JP2018141485A - Slide bearing - Google Patents

Abstract

PROBLEM TO BE SOLVED: To prevent variation in assembly of a flange into a half-split bearing.SOLUTION: A half-split bearing member 11 has a trapezoidal concave part on an end surface in an axial direction, and a flange member 12 has a trapezoidal convex part, fitted into the concave part, on an inner peripheral surface side. When the flange member 12 is cooled, the convex part contracts, and then a width in a circumferential direction of the convex part is made narrower than a width of an opening part of the concave part. The flange member 12, whose convex part has contracted, is fitted into the normal-temperature concave part. When a temperature of the flange member 12 rises, the convex part expands, and under the normal temperature, a width on an axial center side of the convex part is made wider than the width of the opening part of the concave part, thereby preventing the convex part from falling from the inside of the concave part to the outside.SELECTED DRAWING: Figure 1

Description

  The present invention relates to a bearing having a flange.

  In an internal combustion engine, in order to rotatably support a crankshaft (main shaft), a sliding bearing is used in which a half bearing with a flange assembled is arranged up and down. In this sliding bearing, the half bearing receives a load in a direction perpendicular to the axial direction of the crankshaft, and the flange receives an axial load. As a method of assembling the flange on the half bearing, for example, as in the method disclosed in Patent Document 1, there is a method of fitting the convex portion of the flange into the concave portion of the half bearing and caulking the periphery of the concave portion. .

Japanese Patent Laid-Open No. 2015-200381

  In the method disclosed in Patent Document 1, the periphery of the concave portion is caulked after the plurality of convex portions are fitted into the plural concave portions at the time of manufacturing. However, the load and position at the time of caulking may vary. If variation occurs in the load or position when caulking in this way, the force for fixing the convex portion varies depending on the position, and the flange may be detached from the half bearing before the half bearing is assembled to the cylinder block. .

  An object of the present invention is to prevent variations in the assembly of a flange to a half bearing.

  The present invention provides a slide having a semi-cylindrical half bearing member having an inner peripheral surface that slides with a mating shaft, and a flange member assembled to at least one end of the half bearing member in the axial direction. The half bearing member has a plurality of concave portions recessed in the axial direction on the end surface in the axial direction, and the flange member has a convex portion at each of positions corresponding to the plurality of concave portions. The convex portion fits into the concave portion, the circumferential width of the concave portion gradually decreases toward the end surface side, and the circumferential width of the convex portion fitted into the concave portion gradually decreases toward the end surface side. The convex portion provides a plain bearing having a portion wider than the circumferential width of the end surface of the concave portion.

  In the present invention, the concave portion located at the end in the circumferential direction among the plurality of concave portions may have a deeper depth in the axial direction than the concave portion not located at the end in the circumferential direction.

  According to the present invention, it is possible to prevent variation in the assembly of the flange to the half bearing.

The figure which illustrated the bearing 10 which concerns on one Embodiment of this invention. The front view of the half bearing member 11. FIG. The top view of the half bearing member 11. FIG. The front view of the flange member 12. FIG. The top view of the flange member 12. FIG. The front view of the flange member 13. FIG. The top view of the flange member 13. FIG. The top view of the half bearing member 11 which concerns on a modification. The figure which showed an example of the convex part 122 which concerns on a modification.

[Embodiment]
FIG. 1 is a diagram illustrating a bearing 10 according to an embodiment of the present invention. The bearing 10 is an example of a sliding bearing that supports the crankshaft S in a cylinder block B (an example of a housing) of an automobile engine, for example. The crankshaft S is a cylindrical shaft and rotates relative to the bearing 10. The crankshaft S is an example of a counterpart shaft for the bearing 10.

  The bearing 10 includes a half bearing member 11, a flange member 12, and a flange member 13. The half bearing member 11 has a semi-cylindrical shape obtained by dividing the cylinder into two along the axial direction. The inner peripheral surface of the half bearing member 11 slides with the outer peripheral surface of the crankshaft S. The half bearing member 11 is a main bearing that receives a load perpendicular to the axial direction. The flange member 12 and the flange member 13 have a semicircular shape in which a ring shape is divided into two along the diameter. The flange member 12 and the flange member 13 are thrust bearings (thrust washers) that receive an axial load (thrust load) from the crankshaft S. In addition, the shape of the flange member 12 and the flange member 13 is not limited to a semicircular shape, and may be an arc shape whose circumferential length is shorter than the semicircular shape.

  The bearing 10 supports half of the outer periphery of the crankshaft S in the circumferential direction. That is, in order to support the crankshaft S over the entire circumference, two bearings 10 are used for each position where the bearings 10 are arranged in the cylinder block B. In the example of FIG. 1, two bearings are shown: a bearing 10 a that supports the upper half of the outer periphery of the crankshaft S and a bearing 10 b that supports the lower half of the outer periphery of the crankshaft S. The bearing 10a and the bearing 10b do not necessarily need to be used in pairs, and only one of them may be used. Moreover, when using two as a set, both the bearing 10a and the bearing 10b do not necessarily need to have a flange member, and only one of the bearings or both axial ends of the flanges are flanged. A member may be provided.

  Hereinafter, for convenience of explanation, a coordinate system is defined. In this coordinate system, the axial direction of the counterpart axis is the z direction, and the positions in the circumferential direction and radial direction of the axis are represented by a polar coordinate system (r, θ). θ represents a displacement angle from a reference plane (for example, a horizontal plane), and r represents a distance from the reference point.

  The half bearing member 11 has, for example, a multi-layer structure of a back metal, a lining layer, and an overlay layer from the outer peripheral surface side, which is a semi-cylindrical outer surface, toward the inner peripheral surface side that supports the crankshaft S. The backing metal is a layer that gives the half bearing member 11 mechanical strength. The back metal is made of steel, for example.

  The lining layer is a layer for improving characteristics as a bearing, for example, friction characteristics, seizure resistance, wear resistance, conformability, foreign material embedment property (foreign material robustness), and corrosion resistance. . The lining layer is formed of a bearing alloy. In order to prevent the lining layer from adhering to the shaft, the same material system as the shaft is avoided and a material system different from the shaft is used. For example, when the crankshaft S is made of steel, an alloy different from steel, such as an aluminum alloy, is used as the bearing alloy. In addition to an aluminum alloy, an alloy based on a metal other than aluminum, such as a copper alloy, may be used.

The overlay layer forms an inner peripheral surface that supports the crankshaft S, and is a layer for improving the characteristics of the lining layer such as the coefficient of friction, conformability, corrosion resistance, and foreign material embedding property (foreign material robustness). is there. The overlay layer includes, for example, at least a binder resin. As the binder resin, for example, a thermosetting resin is used. Specifically, the binder resin includes at least one of a polyamideimide (PAI) resin, a polyimide (PI) resin, a polyamide resin, a phenol resin, a polyacetal resin, a polyether catalyst ketone resin, and a polyphenylene sulfide resin. The overlay layer may further include a solid lubricant. Solid lubricant is added to improve the friction properties. The solid lubricant includes, for example, at least one of MoS ₂ , WS ₂ , polytetrafluoroethylene (PTFE), graphite, h-BN, and SB ₂ O ₃ . For example, MoS ₂ gives good lubricity. Further, PTFE has an effect of reducing the friction coefficient because of its low intermolecular cohesion. In addition, graphite improves wettability and improves initial conformability. The initial conformability is a property that improves the slidability when the sliding surface wears and becomes smooth when slidably contacting with the counterpart material after the start of sliding. When the slidability is improved by the expression of the initial conformability, the wear amount of the entire sliding layer is reduced. In the present embodiment, the half bearing member 11 includes an overlay layer. However, the half bearing member 11 may include a two-layer structure including a back metal and a lining layer without including an overlay layer. Further, the overlay layer may be provided on only one of the bearing 10a and the bearing 10b.

  The flange member 12 and the flange member 13 are formed of the same material as the half bearing member 11. The flange member 12 and the flange member 13 are manufactured separately from the half bearing member 11 and then assembled to the half bearing member 11. The flange member 12 and the flange member 13 may be formed of a material different from that of the half bearing member 11 or may be formed with a different thickness.

  FIG. 2 is a front view of the half bearing member 11, and FIG. 3 is a plan view of the half bearing member 11. 4 is a front view of the flange member 12, FIG. 5 is a plan view of the flange member 12, FIG. 6 is a front view of the flange member 13, and FIG. 7 is a plan view of the flange member 13.

  The half bearing member 11 has a mating surface 115 and a mating surface 116 that are in contact with other bearings 10. A concave portion 112a, a concave portion 112b, and a concave portion 112c are formed on the end surface 111 on the + z direction side of the half bearing member 11 in order to assemble the flange member 12. In addition, a concave portion 114a, a concave portion 114b, and a concave portion 114c are formed on the end surface 113 on the −z direction side of the half bearing member 11 in order to assemble the flange member 13. In addition, since the recessed part 112a, the recessed part 112b, and the recessed part 112c are respectively the same shapes and sizes, it is set as the recessed part 112 when it is not necessary to distinguish each in the following description. In addition, since the concave portion 114a, the concave portion 114b, and the concave portion 114c have the same shape and size, in the following description, the concave portion 114 is used when it is not necessary to distinguish each other.

  The recess 112 is a notch provided in the −z direction from the end surface 111. The circumferential width of the concave portion 112 is the width w1 at the end surface 111 portion (the opening portion of the concave portion 112: second portion), and the end portion (first portion) on the end surface 113 side (bottom side of the concave portion 112). ) Is the width w2. In the present embodiment, the width w1 <the width w2, and the circumferential width of the recess 112 is a tapered shape (a trapezoidal shape as viewed in the radial direction) in which the circumferential width gradually decreases from the end surface 113 side toward the end surface 111. ). The depth of the concave portion 112 in the axial direction is L1. The recess 112a and the recess 112c are provided at a predetermined interval in the circumferential direction from the recess 112b.

  The recess 114 is a notch provided in the + z direction from the end surface 113. The width of the recess 114c in the circumferential direction is the width w1 at the end surface 113 portion (the opening portion of the recess 114) and the width w2 at the end portion on the end surface 111 side (bottom side of the recess 114). That is, the circumferential width of the recess 114 is a tapered shape (trapezoidal shape as viewed in the radial direction) in which the circumferential width gradually decreases from the end surface 111 side toward the end surface 113. The depth of the concave portion 114 in the axial direction is L1. The recess 114a and the recess 114c are provided with a predetermined interval in the circumferential direction from the recess 114b.

  The flange member 12 has a mating surface 123 and a mating surface 124 that face the flange members of the other bearings 10. On the inner peripheral surface 121 on the radially inner side of the flange member 12, a convex portion 122 a, a convex portion 122 b, and a convex portion 122 c are formed in order to assemble the flange member 12 to the half bearing member 11. An oil groove 126a and an oil groove 126b are formed on the thrust surface 125 that receives the thrust load in the flange member 12. Since the convex part 122a, the convex part 122b, and the convex part 122c are respectively the same shape and size, in the following description, when it is not necessary to distinguish each, it is set as the convex part 122.

  The convex portion 122 is formed to project from the inner peripheral surface 121 in the radial direction. The circumferential width of the convex portion 122 is the width w3 at the end portion on the thrust surface 125 side, and the width w4 at the end portion on the -z direction side. In the present embodiment, the width w3 <the width w4, and the circumferential width of the convex portion 122 is a tapered shape (as viewed in the radial direction) in which the circumferential width gradually decreases from the −z direction side toward the + z direction side. Trapezoidal shape). The oil groove 126 a and the oil groove 126 b are grooves that serve as an oil supply path that holds the lubricating oil and receives the lubricating oil supplied from the half bearing member 11.

  The flange member 13 has a mating surface 133 and a mating surface 134 that face the flange members of the other bearings 10. A convex portion 132 is formed on the inner peripheral surface 131 on the radially inner side of the flange member 13 in order to assemble the flange member 13 to the half bearing member 11. An oil groove 136a and an oil groove 136b are formed on a thrust surface 135 that receives a thrust load in the flange member 13. Since the convex part 132a, the convex part 132b, and the convex part 132c are the same shape and size, respectively, in the following description, when it is not necessary to distinguish each, it is set as the convex part 132.

  The convex portion 132 is formed to project from the inner peripheral surface 131 in the radial direction. The circumferential width of the protrusion 132 is the width w3 at the end portion on the thrust surface 135 side, and the width w4 at the end portion on the + z direction side. That is, the circumferential width of the convex portion 132 is a tapered shape (trapezoidal shape as viewed in the radial direction) in which the circumferential width gradually decreases from the + z direction side toward the −z direction side. The oil groove 136 a and the oil groove 136 b are grooves that serve as an oil supply path that holds the lubricating oil and receives the lubricating oil supplied from the half bearing member 11.

  The relationship between the widths of the recesses 112 and 114 and the widths of the protrusions 122 and 132 is such that the width w1> the width w3 and the width w2> the width w4 at room temperature. Further, at room temperature, the width w4> the width w1.

  Assembly of the flange member 12 and the flange member 13 to the half bearing member 11 is performed by cold fitting. Specifically, the flange member 12 and the flange member 13 are cooled with liquid nitrogen. By cooling with liquid nitrogen, the flange member 12 and the flange member 13 contract, and the convex portion 122 has a width w31 that is narrower than the width w3 at the end portion on the thrust surface 125 side. In the portion, the width w41 is narrower than the width w4. Also in the convex portion 132, the end portion on the thrust surface 135 side has a width w31 that is narrower than the width w3, and the end portion on the + z direction side has a width w41 that is narrower than the width w4.

  After the contraction, the width w41 <the width w1 and the circumferential width of the convex portion 122 is narrower than the width w1, and therefore, the −z direction from the + z direction side to the concave portion 112 of the half bearing member 11 at room temperature. The convex part 122 can be fitted to the side. Further, since the circumferential width of the convex portion 132 is also narrower than the width w1, the convex portion 132 can be fitted from the −z direction side to the + z direction side with respect to the concave portion 114 of the half bearing member 11 at room temperature. .

  After the convex portion 122 is fitted in the concave portion 112 and the convex portion 132 is fitted in the concave portion 114, when the temperature of the flange member 12 and the flange member 13 rises, the flange member 12 and the flange member 13 expand. When the temperature reaches normal temperature, the width of the convex portion 122 at the end on the thrust surface 125 side returns to the width w3, and the width at the end portion on the -z direction side becomes the width w4. Also in the convex portion 132, the width is the width w3 at the end portion on the thrust surface 135 side, and the width is the width w4 at the end portion on the + z direction side. Under normal temperature, the relationship between the width w4 and the width w1 is such that the width w4> the width w1. Therefore, the convex portion 122 is unlikely to come out from the inside of the concave portion 112, and the convex portion 132 goes out from the inside of the concave portion 114. The flange member 12 and the flange member 13 are integrated with the half bearing member 11.

  According to the bearing 10 according to the present embodiment, compared to the case where the flange is assembled to the half bearing by caulking, no load is applied to the recess 112 and the recess 114 during assembly. For this reason, there is no concave portion where the convex portion is easily removed, the flange member 12 and the flange member 13 are unlikely to be detached from the half bearing member 11, and variations in assembly of the flange member to the half bearing member are less likely to occur.

  The state in which the flange member 12 and the flange member 13 are integrated with the half bearing member 11 may be maintained at least until the assembly of the bearing 10 to the cylinder block B is completed. After the assembly, it is not always necessary to maintain the integrated state when the engine is driven. The convex portion 122 and the convex portion 132 may be detached from the half bearing member 11 in response to an axial load. In this case, the flange member 12 and the flange member 13 move according to the load when the engine is operating, and contact the cylinder block B to receive the load.

[Modification]
As mentioned above, although embodiment of this invention was described, this invention is not limited to embodiment mentioned above, It can implement with another various form. For example, the present invention may be implemented by modifying the above-described embodiment as follows. In addition, you may combine each of embodiment mentioned above and the following modifications.

  In the embodiment described above, the depth in the axial direction of the recess 112 and the recess 114 is the same depth, but is not limited to the configuration of the same depth. FIG. 8 is a plan view of a half bearing member 11 according to a modification. As shown in FIG. 8, regarding the recess 112a and the recess 112c, the depth in the axial direction may be set to L2 deeper than L1. Also, the depth in the axial direction of the recess 114a and the recess 114c may be set to L2 deeper than L1 in the axial direction. According to this modified example, compared with the configuration of the embodiment, when the bearing 10 is assembled to the cylinder block B, the movable range of the flange member 12 and the flange member 13 fitted to the half bearing member 11 is widened. This makes it easier to assemble.

  In the above description, the flange member 12 and the flange member 13 are assembled to the half bearing member 11 by cold fitting. However, the half bearing member 11 is heated and protruded into the concave portion 112 having a wide circumferential width. The flange member 12 may be assembled to the half bearing member 11 by fitting the flange 122 to the half bearing member 11 by fitting the portion 122 and fitting the convex portion 132 to the concave portion 114 having a wide circumferential width.

  The shape and number of the concave portions in the half bearing member 11 and the shape and number of the convex portions in the flange member 12 and the flange member 13 are not limited to those described in the embodiment, and may be other shapes and numbers. . Moreover, the position of a recessed part and a convex part does not need to be arrange | positioned at equal intervals.

  The flange member 12 and the flange member 13 may have a non-rotating convex portion on the outer peripheral surface for preventing relative rotation with respect to the cylinder block B. Further, the shape and number of the oil grooves 126 and the shape and number of the oil grooves 136 are not limited to those described in the embodiment, and may be other shapes and numbers.

  In the embodiment described above, the flange member 12 and the flange member 13 are assembled to the half bearing member 11, but only one of the flange member 12 or the flange member 13 is assembled to the half bearing member 11. It may be a configuration.

  In the embodiment described above, the convex portion 122 and the convex portion 132 have a trapezoidal shape when viewed in the radial direction, but the shape when viewed in the radial direction is not limited to the trapezoid. For example, a shape in which a part of the convex part 122 (the convex part 132) is notched into a trapezoidal shape, such as the convex part 222 shown in FIG. 9A, may be used, and as shown in FIG. Like the convex part 322, the shape which cut out a part of convex part 122 (convex part 132) into the semicircle may be sufficient. Moreover, as the convex part 422 shown in FIG.9 (c), it is good also as a structure which has a part wider than the width | variety w1 between the end on the + z direction side, and the end on the -z direction side. Moreover, the convex part should just be a structure with the width | variety of the circumferential direction wider than the + z direction side on the -z direction side, and is constant on the + z direction side like the convex part 522 shown in FIG.9 (d). And a portion having a constant width which is wider on the −z direction side than on the + z direction side.

  In the embodiment described above, two identical bearings 10 are used to support the mating shaft. However, the two bearings used here may have different inner peripheral surfaces (sliding surfaces), for example. Good. For example, an oil groove or an oil hole may be provided on one of the upper and lower sliding surfaces. Further, the use of the bearing 10 is not limited to the one that supports the crankshaft S.

  In the embodiment described above, the convex portion and the concave portion are similar in shape, but the present invention is not limited to the configuration in which the convex portion and the concave portion are similar in shape. For example, the structure which fits the convex part 522 with respect to the recessed part 112 may be sufficient.

DESCRIPTION OF SYMBOLS 10 ... Bearing 11 ... Half bearing member 111 ... End surface 112 ... Concave 113 ... End surface 114 ... Concave 115 ... Mating surface 116 ... Mating surface 12 ... Flange member 121 ... Inner peripheral surface 122 ... Convex part 123 ... Mating surface 124 ... Mating surface 125 ... Thrust surface 126a ... Oil groove 126b ... Oil groove 13 ... Flange member 131 ... Inner peripheral surface 132 ... Convex portion 133 ... Matching surface 134 ... Matching surface 135 ... Thrust surface 136a ... Oil groove 136b ... Oil groove 222 ... Convex portion 322 ... convex part 422 ... convex part

Claims (2)

A half-cylindrical half bearing member having an inner peripheral surface that slides with a counterpart shaft;
A flange member assembled to at least one end in the axial direction of the half bearing member;
A sliding bearing having
The half bearing member has a plurality of recesses recessed in the axial direction on the end surface in the axial direction,
The flange member has a convex portion at each of the positions corresponding to the plurality of concave portions,
The convex part fits into the concave part,
The concave portion has a first portion having a first width in the circumferential direction, and a second portion that is closer to the end face than the first portion and has a smaller width in the circumferential direction than the first portion,
The sliding part fitted into the concave part has a part whose circumferential width is wider than the second part on the center side in the axial direction from the second part. The sliding bearing according to claim 1, wherein a recess located at an end in the circumferential direction among the plurality of recesses has a greater depth in the axial direction than a recess not located at the end in the circumferential direction.

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