JP2016033414A - Slide bearing - Google Patents

Abstract

PROBLEM TO BE SOLVED: To provide a bearing capable of obtaining friction reduction effect and suppressing the total sum of flow-out oil amount.SOLUTION: In a slide bearing 1 in which half members 2 obtained by dividing a cylinder into two in parallel with an axial direction, are vertically disposed, a circumferential fine groove 3 is formed on an axial end portion of the lower half member 2, the fine groove 3 is composed of a bottom surface 3a, a first side wall 3b disposed between an axial outer end of the bottom surface 3a and an inner peripheral face 2a of the half member 2, and a second side wall 3c disposed between an axial inner end of the bottom surface 3a and the inner peripheral face 2a of the half member 2. The first side wall 3b is inclined to an axial outer side from the bottom surface 3a toward the inner peripheral face 2a of the half member 2, the second side wall 3c is inclined to an axial inner side from the bottom surface 3a toward the inner peripheral face 2a of the half member 2, and an inclination angle θ1 to the bottom surface 3a of the first side wall 3b is larger than an inclination angle θ2 to the bottom surface 3a of the second side wall 3c.SELECTED DRAWING: Figure 3

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.

  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, according to the first aspect of the present invention, there is provided a plain bearing in which a half member divided into two in parallel with the axial direction is arranged vertically, and is narrowed in the circumferential direction at the axial end of the lower half member. A groove is provided, and the narrow groove includes a bottom surface, a first side wall provided between an axially outer end of the bottom surface and an inner peripheral surface of the half member, an axially inner end of the bottom surface, and a half member. A second side wall provided between the inner peripheral surface of the first member and the first side wall so as to incline outward in the axial direction from the bottom surface toward the inner peripheral surface of the half member. The second side wall is formed so as to be inclined inward in the axial direction from the bottom surface toward the inner peripheral surface of the half member, and an inclination angle of the first side wall with respect to the bottom surface Is larger than the inclination angle of the second side wall with respect to the bottom surface.

  According to a second aspect of the present invention, an inclination angle of the first side wall with respect to the bottom surface is not less than 60 ° and not more than 90 °.

  According to a third aspect of the present invention, the inclination angle of the second side wall with respect to the bottom surface is not less than 30 ° and not more than 90 °.

  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.
Further, by reducing the inclination angle of the side wall on the inner side in the axial direction, the amount of oil drawn into the inner side in the axial direction can be increased. As a result, oil easily spreads on the inner peripheral surface of the bearing, a sufficient oil film is formed even during cold start, and the temperature of the oil film can be raised quickly by frictional heat, so that friction can be reduced.

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. The BB sectional expanded view which shows the half member which concerns on embodiment of this invention.

  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). 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.

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 and 2. 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 up and down, and mating surfaces 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. 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.

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 inner peripheral surface 2a of the lower half member 2, a narrow groove 3 is formed at the end in the axial direction.
The inner peripheral surface 2 a of the half member 2 is a sliding surface that supports the crankshaft 11.

The narrow groove 3 is provided in the lower half member 2. In the present embodiment, two narrow grooves 3 are provided in parallel in the axial direction. The downstream end portion in the rotation direction of the narrow groove 3 is close to the downstream alignment surface in the rotation direction of the crankshaft 11, and the downstream end portion in the rotation direction and the downstream alignment surface in the rotation direction are provided without communication. Yes.
Specifically, the downstream end of the narrow groove 3 in the rotational direction is disposed at a bearing angle ω0 that is greater than 180 degrees where the downstream facing surface of the crankshaft 11 is located. In other words, the narrow groove 3 is circular in a direction (counterclockwise direction) in which the bearing angle ω is positive from the bearing angle ω that is larger than the mating surface on the downstream side in the rotation direction of the crankshaft 11 (bearing angle ω is 180 degrees). It is provided in the circumferential direction.
In the lower half member 2, the right mating surface in FIG. 1 is the upstream mating surface in the rotational direction, and the left mating surface in FIG. 1 is the downstream mating surface in the rotational direction.

  As shown in FIG. 2B, the circumferential length l of the narrow groove 3 is from the downstream end in the rotational direction (bearing angle is ω0) to the upstream end in the rotational direction (bearing angle is ω1). It is formed in length. The bearing angle ω1 is greater than ω0 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.

Next, the BB cross section of the narrow groove 3 is demonstrated using FIG.2 (c). Here, since the two narrow grooves 3 according to this embodiment have a symmetrical structure and the same configuration, the narrow grooves 3 provided on the front side in the axial direction will be described.
As shown in FIG. 2 (c), the narrow groove 3 includes a bottom surface 3a, a first side wall 3b provided between the axially outer end of the bottom surface 3a and the inner peripheral surface 2a of the half member 2, The second side wall 3c is provided between the axially inner end of the bottom surface 3a and the inner peripheral surface 2a of the half member 2.
The bottom surface 3 a of the narrow groove 3 is a surface formed on the radially outer side of the narrow groove 3, and is provided on the radially outer side with respect to the inner peripheral surface 2 a of the half member 2. In other words, as shown in FIG. 2C, the length d between the bottom surface 3a and the outer peripheral surface is smaller than the length (bearing thickness) D between the inner peripheral surface 2a and the outer peripheral surface. It is formed to become.

The first side wall 3 b is a wall surface provided between the axially outer end of the bottom surface 3 a and the inner peripheral surface 2 a of the half member 2, and goes from the bottom surface 3 a toward the inner peripheral surface 2 a of the half member 2. It is formed so as to be inclined outward in the axial direction.
The second side wall 3 c is a wall surface provided between the axially inner end of the bottom surface 3 a and the inner peripheral surface 2 a of the half member 2, and goes from the bottom surface 3 a toward the inner peripheral surface 2 a of the half member 2. It is formed so as to be inclined inward in the axial direction.
In other words, the axial width of the narrow groove 3 is formed so as to be wider than the width w2 of the bottom surface 3a toward the inner side in the radial direction. The width w1 of the narrow groove at the same height in the radial direction as the inner peripheral surface 2a of the half member 2 is formed to be the largest.

Next, the inclination angle θ1 of the first side wall 3b and the inclination angle θ2 of the second side wall 3c will be described.
Here, the inclination angle is an angle with respect to the bottom surface 3a, and as shown in FIG. 3C, the angle formed by the straight line extending the bottom surface 3a and the first side wall 3b is on the opposite side of the narrow groove 3. The angle that can be formed on the opposite side of the narrow groove 3 among the angle that can be formed and the angle that can be formed by the straight line extending the bottom surface 3a and the second side wall 3c.

  The inclination angle θ1 of the first side wall 3b is not less than 60 ° and not more than 90 °. By setting the inclination angle θ1 to 60 degrees or more, the amount of oil leaking outward in the axial direction can be suppressed to a certain value or less. Further, by providing the first side wall 3b with an inclination, it is possible to suppress the generation of burrs when the narrow groove 3 is provided.

  The inclination angle θ2 of the second side wall 3c is not less than 30 ° and not more than 90 °. By setting the angle of the inclination angle θ2 to 30 ° or more, it is possible to secure the amount of the inner peripheral surface 2a that is pulled inward in the axial direction while avoiding a decrease in load capacity due to a decrease in the sliding area. Further, by providing the second side wall 3c with an inclination, it is possible to suppress the generation of burrs when the narrow groove 3 is provided.

The inclination angle θ1 of the first side wall 3b is configured to be larger than the inclination angle θ2 of the second side wall 3c. In other words, the inclined surface of the first side wall 3b is formed to be steeper than the inclined surface of the second side wall 3c.
With this configuration, the amount of oil drawn from the second side wall 3c increases, and the amount of oil supplied to the inner side in the axial direction of the half member 2 increases. For this reason, it becomes easy to form a lubricating oil film between the crankshaft 11 and the plain bearing 1, and a sufficient oil film is formed even at the time of cold start, and the oil film can be heated quickly by frictional heat, so that friction Can be reduced.

  In the present embodiment, the bottom surface 3a, the first side wall 3b, and the second side wall 3c are formed in a straight line in the cross section of the narrow groove 3 viewed from the circumferential direction. However, the present invention is not limited to this. Instead, the bottom surface or the side wall can be formed in a curved shape in the cross section of the narrow groove as viewed from the circumferential direction.

As described above, the sliding bearing 1 in which the half member 2 obtained by dividing the cylinder into two in parallel with the axial direction is arranged vertically, and is narrowed in the circumferential direction at the axial end of the lower half member 2. The groove 3 is provided, and the narrow groove 3 is formed in the axial direction of the bottom surface 3a, the first side wall 3b provided between the axially outer end of the bottom surface 3a and the inner peripheral surface 2a of the half member 2, and the bottom surface 3a. A second side wall 3c provided between the inner end and the inner peripheral surface 2a of the half member 2, and the first side wall 3b extends from the bottom surface 3a to the inner peripheral surface of the half member 2 The second side wall 3c is formed so as to incline in the axial direction as it goes from the bottom surface 3a toward the inner peripheral surface 2a of the half member 2. The inclination angle θ1 with respect to the bottom surface 3a of the first side wall 3b is greater than the inclination angle θ2 with respect to the bottom surface 3a of the second side wall 3c. Is also big.
With this configuration, by providing the narrow groove 3 that does not hinder the generation of the 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. be able to. Further, by reducing the inclination angle θ2 of the second side wall 3c, the amount of oil drawn inward in the axial direction can be increased. As a result, oil easily spreads on the inner peripheral surface of the bearing, a sufficient oil film is formed even during cold start, and the temperature of the oil film can be raised quickly by frictional heat, so that friction can be reduced.

Further, the inclination angle θ1 of the first side wall 3b with respect to the bottom surface 3a is not less than 60 ° and not more than 90 °.
By comprising in this way, generation | occurrence | production of the burr | flash when forming the narrow groove 3 can be suppressed, preventing the amount of leaked oil from the 1st side wall 3b side increasing.

Further, the inclination angle θ2 with respect to the bottom surface 3a of the second side wall 3c is not less than 30 ° and not more than 90 °.
By configuring in this way, it is possible to suppress the generation of burrs when forming the narrow groove 3 while securing the amount of drawing inward in the axial direction.

DESCRIPTION OF SYMBOLS 1 Slide bearing 2 Half member 2a Inner peripheral surface 3 Narrow groove 3a Bottom face 3b First side wall 3c Second side wall 11 Crankshaft

Claims (3)

A slide bearing in which a half member divided into two in parallel with the axial direction of the cylinder is arranged vertically, and a narrow groove is provided in the circumferential direction at the axial end of the lower half member,
The narrow groove includes a bottom surface, a first side wall provided between an axially outer end of the bottom surface and an inner peripheral surface of the half member, an axial inner end of the bottom surface, and an inner peripheral surface of the half member. And a second side wall provided between and
The first side wall is formed so as to be inclined outward in the axial direction from the bottom surface toward the inner peripheral surface of the half member, and the second side wall is formed from the bottom surface to the inner peripheral surface of the half member. It is formed to incline in the axial direction as it goes to
A sliding bearing, wherein an inclination angle of the first side wall with respect to the bottom surface is larger than an inclination angle of the second side wall with respect to the bottom surface. The sliding bearing according to claim 1, wherein an inclination angle of the first side wall with respect to the bottom surface is 60 ° or more and 90 ° or less. The sliding bearing according to claim 1 or 2, wherein an inclination angle of the second side wall with respect to the bottom surface is 30 ° or more and 90 ° or less.

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