JP5043798B2 - Slide bearing and bearing device - Google Patents

Description

  The present invention combines a pair of halved bearings so as to support a crankshaft of an internal combustion engine to form a cylindrical shape, and a circumferential oil groove along the circumferential direction is formed on the inner peripheral surface of one of the halved bearings Of the split type bearing housing, and a combination surface where the slide bearing abuts a pair of split type bearing housings at both ends in the circumferential direction of the half bearing and the split type bearing housing. The present invention relates to a plain bearing device incorporated so as to coincide with the combined contact surface.

  2. Description of the Related Art Conventionally, a crankshaft plain bearing for an internal combustion engine uses a cylindrical bearing that is a combination of a pair of halved bearings. A circumferential oil groove is formed at the center of the inner peripheral surface of at least one of the pair of half bearings, so that oil is supplied to the sliding surface of the slide bearing through the circumferential oil groove. It was done. Moreover, the combination surface which contact | abuts in the circumferential direction both ends of a pair of half bearing is integrated so that it may correspond with the position of the combination contact surface of a split-type bearing housing (for example, patent document 1).

  In addition, in order to prevent foreign matter mixed in the lubricating oil supplied to the slide bearing from entering the sliding surface of the slide bearing, the bearing inner circumferential surface is communicated with the circumferential oil groove on the bearing inner circumferential surface. There has been proposed a plain bearing in which a relief portion is formed at a circumferential end, and a clearance between the relief portion and the crankshaft is a foreign matter discharge path (for example, Patent Document 2).

In the technique disclosed in Patent Document 2, as shown in FIGS. 4A and 4B, the supply of lubricating oil to the crankshaft slide bearing 21 of the internal combustion engine is performed first. Is supplied into a circumferential oil groove 24 formed on the inner peripheral surface through a supply hole 22 a formed in the upper half-shaped bearing 22, and the lubricating oil is slid on the sliding surface of the crankshaft slide bearing 21. And a sliding surface of a crankpin slide bearing (not shown). In this case, it is known that in the initial operation of the internal combustion engine, foreign matter remaining in the lubricating oil passage is often mixed with the lubricating oil supplied to the circumferential oil groove 24 of the upper half-shaped bearing 22. ing. This foreign matter is metal processing scraps during cutting of the lubricating oil passage, casting sand during casting, and the like, accompanying the flow of lubricating oil due to the rotation of the crankshaft 20, and the inside of the circumferential oil groove 24 in the crankshaft 20. Although it flows to the front side in the relative rotational direction, when it reaches the vicinity of the combined surface 25 of the half-shaped bearings 22, 23, the circumferential end surface of the lower half-shaped bearing 23 that does not form the circumferential oil groove 24 becomes a barrier. It floats to the inner peripheral surface side together with the lubricating oil (see FIG. 5A). Therefore, in the conventional crankshaft plain bearing 21, by forming a clearance 26 such as a crush relief or chamfering at the circumferential end of the inner peripheral surfaces of the half-shaped bearings 22 and 23, a half split from the clearance 26 is achieved. Foreign matter was discharged together with the lubricating oil to the end portions of the shape bearings 22 and 23 in the width direction.
JP-A-8-277831 JP 2005-69283 A

  By the way, in recent internal combustion engines, due to the higher rotation of the crankshaft, the inertial force that tries to go straight in the circumferential direction of foreign matters having a specific gravity greater than that of the lubricating oil is increasing. FIG. 5B shows an enlarged view for explaining the discharge mechanism of the foreign matter slide bearing 21 having such a large specific gravity. When the crankshaft 20 is rotated at a high speed, as shown by an arrow A in FIG. 5B, the foreign matter rolling on the bottom surface of the circumferential oil groove 24 in the upper half-shaped bearing 22 is caused by the circumferential oil groove. Even if it reaches the end of 24, it is not discharged from the gap 26 formed in the circumferential end, and is mixed into the sliding surface of the lower half bearing 23 on the side where the circumferential oil groove 24 is not formed. It was easy to do. Further, as shown by an arrow B in FIG. 5B, the foreign matter that has reached the end of the circumferential oil groove 24 due to the flow of the lubricating oil in the circumferential direction due to the rotation of the crankshaft 20 causes crush relief, chamfering, etc. Even if it entered the gap 26 formed by the above, many were pushed out of the gap 26 again and mixed into the sliding surface of the lower half bearing 23. That is, as shown by an arrow C in FIG. 5B, even if the foreign matter rolling on the groove bottom surface of the circumferential oil groove 24 reaches the end of the circumferential oil groove 24, all the foreign matter is half The split bearings 22 and 23 are not discharged at the end in the width direction, and are often mixed into the sliding surface (inner peripheral surface) of the lower half bearing 23 where the circumferential oil groove 24 is not formed.

  The present invention has been made in view of the circumstances described above, and the object of the present invention is to effectively discharge the foreign matter in order to prevent the foreign matter from entering the sliding surface of the slide bearing. It is an object of the present invention to provide a plain bearing or bearing device that can be used.

  In order to achieve the above object, in the invention according to claim 1, a pair of half bearings are combined so as to support a crankshaft of an internal combustion engine to form a cylindrical shape. In the sliding bearing formed so that circumferential oil grooves along the circumferential direction are opened at both circumferential end surfaces on the circumferential surface, out of the combination surfaces abutting at both circumferential ends of the pair of halved bearings The axial groove along the axial direction orthogonal to the circumferential direction is on the combination surface corresponding to the front side in the relative rotational direction of the crankshaft in the half bearing having at least the circumferential oil groove formed therein. Without opening to the inner peripheral surface side of the half-shaped bearing, it opens to at least one side of the end surface in the width direction of the half-shaped bearing and communicates with the groove bottom surface of the circumferential end of the circumferential oil groove. To be formed into And butterflies.

  In the invention according to claim 2, a pair of half bearings are combined to support the crankshaft of the internal combustion engine to form a cylindrical shape, and the inner circumferential surface of one of the half bearings is along the circumferential direction. In the slide bearing formed so that the circumferential oil groove is opened at both circumferential end faces, at least the circumferential oil groove is formed among the combined surfaces that contact at both circumferential ends of the pair of half bearings. A radial groove along a radial direction of the half-shaped bearing is a groove at a circumferential end of the circumferential oil groove on a combined surface corresponding to the front side in the relative rotational direction of the crankshaft in the half-shaped bearing formed. An axial groove is formed along the axial direction orthogonal to the circumferential direction, and the axial groove opens to the inner peripheral surface side of the half bearing. The width of the half bearing While open on at least one side of the end face, characterized in that it is formed so as to communicate with the radial grooves.

  In the invention according to claim 3, a pair of half bearings are combined so as to support the crankshaft of the internal combustion engine to form a cylindrical shape, and the inner circumferential surface of one of the half bearings is along the circumferential direction. A combined bearing in which a slide bearing formed so that a circumferential oil groove opens to both end faces in the circumferential direction is in contact with a pair of split bearing housings at both circumferential ends of the half bearing, and the split bearing housing In the sliding bearing device incorporated so that the combination contact surface of the pair of bearings coincides, the crankshaft in the half-shaped bearing in which at least the circumferential oil groove is formed among the combination surfaces of the pair of half-shaped bearings A radial groove along the radial direction of the half-shaped bearing opens on the outer circumferential surface of the half-shaped bearing and a circumferential direction of the circumferential oil groove on the combined surface corresponding to the front side in the relative rotational direction of edge Of the combined contact surfaces of the pair of split bearing housings, the inner surface of the combined contact surface corresponding to the side on which the radial groove is formed has a circumferential direction. An axial groove along an axial direction perpendicular to the opening is formed on at least one side of the end surface in the width direction of the split type bearing housing and communicated with the radial groove.

  In the invention which concerns on Claim 1, the relative rotation direction of the said crankshaft in the half-shaped bearing in which the said circumferential direction oil groove was formed at least among the combined surfaces contacted in the circumferential direction both ends of a pair of half-shaped bearing An axial groove that communicates with the groove bottom surface of the circumferential end of the circumferential oil groove is formed on the combination surface corresponding to the front side of the groove. For this reason, the foreign matter that has reached the circumferential end corresponding to the front side in the relative rotational direction of the crankshaft while rolling on the groove bottom surface of the circumferential oil groove enters the axial groove communicating with the groove bottom surface of the circumferential end portion. It is easy to enter, and foreign matter that has entered the axial groove can be discharged to the end surface in the width direction of the slide bearing. In addition, the axial groove is opened on at least one side of the end surface in the width direction of the half bearing, so that it does not open on the inner peripheral surface side of the slide bearing. Without being affected at all by the circumferential flow of the lubricating oil between the surfaces of the shaft, all foreign matter entering the axial groove can be smoothly discharged to the end surface side in the width direction of the slide bearing.

  Moreover, in the invention which concerns on Claim 2, it is the combination surface which hits the front side of the relative rotation direction of a crankshaft in the half-shaped bearing in which the circumferential direction oil groove was formed among the combination surfaces of a pair of half-shaped bearing. A radial groove communicating with the groove bottom surface at the circumferential end of the circumferential oil groove is formed. For this reason, the foreign matter that has reached the circumferential end corresponding to the front side in the relative rotation direction of the crankshaft while rolling on the groove bottom surface of the circumferential oil groove becomes a radial groove that corresponds to the centrifugal force acting direction due to the rotation of the crankshaft. It is easy to enter, and foreign matter that has entered the radial groove can be discharged to the end surface in the width direction of the slide bearing through the axial groove communicating with the radial groove. In addition, the axial groove is opened on at least one side of the end surface in the width direction of the half-shaped bearing and is not opened on the inner peripheral surface side of the slide bearing. Without being affected at all by the circumferential flow of the lubricating oil between the surfaces of the crankshaft, all foreign matter entering the axial groove can be smoothly discharged to the end surface in the width direction of the slide bearing.

  Moreover, in the invention which concerns on Claim 3, it is the combination surface which hits the front side of the relative rotation direction of a crankshaft in the half-shaped bearing in which the circumferential direction oil groove was formed among the combination surfaces of a pair of half-shaped bearing. A radial groove communicating with the groove bottom surface at the circumferential end of the circumferential oil groove is formed. For this reason, the foreign matter that has reached the circumferential end corresponding to the front side in the relative rotation direction of the crankshaft while rolling on the groove bottom surface of the circumferential oil groove becomes a radial groove that corresponds to the centrifugal force acting direction due to the rotation of the crankshaft. It is easy to enter, and foreign matter that has entered the radial groove can be discharged to the end surface in the width direction of the split bearing housing through the axial groove of the split bearing housing that communicates with the radial groove. In addition, the axial groove is formed on the inner peripheral surface side of the combination contact surface of the pair of split bearing housings, so that it does not open on the inner peripheral surface side of the slide bearing. Smoothly remove all foreign matter in the axial groove to the end face in the width direction of the split bearing housing without being affected by the circumferential flow of lubricant between the sliding surface and the surface of the crankshaft. Can be discharged.

  Hereinafter, embodiments of the present invention will be described with reference to FIGS. 1 to 3. FIG. 1 and FIG. 2 are a side view (A) of a plain bearing 1 comprising two upper half bearings 2 and a lower half bearing 3 that support the crankshaft 10, and the upper half bearing 2 and the lower half. FIG. 3B is a plan view (B) of the split bearing 3, and FIG. 3 shows that the slide bearing 1 including the two upper half bearings 2 and the lower half bearing 3 supporting the crankshaft 10 is formed in the split bearing housing 8. FIG. 4 is a side view (A) of the incorporated plain bearing device, and a plan view (B) of the upper bearing housing 12 and the lower bearing housing 13 of the split bearing housing 11 in which the upper and lower half bearings 3 and 4 are incorporated. . The above-described drawings are schematic views of the sliding bearing 1 and the split bearing housing 8 according to the embodiment, and each part is exaggerated or omitted for easy understanding of the configuration, structure, and the like.

  First, a first embodiment corresponding to the invention according to claim 1 will be described with reference to FIG. As shown in FIG. 1 (A), a plain bearing 1 that rotatably supports a crankshaft 10 of an internal combustion engine has a pair of half-shaped bearings 2 and 3 formed in a half-shape at both ends in the circumferential direction. A combination surface 5 in contact with each other is formed so as to form a cylindrical shape by combining two upper and lower surfaces. In order to satisfy the bearing characteristics of the half-shaped bearings 2 and 3 such as non-seizure, the inner peripheral surfaces 2a and 3a of the half-shaped bearings 2 and 3 are made of, for example, a copper alloy, an aluminum alloy, A sliding material such as a base alloy is lined, and an overlay such as a summary alloy or a synthetic resin is applied as necessary.

  Further, as shown in FIG. 1 (B), the half-shaped bearings 2 and 3 and the half-shaped bearings 2 and 3 are arranged at the center in the width direction of the inner peripheral surface 2a of the upper half-shaped bearing 2 among the half-shaped bearings 2 and 3. A circumferential oil groove 4 for supplying lubricating oil to the crankshaft 10 supported by the split bearings 2 and 3 is formed along the entire circumferential direction. The circumferential oil groove 4 is formed with a depth of about 0.8 mm in the case where the thickness of the half bearings 2 and 3 is in the range of 1.5 to 1.8 mm, and both end portions thereof are The upper half bearing 2 is formed so as to open at the circumferential end surface 2b. The circumferential oil groove 4 is formed with a supply hole 4 a for receiving oil supply from the outside so as to penetrate in the radial direction of the upper half-shaped bearing 2.

  By the way, in the combination surface 5 which is a contact surface of the circumferential end surface 2b of the upper half-shaped bearing 2 and the circumferential end surface 3b of the lower half-shaped bearing 3 constituting the slide bearing 1 in this embodiment, FIG. As shown in (A) and (B), an axial groove 6 for discharging foreign matter together with the lubricating oil is formed along the axial direction perpendicular to the circumferential direction and the radial direction of the slide bearing 1. Has been. The axial groove 6 is formed by moving the upper axial groove 6a formed on the circumferential end surface 2b of the upper half bearing 2 and the lower axial groove 6b formed on the circumferential end surface 3b of the lower half bearing 3 up and down. The two are combined to form one axial groove 6 with a certain depth, and both ends thereof are formed to open at the width direction end faces 2c and 3c of the half-shaped bearings 2 and 3. ing. The axial groove 6 is formed so as to communicate with the end 4 b of the groove bottom surface of the circumferential oil groove 4.

  The sliding bearing 1 configured as described above has an axial groove 6 formed in the combined surface 5 of the upper half-shaped bearing 2 and the lower half-shaped bearing 3, so The foreign matter that reaches the circumferential end corresponding to the front side in the relative rotation direction of the crankshaft 10 while rolling on the groove bottom surface of the directional oil groove 4 enters the axial groove 6 that communicates with the groove bottom surface of the circumferential end portion. It is easy to smoothly discharge the foreign matter that has entered the axial groove 6 to the side faces 2c and 3c in the width direction of the half bearings 2 and 3.

  Further, the axial groove 6 is not opened on the inner peripheral surfaces 2a and 3a side of the half-shaped bearings 2 and 3 by opening in the width direction end faces 2c and 3c of the half-shaped bearings 2 and 3, Without being affected at all by the circumferential flow of the lubricating oil between the sliding surface of the sliding bearing 1 and the surface of the crankshaft 10 due to the rotation of the shaft 10, all the foreign matter that has entered the axial groove 6 is removed by half. The split-shaped bearings 2 and 3 can be smoothly discharged to the width direction end faces 2c and 3c side. Thus, in the sliding bearing 1 according to the present embodiment, the foreign matter existing inside the sliding bearing 1 is not caught on the inner peripheral surface 2a side of the lower half-shaped bearing 3, and the sliding surface of the sliding bearing 1 is obtained. It is possible to prevent foreign matters from being mixed into the glass.

  The axial groove 6 and the like formed in the slide bearing 1 according to the first embodiment have been described above. Next, in the embodiment corresponding to the invention according to claim 2, the axial groove is provided in the slide bearing 1. A second embodiment in which a radial groove 7 is formed together with 6 will be described with reference to FIG. In addition, about the member which show | plays the same function as 1st Embodiment, the code | symbol same as 1st Embodiment is attached | subjected.

  First, in the circumferential end surface 2b of the upper half-shaped bearing 2 constituting the sliding bearing 1 according to the second embodiment, as shown in FIG. Are formed along the radial direction of the slide bearing 1. The radial groove 7 is notched at a certain depth, and one end thereof communicates with the end 4b of the groove bottom surface of the circumferential oil groove 4, and the other end thereof is an axial groove described later. 6 is formed so as to communicate with 6.

  Further, the outer peripheral surface 2d of the combination surface 5 which is a contact surface between the circumferential end surface 2b of the upper half-shaped bearing 2 and the circumferential end surface 3b of the lower half-shaped bearing 3 constituting the plain bearing 1 according to the second embodiment. , 3d side, as shown in FIGS. 2 (A) and 2 (B), foreign matter is externally introduced together with the lubricating oil via the radial groove 7 formed in the circumferential end surface 2b of the upper half bearing 2. An axial groove 6 is formed along the axial direction perpendicular to the circumferential direction and the radial direction of the slide bearing 1. The axial groove 6 is formed on the outer circumferential surface 2d side of the circumferential end surface 2b of the upper half bearing 2 and on the outer circumferential surface 3d side of the circumferential end surface 3b of the lower half bearing 3. The formed lower axial grooves 6b are combined with two upper and lower parts to be cut out at a fixed depth so as to form one axial groove 6, and both end portions thereof are end faces in the width direction of the half-shaped bearings 2 and 3. It is formed so as to open at 2c and 3c. The axial groove 6 is formed so as to communicate with the radial groove 7 formed on the circumferential end surface 2 b of the upper half bearing 2.

  In the slide bearing 1 according to the second embodiment configured as described above, since the radial groove 7 is formed in the circumferential end surface 2b of the upper half-shaped bearing 2, the circumferential direction in the upper half-shaped bearing 2 is the same. The foreign matter that has reached the circumferential end corresponding to the front side in the relative rotational direction of the crankshaft 10 while rolling on the bottom surface of the oil groove 4 enters the radial groove 7 that corresponds to the direction of the centrifugal force due to the rotation of the crankshaft 10. It is easy and the foreign matter that has entered the radial groove 7 can be smoothly discharged to the side faces 2c and 3c in the width direction of the half bearings 2 and 3 through the axial groove 6 communicating with the radial groove 7. .

  Further, the axial groove 6 is not opened on the inner peripheral surfaces 2a and 3a side of the half-shaped bearings 2 and 3 by opening in the width direction end faces 2c and 3c of the half-shaped bearings 2 and 3, Without being affected at all by the circumferential flow of the lubricating oil between the sliding surface of the sliding bearing 1 and the surface of the crankshaft 10 due to the rotation of the shaft 10, all the foreign matter that has entered the axial groove 6 is removed by half. The split-shaped bearings 2 and 3 can be smoothly discharged to the width direction end faces 2c and 3c side. As described above, in the sliding bearing 1 according to the second embodiment, the foreign matter existing inside the sliding bearing 1 is not caught on the inner peripheral surface 2a side of the lower half-shaped bearing 3, and the sliding of the sliding bearing 1 is prevented. It is possible to prevent foreign matters from entering the moving surface.

  In the first embodiment and the second embodiment described above, the case where the axial groove 6 is formed on the slide bearing 1 side has been described. Next, an embodiment corresponding to the invention according to claim 3 is described. A third embodiment in which the axial groove 6 is formed on the split bearing housing 11 side will be described with reference to FIG. In addition, about the member which show | plays the same function as 1st Embodiment and 2nd Embodiment, the same code | symbol as these embodiments is attached | subjected.

  First, in the circumferential end surface 2b of the upper half-shaped bearing 2 constituting the plain bearing 1 according to the third embodiment, as shown in FIG. Are formed along the radial direction of the slide bearing 1. The radial groove 7 is notched at a certain depth, and one end portion thereof communicates with the end portion 4 b of the groove bottom surface of the circumferential oil groove 4, and the other end portion thereof halves the bearing 2. The outer peripheral surface 2d is formed so as to open.

  As shown in FIG. 3 (A), the split bearing housing 11 into which the slide bearing 1 is incorporated is a combination of the two upper and lower bearing housings 12 and 13 and the combined surface 5 of the half bearings 2 and 3 and the bearing housing. The combination contact surfaces 14 and 13 are formed so as to coincide with each other. Further, on the inner peripheral surfaces 12 a and 13 a side of the combined contact surface 14 of the upper bearing housing 12 and the lower bearing housing 13, as shown in FIGS. An axial groove 6 is formed along the width direction of the split bearing housing 11 for discharging foreign matter together with the lubricating oil through a radial groove 7 formed in the direction end face 2b. The axial groove 6 is formed on the inner circumferential surface 13 a side of the upper axial groove 6 a formed on the inner circumferential surface 12 a side of the circumferential end surface 12 b of the upper bearing housing 12 a and the circumferential end surface 13 b of the lower bearing housing 13. In addition, the lower axial groove 6b is combined with two upper and lower parts to be cut out at a fixed depth so as to form one axial groove 6, and both end portions thereof are width direction end faces 12c and 13c of the bearing housings 12 and 13, respectively. It is formed to open. The axial groove 6 is formed so as to communicate with the radial groove 7 formed on the circumferential end surface 2b of the upper half-shaped bearing 2 when the slide bearing 1 is mounted.

  Since the slide bearing 1 and the split bearing housing 11 according to the third embodiment configured as described above are formed with the radial grooves 7 on the circumferential end surface 2b of the upper half-shaped bearing 2, the upper half The foreign matter that has reached the circumferential end corresponding to the front side in the relative rotational direction of the crankshaft 10 while rolling on the bottom surface of the circumferential oil groove 4 in the shape bearing 2 corresponds to the acting direction of the centrifugal force due to the rotation of the crankshaft 10. It is easy to enter the radial groove 7, and foreign matter that has entered the radial groove 7 is smoothly discharged to the width direction end faces 12 c and 13 c side through the axial grooves 6 of the bearing housings 12 and 13 communicating with the radial groove 7. can do.

  Further, the axial groove 6 is formed on the inner peripheral surfaces 12a and 13a side of the combined contact surface 14 of the bearing housings 12 and 13 so that it is formed on the inner peripheral surfaces 2a and 3a side of the half-shaped bearings 2 and 3. Since it is not opened, it is not affected by the flow of the lubricating oil in the circumferential direction between the sliding surface of the slide bearing 1 and the surface of the crankshaft 10 due to the rotation of the crankshaft 10 and enters the axial groove 6. All the foreign matters can be smoothly discharged to the width direction end faces 12c, 13c side of the bearing housings 12, 13. Thus, in the slide bearing 1 and the split bearing housing 11 according to the third embodiment, the foreign matter existing inside the slide bearing 1 is not caught on the inner peripheral surface 2 a side of the lower half-shaped bearing 3. It is possible to prevent foreign matters from entering the sliding surface of the slide bearing 1.

  In all the embodiments described above, the axial grooves 6 and the radial grooves 7 are combined surfaces 5 on both sides in the circumferential direction of the upper half-shaped bearing 2 and the lower half-shaped bearing 3 constituting the slide bearing 1. However, since the foreign matter rolling in the circumferential oil groove 24 flows to the front side in the relative rotation direction of the crankshaft 20, the upper half-shaped bearing 2 that forms the circumferential oil groove 4 is used. You may form only in the combination surface 5 used as the front side of the relative rotation direction of the crankshaft 10. FIG. In the third embodiment, the axial grooves 6 are formed on the combined surfaces 14 on both sides of the upper bearing housing 12 and the lower bearing housing 13 constituting the split bearing housing 11. May be formed only on the combination surface 14 of the split bearing housing 11 which is the front side in the relative rotational direction of the crankshaft 10 with respect to the upper half-shaped bearing 2 that forms the same.

  Further, in all the embodiments, the axial groove 6 is opened at both end surfaces of the width direction end surfaces 2c, 3c of the half-shaped bearings 2, 3 and the width direction end surfaces 12c, 13c of the bearing housings 12, 13. Although formed, it may be formed so as to open only at one end face. The axial groove 6 and the radial groove 7 may be formed on both circumferential end faces 2c and 3c of the pair of half bearings 2 and 3 that form the combination surface 5, and either one of the half grooves You may form only in the circumferential direction end surface (For example, the circumferential direction end surface 2c of the upper half-shaped bearing 2) of a shape bearing. In the third embodiment, the axial grooves 6 are formed on the circumferential end faces 12c and 13c on both sides of the upper bearing housing 12 and the lower bearing housing 13 constituting the split bearing housing 11, but either You may form only in the circumferential direction end surface (For example, circumferential direction end surface 12c of the upper bearing housing 12) of one bearing housing. Moreover, the cross-sectional shape of the axial direction groove | channel 6 and the radial direction groove | channel 7 is not restrict | limited as long as the foreign material in lubricating oil can be discharged | emitted.

Further, the larger the cross-sectional area of the axial groove 6 and the radial groove 7, the higher the effect of discharging foreign matters in the lubricating oil. However, if the cross-sectional area is excessively increased, the amount of leakage of the lubricating oil becomes excessive. Taking a groove with a V-shaped cross section as an example, the depth is 0.2 to 1 mm, the width is 0.4 to ² mm, and the cross-sectional area is preferably 0.04 to ¹ mm ² . Further, when the groove is formed in another cross-sectional shape, the cross-sectional area within this range is preferable.

  Further, the depth, width dimension and cross-sectional shape of the circumferential oil groove 4 are determined by the specifications of the internal combustion engine and are not particularly limited in the present application. Moreover, the circumferential cross-sectional shape of the circumferential oil groove 4 is not limited to the single arc shape shown in the embodiment, and may be a shape formed by multiple arcs. Further, the depth and width of the circumferential oil groove 4 can be formed so as to change in the circumferential direction.

  Furthermore, in the sliding bearing 1 of the present application, the thickness of the half-shaped bearings 2 and 3 may be changed from the center portion to the end portion in the bearing circumferential direction, as in the conventional sliding bearing. Further, the inner peripheral surfaces 2a. A crush relief, chamfering, or the like may be formed at the circumferential end on the 3a side.

The side view (A) of the slide bearing which consists of two upper half bearings and a lower half bearing which support the crankshaft which concerns on 1st Embodiment, and the top view of an upper half bearing and a lower half bearing (B). FIG. 3 is a view corresponding to FIG. 1 according to a second embodiment. A side view (A) of a plain bearing device in which a plain bearing comprising two upper half bearings and a lower half bearing for supporting a crankshaft according to a third embodiment is incorporated in a split type bearing housing; It is a top view (B) of an upper bearing housing and a lower bearing housing in which a split bearing is incorporated. It is a figure equivalent to FIG. 1 which shows a prior art example. It is an enlarged view for demonstrating the discharge mechanism of the foreign material in the conventional slide bearing.

Explanation of symbols

DESCRIPTION OF SYMBOLS 1 Slide bearing 2 Upper half-shaped bearing 3 Lower half-shaped bearing 4 Circumferential oil groove 4a Supply hole 5 Combination surface 6 Axial groove 7 Radial groove 10 Crankshaft 11 Split type bearing housing 12 Upper bearing housing 13 Lower bearing housing 14 Combination contact surface

Claims (3)

A pair of half bearings are combined to support a crankshaft of an internal combustion engine to form a cylindrical shape, and circumferential oil grooves along the circumferential direction are formed on the inner circumferential surface of the one half bearing. In the plain bearing formed to open to the surface,
Of the combination surfaces that contact at both circumferential ends of the pair of half bearings, at least the combination surface corresponding to the front side in the relative rotational direction of the crankshaft in the half bearing in which the circumferential oil grooves are formed The axial groove along the axial direction orthogonal to the circumferential direction opens to at least one side of the end surface in the width direction of the half-shaped bearing without opening to the inner circumferential surface side of the half-shaped bearing. In addition, the slide bearing is formed so as to communicate with the groove bottom surface of the circumferential end of the circumferential oil groove. A pair of half bearings are combined to support a crankshaft of an internal combustion engine to form a cylindrical shape, and circumferential oil grooves along the circumferential direction are formed on the inner circumferential surface of the one half bearing. In the plain bearing formed to open to the surface,
Of the combination surfaces that contact at both circumferential ends of the pair of half bearings, at least the combination surface corresponding to the front side in the relative rotational direction of the crankshaft in the half bearing in which the circumferential oil grooves are formed A radial groove along the radial direction of the half bearing is formed so as to communicate with a groove bottom surface at a circumferential end of the circumferential oil groove, and along an axial direction orthogonal to the circumferential direction. Axial groove is formed,
The axial groove is formed so as to open to at least one side of the end surface in the width direction of the half-shaped bearing and to communicate with the radial groove without opening to the inner peripheral surface side of the half-shaped bearing. A plain bearing characterized by being made. A pair of half bearings are combined to support a crankshaft of an internal combustion engine to form a cylindrical shape, and circumferential oil grooves along the circumferential direction are formed on the inner circumferential surface of the one half bearing. In the plain bearing formed so as to open to the surface, a combination surface that abuts the pair of split bearing housings at both ends in the circumferential direction of the half-shaped bearing coincides with a combination contact surface of the split bearing housing In the slide bearing device incorporated as follows:
Among the combination surfaces of the pair of half bearings, the combination surface corresponding to the front side in the relative rotation direction of the crankshaft in at least the half bearing in which the circumferential oil groove is formed includes the half bearing. A radial groove along the radial direction is formed to open to the outer peripheral surface of the halved bearing and to communicate with the groove bottom surface of the circumferential end of the circumferential oil groove,
An axial direction along the axial direction perpendicular to the circumferential direction is provided on the inner peripheral surface side of the combined contact surface corresponding to the side where the radial groove is formed, of the combined contact surfaces of the pair of split bearing housings. A plain bearing device, wherein a groove is formed to open to at least one side of the end surface in the width direction of the split bearing housing and to communicate with the radial groove.

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