JP6541144B2 - Slide bearing - Google Patents

Description

  The present invention relates to the technology of a slide bearing, and relates to the technology of a slide bearing in which half members obtained by dividing a cylinder into two in parallel with the axial direction are disposed one above the other.

  2. Description of the Related Art Conventionally, there has been known a sliding bearing for supporting a crankshaft of an engine, which is a half-split structure in which two members obtained by dividing a cylindrical shape into two are combined. In addition, there is a structure in which the width of the bearing is narrowed in order to reduce the sliding area of the bearing and obtain a friction reduction effect. However, when the width of the bearing was narrowed, the amount of oil spilled was increasing. Then, the bearing which formed the relief part (thin groove) in the perimeter in the axial direction both ends of the above-mentioned bearing is publicly known (for example, refer to patent documents 1).

Japanese Patent Publication No. 2003-532036

  However, in the conventional bearing in which the narrow groove is formed on the entire circumference, the load capacity is reduced due to the reduction of the sliding area, and the oil film thickness necessary for good lubrication can not be secured. There was a large amount.

  Then, in view of the subject which concerns on this invention, the friction reduction effect can be acquired and the bearing which can suppress the amount of oil spills of a sum total is provided.

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

That is, according to the first aspect of the present invention, there is provided a slide bearing in which half members obtained by dividing a cylinder into two halves in parallel with the axial direction are vertically disposed, the upper half member in the rotational direction of the shaft held by the slide bearing. The position of the mating surface between the end face on the lower side and the end face on the upper side in the direction of rotation of the lower half of the shaft is defined as 0 °, and from the position of 0 ° opposite to the direction of rotation of the axis range in the case of defining a bearing angle as the rotation angle of the direction, the half-split elements of the lower, from the position before SL bearing angle 180 °, to a position of the bearing angle is greater than 180 ° 270 ° or less Only in the circumferential direction, the longitudinal direction is the same, and two narrow grooves are provided in parallel in the axial direction, and the radius of the half member is smaller than the bottom of the narrow groove at the peripheral edge on the axial end face side of the narrow groove. While projecting inward in the direction A stepped portion recessed outward in the radial direction with respect to the inner circumferential surface of the member is provided, and the sum of the axial widths of the stepped portions is larger than 0 mm to the axial width of the narrow groove from the axial width of the half member It is formed to be equal to or less than the length obtained by subtracting the sum of.

  According to the second aspect of the present invention, the ratio of the sum of the axial widths of the stepped portions to the axial width of the half members is greater than 0% and not more than 70%.

  The effects of the present invention are as follows.

That is, by providing the fine groove not to prevent the generation of the oil film pressure, it is possible to obtain the friction reduction effect while reducing the sliding area, and to suppress the total amount of oil outflow.
Further, by providing the step portion at the peripheral portion of the narrow groove, it is possible to effectively obtain the friction reduction effect, and to suppress the total amount of oil spilled.

The front view showing the slide bearing concerning the embodiment of the present invention. (A) The enlarged plane view which shows the half member based on embodiment of this invention. (B) Similarly the AA line cross section enlarged view. (C) Similarly the B-B line cross section enlarged view. Similarly, the graph figure 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 level | step-difference part, and the amount of leaked oil. (A) The plane enlarged view which shows the half member concerning 2nd embodiment of this invention. (B) Similarly the AA line cross section enlarged view. (C) Similarly the B-B line cross section enlarged view. (A) The plane enlarged view which shows the half member based on 3rd embodiment of this invention. (B) Similarly the AA line cross section enlarged view. (C) Similarly the B-B line cross section enlarged view.

  Next, an embodiment of the invention will be described. In addition, FIG. 1 is a front view of the slide bearing 1, and let the upper and lower sides of a screen be the up-down direction, and let the near direction and the back direction of a screen be 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 as shown in FIG. 1, is applied to a slide bearing structure of a crankshaft 11 of an engine. The slide bearing 1 is composed of two half members 2. The two half members 2 have a shape obtained by dividing a cylinder into two in parallel with the axial direction, and are formed to have a semicircular cross section. In the present embodiment, the half members 2 are vertically disposed, and the right and left mating surfaces are disposed. When the crankshaft 11 is 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 the 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 the circumferential direction. Further, a direction orthogonal 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 rotational direction of the crankshaft 11 is in the clockwise direction as viewed from the front as shown by the arrow in FIG. Further, the bearing angle ω makes the position of the right end in FIG. 1 0 degrees, and in FIG. 1, makes the counterclockwise direction positive. That is, in FIG. 1, the bearing angle ω at the left end position is 180 degrees, and the bearing angle ω at the lower end position is 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.

A groove is provided circumferentially on the inner periphery of the upper half member 2, and a circular hole is provided at the center. Moreover, the mating surface is disposed on the left and right of the upper half member 2.
In the sliding surface on the inner periphery of the lower half member 2, a narrow groove 3 is formed on the inner side of both end surfaces in the axial direction.

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 rotation direction downstream end 3 a of the narrow groove 3 is provided to communicate with the rotation direction downstream mating surface 2 a of the half member 2.
Specifically, the downstream end portion 3 a of the narrow groove 3 in the rotational direction is disposed on the downstream mating surface 2 a of the half member 2 in the rotational direction.
In the lower half member 2, the left mating surface in FIG. 1 is the downstream mating surface 2a in the rotational direction, and the right mating surface in FIG. 1 is the upstream mating surface 2b in the rotational direction.

  Further, at the peripheral edge on the end face side in the axial direction of the narrow groove 3, there is provided a step 4 which is recessed outward in the radial direction with respect to the inner peripheral surface of the half member 2. In the present embodiment, two step portions 4 are provided on the peripheral edge on the rear side of the narrow groove 3 on the rear side in the axial direction and on the peripheral edge on the front side of the narrow groove 3 on the front side in the axial direction It is provided so as to be parallel to the longitudinal direction of the narrow groove 3. The rotation direction downstream side end 4a of the step 4 is provided to communicate with the rotation direction downstream side mating surface 2a. Further, the rotational direction upstream end 4b is provided to the same position as the rotational direction upstream end 3b of the narrow groove 3 in the circumferential direction. In other words, the circumferential length of the step 4 is equal to the circumferential length l of the narrow groove 3.

  Next, the detailed configuration of the narrow groove 3 will be described with reference to FIG.

  The circumferential length l of the narrow groove 3 is a length 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 bearing angle ω1 is greater than 180 degrees and equal to or less than 270 degrees. More specifically, the bearing angle ω1 is in a region that is usually larger than 225 degrees and not larger than 270 degrees.

The radial depth H2 of the narrow groove 3 is formed to be shorter than the bearing thickness H1, as shown in FIG. 2 (c).
The sum of the axial width W2 of the two narrow grooves 3 is configured to be shorter than the axial width W1 of the half member 2, as shown in FIG. 2 (c).

  Next, the detailed configuration of the stepped portion 4 will be described with reference to FIG.

The circumferential length of the step portion 4 is set to be the same as the circumferential length l of the narrow groove 3 as shown in FIG. 2 (b).
The radial length H3 from the inner circumferential surface 4c of the step 4 to the bottom surface 3c of the narrow groove 3 is, as shown in FIG. 2C, equal to or less than the radial depth H2 of the narrow groove 3 It is formed.
The sum of the axial width W3 of the step 4 is not less than 0 mm and equal to or less the sum of the axial width W2 of the fine groove 3 and the axial width W1 of the half member 2 It is configured. In the present embodiment, the sum of the axial width W3 of the step portion 4 is shorter than the sum of the axial width W2 of the narrow groove 3 and the axial width W1 of the half member 2. Is formed.
With such a configuration, it is possible to obtain a friction reduction effect and a leakage oil amount reduction effect.

  The ratio of the sum of the axial width W3 of the step 4 to the axial width W1 of the half member 2 is 0% or more and 70% or less. In the present embodiment, the ratio of the sum of the axial width W3 of the stepped portion 4 to the axial width W1 of the half member 2 is approximately 40%.

  With such a configuration, it is possible to effectively obtain the friction reduction effect and the leakage oil amount reduction effect. For example, as shown in FIG. 3, as the ratio of the sum of the axial width W3 of the step 4 to the axial width W1 of the half member 2 increases from 0%, the friction reduction effect and the leakage oil amount reduction The effect is greater. When the ratio of the sum of the axial width W3 of the step 4 to the axial width W1 of the half member 2 exceeds 70%, the amount of oil leakage becomes substantially 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.
The half member 2 which is 2nd embodiment is shown by FIG. 4 (a)-(c). In the present embodiment, no stepped portion is provided, and the side surface on the axial direction end face side of the narrow groove 3 communicates with the axial direction end face.
That is, in the present embodiment, the axial length of the step portion is 0 mm, and the ratio to the axial width W1 of the half member 2 is 0%.
Even in such a configuration, it is possible to effectively obtain the friction reduction effect and the leakage oil amount reduction effect.

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.
The half member 2 which is 3rd embodiment is shown by FIG. 5 (a)-(c). In the present embodiment, one narrow groove 3 is provided, and the step portion 4 is provided on the peripheral edge on both sides in the axial direction.

  Next, the detailed configuration of the narrow groove 3 will be described with reference to FIG.

  The circumferential length l of the narrow groove 3 is a length 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 bearing angle ω1 is greater than 180 degrees and equal to or less than 270 degrees. More specifically, the bearing angle ω1 is in a region that is usually larger than 225 degrees and not larger than 270 degrees.

The radial depth H2 of the narrow groove 3 is formed to be shorter than the bearing thickness H1, as shown in FIG. 5 (c).
The axial width W2 of the narrow groove 3 is configured to be shorter than the axial width W1 of the half member 2, as shown in FIG. 5 (c).

  Next, the detailed configuration of the stepped portion 4 will be described with reference to FIG.

The length in the circumferential direction of the step portion 4 is set to be the same as the length l in the circumferential direction of the narrow groove 3 as shown in FIG. 5A.
The radial length H3 from the inner circumferential surface 4c of the step portion 4 to the bottom surface 3c of the narrow groove 3 is formed to be equal to or less than the radial depth H2 of the narrow groove 3.
In the present embodiment, the sum of the axial width W3 of the stepped portion 4 is a length obtained by subtracting the axial width W2 of the narrow groove 3 from the axial width W1 of the half member 2.
Further, in the present embodiment, the ratio of the sum of the axial width W3 of the stepped portion 4 to the axial width W1 of the half member 2 is approximately 70%.
With such a configuration, it is possible to obtain a friction reduction effect and a leakage oil amount reduction effect.

  In the slide bearings according to the first to third embodiments, the narrow groove is formed by two or one, but the invention is not limited to this, and three or more can also be formed. .

As mentioned above, it is the slide bearing 1 which has arranged the half member 2 which divided the cylinder into two in parallel with the axial direction up and down, and the narrow groove which makes the circumferential direction a longitudinal direction in the lower half member 2 3 is provided, and the step portion 4 recessed outward in the radial direction with respect to the inner peripheral surface of the half member 2 is provided on the peripheral edge portion on the axial end face side of the narrow groove 3; Is equal to or less than 0 mm and equal to or less than the sum of the axial width W2 of the narrow grooves 3 from the axial width W1 of the half member 2.
With such a configuration, by providing the narrow groove 3 that does not prevent the generation of the oil film pressure, it is possible to obtain the friction reduction effect while reducing the sliding area, and to suppress the total amount of oil outflow. be able to. Further, by providing the step 4 at the peripheral edge of the narrow groove 3, it is possible to adjust so as to increase the amount of oil suctioned back.

The ratio of the sum of the axial width W3 of the step 4 to the axial width W1 of the half member 2 is 0% or more and 70% or less.
By configuring in this manner, it is possible to more effectively obtain the leakage oil amount reduction effect and the friction reduction effect.

DESCRIPTION OF SYMBOLS 1 slide bearing 2 half member 2a rotation direction downstream mating surface 2b rotation direction upstream mating surface 3 fine groove 3a rotation direction downstream end 3b rotation direction upstream end 4 stepped portion 4a rotation direction downstream end 4b rotation Upstream end 11 crankshaft

Claims (2)

A slide bearing in which half members obtained by dividing a cylinder into two in parallel to the axial direction are disposed at the top and bottom,
The position of the mating surface of the end face on the lower side of the upper half of the half in the direction of rotation of the shaft held by the slide bearing and the end face on the upper side in the direction of rotation of the lower half of the half is 0 In the case where a bearing angle is defined as a rotation angle from the 0 ° position to the opposite direction to the rotation direction of the shaft,
Said half member of the lower, from a position before the SL bearing angle 180 °, the range only to the position of the bearing angle is greater than 180 ° 270 ° or less, the circumferential and longitudinal direction, in the axial direction Provide two parallel narrow grooves,
A step which protrudes inward in the radial direction of the half member from the bottom of the narrow groove and is recessed outward in the radial direction of the inner circumferential surface of the half member at the peripheral edge on the axial end face side of the narrow groove. Set up the
The sum of the axial widths of the stepped portions is greater than 0 mm and equal to or less than the length obtained by subtracting the sum of the axial widths of the narrow grooves from the axial width of the half member. Sliding bearings. The slip according to claim 1, wherein the ratio of the sum of the axial width of the step portion to the axial width of the half member is greater than 0% and not more than 70%. bearing.

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