from the stepped portion is provided.
The sum of the axial widths of the grooves is greater than 0 mm and is equal to or less than the length obtained by subtracting the sum of the axial widths of the stepped portions from the axial width of the half member. The plain bearing according to claim 1. The slide bearing according to claim 2, wherein a ratio of a sum of the widths in the axial direction of the groove portions to a width in the axial direction of the half member is greater than 0% and equal to or less than 60%. .

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