KR102231313B1 - Crosshead bearings and crossheads and furniture, crosshead internal combustion engines - Google Patents

Abstract

In a crosshead bearing, a crosshead, furniture, and a crosshead type internal combustion engine, the bearing body 71 forming a semi-cylindrical shape, the bearing surface 72 formed on the inner surface of the bearing body 71, and the bearing body 71 ), and an inclined groove 76 as an inclined portion whose depth increases from both ends in the axial direction toward the central portion on the inner surface of the bearing body 71 as a communication portion penetrating in the thickness direction of .

Description

Crosshead bearings and crossheads and furniture, crosshead internal combustion engines

The present invention relates to a crosshead bearing used in a crosshead type internal combustion engine constituting an internal combustion engine such as a diesel engine or a gas engine, a crosshead having a crosshead bearing, a furniture having a crosshead, and the furniture. It relates to a crosshead type internal combustion engine provided.

For example, as a main machine for propulsion of a ship, there is a crosshead internal combustion engine of a uniflow scavenging system of 2 strokes and 1 cycle. This crosshead type internal combustion engine is provided with a crosshead bearing device for converting a reciprocating motion of a piston into a rotational motion of a crankshaft. This crosshead bearing device is provided with a connecting rod and a bearing metal. The connecting rod has a lower end connected to the crank, a semicircular support surface is formed at the upper end, and the bearing metal has a semi-cylindrical shape and supports the outer peripheral surface of the crosshead pin to which the lower end of the piston rod is connected so that it can slide freely. The bearing surface is formed.

Further, the connecting rod has a circumferential oil groove formed on the support surface along the circumferential direction. In the bearing metal, a circumferential oil groove is formed along the circumferential direction on the bearing surface, and a plurality of axial oil grooves communicated with the circumferential oil groove are formed, and the circumferential oil groove of the support surface and the circumferential direction of the bearing surface. A plurality of communication holes for communicating the oil groove are formed. Therefore, the lubricating oil is supplied to the circumferential oil groove and the axial oil groove of the bearing surface from a supply flow path formed in the crosshead pin, and when the crosshead pin and the bearing metal (connecting rod) move relative to each other, the crosshead It spreads widely between the outer peripheral surface of the pin and the bearing surface to perform lubrication. As such a crosshead bearing, there exists what was described in following patent document 1, for example.

Japanese Patent Publication No. 4912046

In the above-described crosshead bearing, the rear side is supported by being in close contact with the supporting surface of the connecting rod, and the bearing surface on the front side is supported so that the outer circumferential surface of the crosshead pin can slide freely. Therefore, when the crosshead type internal combustion engine is operated, the bearing surface of the crosshead bearing receives a load from the outer peripheral surface of the crosshead pin. At this time, the oil film pressure in the axial direction of the crosshead pin generated on the bearing surface of the crosshead bearing is lowest at the end in the axial direction due to the deformation of the bearing surface, and moves from the end in the axial direction to the center. It is rising towards. Therefore, in the crosshead bearing, there is a possibility that the central portion in the axial direction at which the oil film pressure is maximized is damaged.

An object of the present invention is to provide a crosshead bearing, a crosshead, furniture, and a crosshead type internal combustion engine capable of satisfactorily supporting a crosshead pin by suppressing damage due to a bearing load by solving the above-described problems. It is done.

A crosshead bearing of the present invention for achieving the above object is a crosshead bearing supported by a support surface of a connecting rod so as to freely slide an outer circumferential surface of a crosshead pin, comprising: a bearing body having a semi-cylindrical shape; A bearing surface formed on an inner surface of the bearing body, a communication portion penetrating in the thickness direction of the bearing body, and an inclined portion increasing in depth toward the center from both ends in the axial direction on the inner surface of the bearing body. It is characterized by.

Therefore, by forming inclined portions that increase in depth from both ends in the axial direction toward the center on the inner surface of the bearing body, when the crosshead is operated, the bearing surface of the crosshead bearing receives surface pressure from the outer peripheral surface of the crosshead pin. The inclined portion can suppress an increase in local oil film pressure and a decrease in oil film thickness in the central portion in the axial direction. As a result, damage due to the bearing load can be suppressed and the crosshead pin can be satisfactorily supported.

In the crosshead bearing of the present invention, the inclined portion is characterized in that the depth increases from the outside in the width direction of the connecting rod toward the central portion in the axial direction of the bearing body.

Therefore, by increasing the depth of the inclined portion from the outer side in the width direction of the connecting rod toward the central portion in the axial direction of the bearing body, a sufficient area inclined portion can be secured, and the local oil film pressure at the central portion in the axial direction is reduced. It can effectively suppress the rise.

In the crosshead bearing of the present invention, the inclined portion is formed toward the central portion from a position shifted by a predetermined length toward the central portion from an end portion in the axial direction of the bearing body.

Therefore, the inclined portion is formed from a position shifted by a predetermined length from both ends of the bearing body in the axial direction toward the center, so that a bearing surface that always contacts the outer peripheral surface of the crosshead pin can be secured in a region of a predetermined length from the end of the bearing body. As a result, the crosshead pin can be stably supported.

In the crosshead bearing of the present invention, the inclined portion is characterized in that the bottom surface is a flat inclined plane.

Therefore, by making the inclined portion an inclined plane with a flat bottom surface, it is possible to facilitate workability and reduce processing cost.

In the crosshead bearing of the present invention, the inclined portion is characterized in that an inclined curved surface that is convex or concave toward the crosshead pin is formed on the bottom surface.

Therefore, by making the inclined portion a convex or concave inclined curved surface toward the crosshead pin side, an increase in oil film pressure at the edge periphery of the circumferential oil groove can be effectively suppressed.

In the crosshead bearing of the present invention, the inclined portion receives a load through an oil film when the bearing surface receives a maximum load from the crosshead pin.

Therefore, when the bearing surface receives the maximum load from the crosshead pin, the outer circumferential surface of the crosshead pin is subjected to the load through the oil film in the inclined plane or the inclined curved surface. While the increase in oil film pressure can be effectively suppressed, the crosshead pin can be stably supported.

In the crosshead bearing of the present invention, a circumferential oil groove is formed along the circumferential direction on the bearing surface at the center of the bearing body in the axial direction, and the inclined portion is formed from both ends of the bearing body in the axial direction. It is characterized in that the depth increases toward the circumferential oil groove.

Accordingly, when the bearing surface of the crosshead bearing receives surface pressure from the outer circumferential surface of the crosshead pin, it is possible to suppress an increase in local oil film pressure or decrease in oil film thickness at the edge periphery of the circumferential oil groove by the inclined portion.

In the crosshead bearing of the present invention, the communication portion is formed along a circumferential direction at a central portion in the axial direction of the bearing body, and the inclined portion has a depth from both ends of the bearing body in the axial direction toward the communication portion. It is characterized by being larger.

Accordingly, when the bearing surface of the crosshead bearing receives surface pressure from the outer circumferential surface of the crosshead pin, it is possible to suppress an increase in local oil film pressure or a decrease in oil film thickness at the edge periphery of the communication portion by the inclined portion.

In the crosshead bearing of the present invention, axial oil grooves along the axial direction of the crosshead pin are formed on the bearing surface at predetermined intervals in the circumferential direction, and the inclined portion is formed in the width direction of the plurality of axial oil grooves. It is characterized in that it is formed on both sides of the.

Therefore, by forming a plurality of axial oil grooves at predetermined intervals on the bearing surface, and forming inclined portions on both sides of the width direction of each axial oil groove, stable supply of lubricating oil is possible by the axial oil groove, and the axial oil By forming inclined portions on both sides of the groove in the width direction, it is possible to effectively suppress an increase in local oil film pressure at the edge periphery of the circumferential oil groove.

In addition, the crosshead of the present invention includes a crosshead pin, a bearing portion having a support surface curved to form a semicircular shape, and a support surface of the bearing portion so that the outer circumferential surface of the crosshead pin can slide freely. It is characterized in that it comprises the crosshead bearing.

Therefore, when the crosshead is operated, when the bearing surface of the crosshead bearing receives surface pressure from the outer circumferential surface of the crosshead pin, local increase in oil film pressure or decrease in oil film thickness at the center in the axial direction by the inclined portion is suppressed. can do. As a result, damage to the crosshead bearing caused by the bearing load can be suppressed, and the crosshead pin can be satisfactorily supported.

In addition, the furniture of the present invention includes a top plate disposed on a top, a bottom plate disposed on a bottom, a side plate disposed on a side and one end connected to the top plate, and a side plate to which a tartan portion is connected to the bottom plate, and the top plate. And a partition wall in which a plurality of spaces are partitioned by being connected to the bottom plate and the side plate, a guide plate fixed to each of the partition walls, and the crosshead supported so as to be freely movable on each of the guide plates. will be.

Therefore, when the crosshead is operated, when the bearing surface of the crosshead bearing receives surface pressure from the outer circumferential surface of the crosshead pin, local increase in oil film pressure or decrease in oil film thickness at the center in the axial direction by the inclined portion is suppressed. can do. As a result, damage to the crosshead bearing caused by the bearing load can be suppressed, and the crosshead pin can be satisfactorily supported.

In addition, the crosshead type internal combustion engine of the present invention penetrates the base plate, the furniture formed on the base, a cylinder jacket formed on the furniture, the base plate, the furniture, and the cylinder jacket. It is characterized in that it comprises a connecting member to connect.

Therefore, when the crosshead is operated, when the bearing surface of the crosshead bearing receives surface pressure from the outer circumferential surface of the crosshead pin, local increase in oil film pressure or decrease in oil film thickness at the center in the axial direction by the inclined portion is suppressed. can do. As a result, damage to the crosshead bearing caused by the bearing load can be suppressed, the crosshead pin can be satisfactorily supported, and the fuel economy and reliability can be improved.

According to the crosshead bearing, crosshead, furniture, and crosshead type internal combustion engine of the present invention, damage due to a bearing load can be suppressed, and the crosshead pin can be satisfactorily supported.

1 is a schematic configuration diagram showing a diesel engine according to a first embodiment.
2 is a front view showing the furniture of the first embodiment.
3 is a perspective view showing a crosshead of the first embodiment.
4 is a plan view showing a crosshead from which a crosshead pin is omitted.
5 is a VV cross-sectional view of FIG. 4.
6 is a cross-sectional view of VI-VI in FIG. 4.
7 is a perspective view showing a bearing metal.
8 is a cross-sectional view showing a main part of a crosshead.
9 is a cross-sectional view showing a detailed shape of a bearing metal.
10 is a cross-sectional view showing a detailed shape of a first modified example of a bearing metal.
11 is a plan view of a crosshead showing a second modified example of the bearing metal.
12 is a plan view of a crosshead showing a third modified example of the bearing metal.
Fig. 13 is a schematic diagram showing the oil film pressure and bearing surface shape when a maximum load is applied to the bearing metal.
14 is a plan view showing a crosshead according to a second embodiment.
15 is an XV-XV cross-sectional view of FIG. 14.
16 is a plan view showing a crosshead according to a third embodiment.
17 is a cross-sectional view taken along the line XVII-XVII in FIG. 16.
18 is a cross-sectional view showing a detailed shape of a first modified example of a bearing metal.
19 is a plan view of a crosshead showing a second modified example of the bearing metal.
Fig. 20 is a schematic diagram showing an oil film pressure and a bearing surface shape when a maximum load is applied to the bearing metal.

Hereinafter, preferred embodiments of the crosshead bearing, crosshead, furniture, and crosshead type internal combustion engine according to the present invention will be described in detail with reference to the accompanying drawings. In addition, the present invention is not limited by this embodiment, and when there are a plurality of embodiments, a combination of each embodiment is also included.

[First Embodiment]

1 is a schematic diagram showing a diesel engine according to a first embodiment.

In the first embodiment, as shown in Fig. 1, the diesel engine 10 is used as a cycle for propulsion of a ship, for example, and is a crosshead type internal combustion engine of a uniflow scavenging system of two strokes and one cycle. This diesel engine 10 is provided with the base plate 11 located below, the furniture 12 formed on the base 11, and the cylinder jacket 13 formed on the furniture 12. The base plate 11, the furniture 12, and the cylinder jacket 13 are integrally fastened and fixed by a plurality of tie bolts (connection members) 14 and nuts 15 extending in the vertical direction.

The cylinder liner 16 is disposed in the cylinder jacket 13, and the cylinder cover 17 is fixed at the upper part to partition the space, and the piston 18 is formed so that the piston 18 can freely reciprocate up and down in this space. . In addition, the cylinder cover 17 is provided with an exhaust valve 20, and the exhaust valve 20 can be opened and closed by a moving device 21. The exhaust valve 20 forms the combustion chamber 19 together with the cylinder liner 16, the cylinder cover 17, and the piston 18. The exhaust valve 20 opens and closes the combustion chamber 19 and the exhaust pipe 22.

Therefore, for the combustion chamber 19, a fuel supplied from a fuel injection pump (not shown, for example, low quality oil, natural gas, or a mixed fuel thereof), and for combustion compressed by a compressor (not shown) When a gas (for example, air, EGR gas, or a mixture thereof) is supplied, fuel and combustion gas are combusted in the combustion chamber 19. Then, the piston 18 reciprocates in the piston axial direction by the energy generated by this combustion. At this time, when the exhaust valve 20 is operated by the moving device 21 to open the combustion chamber 19, the exhaust gas generated by combustion is extruded into the exhaust pipe 22, while combustion from an unillustrated scavenging port. The solvent gas is introduced into the combustion chamber 19.

As for the piston 18, the upper end of the piston rod 23 is connected to the lower end. The base plate 11 constitutes a crankcase, and is supported so that the crankshaft 24 can rotate freely by a bearing 25. The crankshaft 24 is connected so that the lower end of the connecting rod 27 can freely rotate through the crank 26. The furniture 12 is arranged so that guide plates 28 formed along the piston axis direction form a pair at predetermined intervals in the width direction. The crosshead 29, which will be described later, is between the crosshead pin connected to the lower end of the piston rod 23, the bearing portion of the connecting rod 27 connected to the crankshaft 24, and the crosshead pin and the bearing portion. It is composed of a formed crosshead bearing (bearing metal), and a crosshead pin is connected to the bearing part so that it can rotate freely through the crosshead bearing. This crosshead 29 is disposed between a pair of guide plates 28 and is supported so as to move freely along the guide plates 28.

Therefore, when the piston 18 reciprocates along the piston axial direction, the piston rod 23 together with the piston 18 reciprocates along the piston axial direction, so that the crosshead 29 moves the guide plate 28 back and forth. It reciprocates along the direction of the piston axis along the way. Thereby, the crosshead pin of the crosshead 29 applies a rotational driving force to the connecting rod 27 via the crosshead bearing. By this rotational driving force, the crank 26 connected to the lower end of the connecting rod 27 cranks and rotates the crankshaft 24.

Here, the furniture 12 constituting the diesel engine 10 will be described in detail. Fig. 2 is a front view showing the furniture of the first embodiment, and Fig. 3 is a perspective view showing the crosshead of the first embodiment. In the following description, the circumferential direction C is the circumferential direction of the crosshead pin, the axial direction A is the axial center direction of the crosshead pin, and the radial direction R is the radial direction of the crosshead pin.

As shown in FIG. 2, the furniture 12 is composed of a top plate 31, a floor plate 32, a side plate 33, and a plurality of partition walls 34. The top plate 31 is disposed at the top and connected to the cylinder jacket 13 (see Fig. 1). The bottom plate 32 is disposed on the bottom and connected to the base plate 11 (see Fig. 1). The side plate 33 is disposed on the left and right side portions, and one end (lower end) in the piston axial direction is connected to the bottom plate 32, and the tartan portion (upper end) is connected to the top plate 31. The plurality of partition walls 34 are arranged in parallel at regular intervals along the crankshaft direction.

In this furniture 12, the space part 35 is formed by the top plate 31, the bottom plate 32, the side plate 33, and each partition wall 34. This space part 35 is a space part in which the crosshead 29 is supported by the guide plate 28 and is movable, and the crosshead 29 is accommodated in this space part 35 and reciprocates in the piston axial direction. You can move.

The partition wall 34 has a central plate 41, an intermediate plate 42, and a guide plate 28. The central plate 41 forms a central portion of the partition wall 34 in the width direction of the internal combustion engine. Each intermediate plate 42 forms both end portions of the partition wall 34 in the width direction of the internal combustion engine. The guide plate 28 is disposed between the central plate 41 and each intermediate plate 42 in the partition wall 34 and is connected by welding. The central plate 41 is a flat plate having a rectangular shape in which a cutout 41a is formed on one side, and is disposed so that the cutout 41a is located under the partition wall 34. In the center plate 41, both ends in the width direction of the internal combustion engine are connected to the guide plate 28 by welding.

2 and 3, the crosshead 29 includes a piston rod 23, a connecting rod 27, a pair of guide shoes 51, a crosshead pin 52, and a bearing metal. (Crosshead bearing) (53).

The connecting rod 27 is connected to the connecting rod main body 61, a lower bearing part 62 integrally formed at the upper end of the connecting rod main body 61, and a plurality of fastening bolts 63 on the upper part of the lower bearing part 62. It consists of an upper bearing part 64 which is integrally fastened by. In this case, the connecting rod main body 61 is a portion whose width and thickness are set to be the same dimension in the longitudinal direction. The piston rod 23 is constituted by a piston rod main body 65 and a connecting portion 66 (see Fig. 5) integrally formed at the lower end of the piston rod main body 65. A pair of guide shoes 51 has a rectangular shape, and is composed of a guide shoe body 67 and guide portions 68 formed on both sides of the guide shoe body 67, respectively, and the guide shoe body 67 Mounting holes 69 are formed in the. The crosshead pin 52 is integrally connected to the lower end of the piston rod 23 via a connecting portion 66. The bearing metal 53, as described later, has a semi-cylindrical shape, and lubricating oil is supplied to the inner and outer surfaces.

The bearing metal 53 is mounted on the inner surface of the lower bearing part 62 of the connecting rod 27, the crosshead pin 52 is disposed inside, and the upper bearing part 64 is located on the upper part of the lower bearing part 62. ) Is fastened, so that the crosshead pin 52 can be freely rotated by the bearing metal 53. The pair of guide shoes 51 is fixed by fitting the end of the crosshead pin 52 to the mounting hole 69 on both sides of the piston rod 23 and the connecting rod 27.

Therefore, the crosshead pin 52 connected to the piston rod 23 and the bearing portions 62 and 64 formed on the upper end of the connecting rod 27 are connected so that they can rotate freely through the bearing metal 53 do. That is, when the piston 18 (see Fig. 1) reciprocates, the piston rod 23 integral with the piston 18 reciprocates along the moving direction, and at this time, a pair of guide shoes 51 is 1 It reciprocates along the pair of guide plates 28. The connecting rod 27 reciprocates along the same direction in conjunction with the piston rod 23, and rotates relatively reciprocally with respect to the piston rod 23 using the crosshead pin 52 as a support point. And the connecting rod 27 and the crank 26 (refer FIG. 1) crank movement, and the crankshaft 24 (refer FIG. 1) rotates.

Hereinafter, the crosshead 29 will be described in detail. Fig. 4 is a plan view showing a crosshead from which a crosshead pin is omitted, Fig. 5 is a V-V cross-sectional view of Fig. 4, Fig. 6 is a VI-VI cross-sectional view of Fig. 4, and Fig. 7 is a perspective view showing a bearing metal.

4 to 7, in the crosshead 29, the crosshead pin 52 connected to the piston rod 23 is attached to the lower bearing portion 62 and the upper bearing portion 64 of the connecting rod 27. It is connected so that it can rotate freely through the bearing metal 53. This bearing metal 53 is a bearing body 71, a bearing surface 72, a circumferential oil groove 73, an axial oil groove 74, a communication hole (communication part) 75, and , An inclined groove (inclined portion) 76 is provided.

The bearing body 71 has a semi-cylindrical shape, and the outer surface is supported by a support surface 62a having a semicircular shape formed on the lower bearing portion 62 of the connecting rod 27, and the inner surface of the crosshead pin 52 A bearing surface 72 is formed to support the outer circumferential surface so that it can freely rotate along the circumferential direction C. The bearing metal 53 has a circumferential oil groove 73 formed along the circumferential direction C at the center position O1 in the width direction (axial direction A) of the bearing surface 72. This circumferential oil groove 73 is a concave portion formed along the circumferential direction C with a predetermined width on the inner surface of the bearing metal 53, and each end portion in the circumferential direction is in the circumferential direction C in the bearing body 71. It extends to the immediate front of each end and protrudes.

In the bearing metal 53, a plurality of (in this embodiment, eight) axial oil grooves 74 are formed on the bearing surface 72 at predetermined intervals along the axial direction A in the circumferential direction C. This axial oil groove 74 is a concave portion formed along the axial direction A with a predetermined width on the inner surface of the bearing metal 53, and is located on both sides of the circumferential oil groove 73 in the width direction (axial direction A). Is formed. That is, each axial direction oil groove 74 has one end in communication with the circumferential direction oil groove 73.

In the first embodiment, the circumferential oil groove 73 has a width larger than that of each axial oil groove 74, and the depth is formed larger than the depth of each axial oil groove 74. However, it is not limited to this configuration, and the width of the circumferential oil groove 73 may be the same as or smaller than the width of each axial oil groove 74, and the depth may be reduced in each axial oil groove ( 74) You may make it the same as the depth, or you may make it small.

In the bearing metal 53, a plurality of (five in this embodiment) communication holes 75 penetrating from the bottom surface of the circumferential oil groove 73 to the outer surface in the thickness direction of the bearing body 71 are formed. have. Each communication hole 75 is formed in the circumferential direction oil groove 73 at predetermined intervals in the circumferential direction C.

Moreover, the bearing metal 53 is circumferentially from the outer side of the width direction (axial direction A) of the bearing main body 71 to the bearing surfaces 72 on both sides of the width direction (axial direction A) of the circumferential direction oil groove 73 A plurality of (two in this embodiment) inclined grooves 76 that have a larger depth toward the directional oil groove 73 are formed. Each inclined groove 76 is at a position shifted by a predetermined length from the end of the bearing body 71 in the width direction, and from a position outside the width direction of the connecting rod 27 toward the circumferential oil groove 73 The depth has increased. In each of these inclined grooves 76, each end in the axial direction A is located in the middle part of the longitudinal direction of each axial oil groove 74, and each end in the circumferential direction C is in the circumferential direction C of the bearing body 71. It is located at the end. Therefore, each inclined groove 76 is formed on both sides of each axial direction oil groove 74 in the width direction.

In the bearing metal 53, the bearing surface 72 is formed on the inner surface of the bearing body 71, but the circumferential oil groove 73 and each inclined groove 76 are continuously formed on the central side of the axial direction A. Therefore, the region A1 located on the end side of the axial direction A becomes the first pressure receiving surface that always receives the load from the crosshead pin 52. Moreover, each inclined groove 76 becomes deeper toward the circumferential oil groove 73, and when the crosshead 29 is stopped, the outer peripheral surface of the crosshead pin 52 and each inclined groove 76 A minute gap is secured between the bottom surfaces of the floor. However, when the bearing metal 53 is driven by the crosshead 29, when the bearing surface 72 receives the maximum load from the crosshead pin 52, the bearing body 71 is deformed and each inclined groove 76 ) The load is received through this oil film. Therefore, the region A2 in which each inclined groove 76 is formed becomes a second pressure receiving surface that receives a load from the crosshead pin 52.

Here, the circumferential oil groove 73 and the inclined groove 76 in the bearing metal 53 will be described in detail. 8 is a cross-sectional view showing a main part of a crosshead, and FIG. 9 is a cross-sectional view showing a detailed shape of a bearing metal.

As for the bearing metal 53, as shown in FIG. 8 and FIG. 9, while the circumferential direction oil groove 73 is formed in the bearing surface 72 of the bearing main body 71, the inclined groove 76 is formed on both sides thereof. Each is formed. The circumferential oil groove 73 is formed along the circumferential direction C at the center position O1 in the axial direction A, and side surfaces 73b orthogonal to both sides of the bottom surface 73a are formed. The inclined groove 76 shifts from the end portion in the width direction of the bearing body 71 by a predetermined length and increases in depth from the outer position P in the width direction of the connecting rod 27 toward the circumferential oil groove 73, It is connected to the upper end of the side surface 73b of the circumferential direction oil groove 73 at a predetermined angle (obtuse angle). Therefore, the width (length in the axial direction A) W2 of the inclined groove 76 including the circumferential direction oil groove 73 becomes a dimension larger than the width (length in the axial direction A) W1 of the connecting rod 27. This inclined groove 76 is a flat inclined plane in which the bottom surface is inclined at a predetermined angle with respect to the bearing surface 72, and the maximum depth at a position communicating with the circumferential oil groove 73 is the inclined groove 76 It has a dimension smaller than the depth of the circumferential direction oil groove 73 at this communication position.

In addition, the shape of the inclined groove 76 is not limited to the thing mentioned above. 10 is a cross-sectional view showing a detailed shape of a first modified example of a bearing metal.

As shown in FIG. 10, in the bearing metal 53A, the circumferential oil groove 73 is formed in the bearing surface 72 of the bearing main body 71, and inclined grooves 77 are formed on both sides thereof, respectively. have. The inclined groove 77 shifts from the end portion in the width direction of the bearing body 71 by a predetermined length and increases in depth from the outer position P of the connecting rod 27 in the width direction toward the circumferential oil groove 73. Therefore, the width (length in the axial direction A) W2 of the inclined groove 77 including the circumferential direction oil groove 73 becomes a dimension larger than the width (length in the axial direction A) W1 of the connecting rod 27. This inclined groove 77 is an inclined curved surface curved so that the bottom surface is convex toward the crosshead pin 52 in the radial direction R, and from the position P of the bearing surface 72 to the circumferential oil groove 73 It is a continuous curved surface without a step to the bottom. In addition, the inclined groove 77 is a curved surface that increases in depth from the position P toward the circumferential oil groove 73, like the inclined groove 76, and is the upper end of the side surface 73b of the circumferential oil groove 73 You may be connected to.

In addition, the position of the inclined groove 76 is not limited to the one described above. Fig. 11 is a plan view of a crosshead showing a second modification of the bearing metal, and Fig. 12 is a plan view of a crosshead showing a third modification of the bearing metal.

As shown in FIG. 11, the bearing metal 53 is applied to the bearing surfaces 72 on both sides of the circumferential oil groove 73 in the width direction (axial direction A) in the width direction (axial direction A) of the bearing body 71. ), an inclined groove 91 that increases in depth toward the oil groove 73 in the circumferential direction is formed. The inclined groove 91 is at a position shifted from the end portion in the width direction of the bearing body 71 by a predetermined length, and further from the outer position in the width direction of the connecting rod 27 toward the circumferential oil groove 73 Has grown. In each of these inclined grooves 91, each end in the axial direction A is located in the middle part of the longitudinal direction of each axial oil groove 74, and each end in the circumferential direction C is in the circumferential direction C of the bearing body 71. It is located right in front of the end by a predetermined length, and has a rectangular shape when viewed from the top. Therefore, the inclined groove 91 is surrounded by the bearing surface 72 having a flat circumference, and leakage of the lubricating oil to the outside is suppressed.

In addition, as shown in FIG. 12, the bearing metal 53 is formed on the bearing surfaces 72 on both sides of the circumferential oil groove 73 in the width direction (axial direction A) in the width direction (axial direction) of the bearing body 71. An inclined groove 92 that increases in depth toward the circumferential oil groove 73 from the outside of the direction A) is formed. The inclined groove 92 is at a position shifted from the end portion in the width direction of the bearing body 71 by a predetermined length, and further from a position outside the width direction of the connecting rod 27 toward the circumferential oil groove 73. Has grown. In each of these inclined grooves 92, each end of the axial direction A is located in the middle part of the longitudinal direction of each axial oil groove 74, and each end of the circumferential direction C is located at the outermost axial oil groove 74. ), so it is elliptical when viewed from the top. Therefore, the inclined groove 92 is surrounded by the bearing surface 72 having a flat circumference, and leakage of the lubricating oil to the outside is suppressed.

The connecting rod 27 has a circumferential oil groove 81 formed along the circumferential direction C at the center position O1 in the width direction (axial direction A) in the support surface 62a of the lower bearing portion 62. have. The circumferential oil groove 81 is a concave portion formed along the circumferential direction C with a predetermined width in the support surface 62a of the lower bearing portion 62, and each end portion in the circumferential direction is in the bearing body 71 It extends to each end of the circumferential direction C and protrudes. The circumferential oil groove 81 of the lower bearing part 62 is formed in conformity with the circumferential oil groove 73 of the bearing metal 53 and the radial direction R, and the circumferential oil groove 73 and the circumferential direction The oil groove 81 is communicated with the communication hole 75. Moreover, as for the connecting rod 27, the supply flow path 82 is formed along the longitudinal direction at the position where the center position O1 in the axial direction A and the center position O2 in the circumferential direction C intersect. In this supply flow path 82, the upper end part communicates with the circumferential direction oil groove 81, and the tartan part protrudes to the crank 26 (refer FIG. 1).

The crosshead pin 52 has an oil hole 83 formed along the center position O3, and the first supply flow passage 84 and the second supply flow passage 85 cross the radial direction R with respect to the oil hole 83. It is formed according to. The first supply flow passage 84 has one end extending through the piston rod 23 and extending to the piston 18 (see FIG. 1 ), and the tartan portion is in communication with the oil hole 83. In the second supply flow passage 85, one end is in communication with the oil hole 83, and the tartan portion is in communication with the circumferential oil groove 73.

The bearing metal 53 is mounted on the support surface 62a of the lower bearing portion 62 in the connecting rod 27, and the crosshead pin 52 is attached to the bearing surface 72, The lower bearing portion 62 and the upper bearing portion 64 are positioned by being fixed, and the crosshead pin 52 of the piston rod 23 can freely rotate on the connecting rod 27 through the bearing metal 53. So that it is connected.

In addition, in the first embodiment, the circumferential oil groove 73, the axial oil groove 74, the communication hole 75, and the inclined groove 76 of the bearing metal 53 are left and right with respect to the center position O1, respectively. It is formed symmetrically, but it does not have to be symmetrical left and right.

Hereinafter, the supply of lubricating oil will be described. As shown in FIGS. 4 to 6, the lubricating oil (cooling oil) is supplied to the circumferential oil groove 81 on the outer surface side of the bearing metal 53 from a supply passage (not shown) formed in the connecting rod 27. Then, the lubricating oil is supplied to the circumferential oil groove 73 on the inner surface side of the bearing metal 53 through the plurality of communication holes 75, and from the circumferential oil groove 73 to the axial oil groove 74. It is supplied, and is temporarily stored in the circumferential direction oil groove 73 and the axial direction oil groove 74. And, during the operation of the piston rod 23 and the connecting rod 27, the lubricating oil of the circumferential oil groove 73 and the axial oil groove 74 is the bearing surface 72 or the inclined groove of the bearing metal 53 It spreads widely to the outer peripheral surface of 76 and the crosshead pin 52, and is lubricated.

In addition, during the operation of the piston rod 23 and the connecting rod 27, the lubricating oil in the circumferential oil groove 73 is formed in the second supply flow path 85 and the oil hole 83 formed inside the crosshead pin 52. ), is supplied to the piston 18 (see Fig. 1) through the inside of the piston rod 23 from the first supply flow path 84 to be lubricated and cooled. Further, the lubricating oil in the circumferential oil groove 81 is supplied to the crankshaft 24 (see Fig. 1) through the supply passage 82 formed inside the connecting rod 27 to be lubricated and cooled.

Here, the oil film pressure of the bearing metal 53 is demonstrated. Fig. 13 is a schematic diagram showing the oil film pressure and bearing surface shape when a maximum load is applied to the bearing metal.

When the piston rod 23 and the connecting rod 27 are operated, the bearing metal 53 receives a load from the outer circumferential surface of the crosshead pin 52 on the inner surface of the bearing metal 53 and receives surface pressure, so that the oil film pressure increases. At this time, in the conventional bearing metal in which the circumferential oil groove 73 is formed on the inner surface and the inclined groove 76 is not formed, the bearing surface is the crosshead pin 52 as shown by the dotted line in FIG. Since the deformation is convex toward the side, the oil film pressure gradually increases from the end side in the width direction (axial direction A) toward the center, and becomes maximum at the edge periphery of the circumferential oil groove 73. Therefore, there is a risk that the conventional bearing metal is damaged at the edge periphery of the circumferential oil groove 73 due to a high oil film pressure.

On the other hand, the bearing metal 53 of the first embodiment in which the circumferential oil groove 73 is formed on the inner surface and the inclined grooves 76 are formed on both sides thereof, as shown by the solid line in FIG. It gradually increases from the end side in the width direction (axial direction A) toward the center, and becomes maximum at the edge periphery of the circumferential oil groove 73, but is inclined compared to the conventional bearing metal in which the inclined groove 76 is not formed. As there are grooves 76, the convex shape of the bearing surface becomes smooth, and the oil film pressure decreases. Therefore, in the bearing metal 53 of the first embodiment, the increase in the local oil film pressure and decrease in the oil film thickness at the edge periphery of the circumferential oil groove 73 are suppressed by the inclined groove 76, and are damaged. The risk of becoming is lowered.

As described above, in the crosshead bearing (bearing metal 53) of the first embodiment, the bearing body 71 forming a semi-cylindrical shape, the bearing surface 72 formed on the inner surface of the bearing body 71, and the bearing Communication holes (communication portions) 75 penetrating in the thickness direction of the main body 71, and inclined grooves (inclined portions) that increase in depth from both ends in the axial direction A toward the center on the inner surface of the bearing main body 71 (76) are formed.

Therefore, during the operation of the crosshead 29, when the bearing surface 72 of the bearing metal 53 receives surface pressure from the outer circumferential surface of the crosshead pin 52, the inclined groove 76 in the center of the axial direction It is possible to suppress a local increase in oil film pressure or decrease in oil film thickness. As a result, damage due to the bearing load can be suppressed, and the crosshead pin 52 can be satisfactorily supported.

In the crosshead bearing (bearing metal 53) of the first embodiment, a circumferential oil groove 73 is formed along the circumferential direction on the bearing surface 72 at the center of the bearing body 71 in the axial direction. The depth of the inclined groove 76 is increased from both ends of the bearing body 71 in the axial direction toward the circumferential oil groove 73. Therefore, when the bearing surface 72 of the bearing metal 53 receives surface pressure from the outer circumferential surface of the crosshead pin 52, the local oil film at the edge periphery of the circumferential oil groove 73 by the inclined groove 76 It is possible to suppress an increase in pressure or a decrease in the thickness of the oil film.

In the crosshead bearing (bearing metal 53) of the first embodiment, the inclined groove 76 has a depth from the outer side in the width direction of the connecting rod main body 61 of the connecting rod 27 toward the circumferential oil groove 73 Is making it bigger. Therefore, the inclined groove 76 of a sufficient area can be ensured, and the local oil film pressure increase in the center part or the edge peripheral part of the circumferential direction oil groove 73 can be suppressed effectively.

In the crosshead bearing (bearing metal 53) of the first embodiment, the inclined groove 76 is formed with a circumferential oil groove 73 from a position P shifted from the end of the bearing body 71 by a predetermined length. have. Therefore, it is possible to ensure the bearing surface 72 always in contact with the outer circumferential surface of the crosshead pin 52 in a region of a predetermined length from the end of the bearing body 71, and the crosshead pin 52 can be stably supported. have.

In the crosshead bearing (bearing metal 53) of the first embodiment, an inclined groove 76 having a flat inclined plane with a flat bottom surface, or an inclined groove having an inclined curved surface convex toward the crosshead pin 52 (77). The inclined groove 76 facilitates workability, thereby reducing the processing cost, and the inclined groove 77 effectively suppresses an increase in oil film pressure at the edge periphery of the circumferential oil groove 73.

In the crosshead bearing (bearing metal 53) of the first embodiment, the inclined plane of the inclined groove 76 and the inclined curved surface of the inclined groove 77 are the maximum bearing surface 72 from the crosshead pin 52. When receiving the load, the load is received from the crosshead pin 52. Therefore, the increase in local oil film pressure at the edge periphery of the circumferential oil groove 73 by the inclined grooves 76 and 77 can be effectively suppressed, while the crosshead pin 52 can be stably supported. have.

In the crosshead bearing (bearing metal 53) of the first embodiment, along the axial direction A of the crosshead pin 52 on both sides in the width direction of the circumferential oil groove 73 in the bearing surface 72 The axial oil grooves 74 are formed at predetermined intervals in the circumferential direction C, and inclined grooves 76 are formed on both sides of the respective axial oil grooves 74 in the width direction. Accordingly, stable supply of lubricating oil is possible by the plurality of axial oil grooves 74, and the increase in local oil film pressure at the edge periphery of the circumferential oil groove 73 by the inclined groove 76 can be effectively suppressed. I can.

Further, in the crosshead of the first embodiment, the crosshead pin 52, the lower bearing portion 62 of the connecting rod 27 on which the support surface 62a curved to form a semicircular shape is formed, and the lower bearing portion A bearing metal 53 is formed which is supported by the support surface 62a of 62 and supports the outer peripheral surface of the crosshead pin 52 so that it can slide freely. Therefore, during the operation of the crosshead 29, when the bearing surface 72 of the bearing metal 53 receives surface pressure from the outer circumferential surface of the crosshead pin 52, the inclined groove 76 in the center of the axial direction It is possible to suppress a local increase in oil film pressure or decrease in oil film thickness. As a result, damage to the bearing metal 53 due to a bearing load can be suppressed, and the crosshead pin 52 can be satisfactorily supported.

In addition, in the furniture of the first embodiment, the top plate 31 disposed at the top, the bottom plate 32 disposed at the bottom, and the tartan portion are connected to the top plate 31 at one end disposed at the side. A plurality of partition walls in which a side plate 33 connected to the plate 32 and a plurality of space portions 35 penetrating in the vertical direction by being connected to the top plate 31 and the bottom plate 32 and the side plate 33 are partitioned ( 34) and, a plurality of guide plates 28 fixed to the plurality of spaces 35, respectively, and a plurality of crossheads 29 supported so as to be freely movable to each of the plurality of guide plates 28, and have. Therefore, during the operation of the crosshead 29, when the bearing surface 72 of the bearing metal 53 receives surface pressure from the outer circumferential surface of the crosshead pin 52, the inclined groove 76 in the center of the axial direction It is possible to suppress a local increase in oil film pressure or decrease in oil film thickness. As a result, damage to the bearing metal 53 due to a bearing load can be suppressed, and the crosshead pin 52 can be satisfactorily supported.

In addition, in the crosshead type internal combustion engine of the first embodiment, the base plate 11, the furniture 12 formed on the base 11, the cylinder jacket 13 formed on the furniture 12, A plurality of tie bolts 14 connected through the base 11, the furniture 12, and the cylinder jacket 13 are formed. Therefore, when the internal combustion engine is operated, when the bearing surface 72 of the bearing metal 53 receives surface pressure from the outer circumferential surface of the crosshead pin 52, the inclined groove 76 causes a local area in the center of the axial direction. It is possible to suppress an increase in oil film pressure or a decrease in oil film thickness. As a result, damage to the bearing metal 53 due to a bearing load can be suppressed, the crosshead pin 52 can be satisfactorily supported, and the fuel economy and reliability can be improved.

[Second Embodiment]

Fig. 14 is a plan view showing a crosshead of the second embodiment, and Fig. 15 is a cross-sectional view taken along XV-XV in Fig. 14. In addition, members having the same functions as those in the above-described embodiment are denoted by the same reference numerals, and detailed descriptions are omitted.

In the crosshead of the second embodiment, as shown in Figs. 14 and 15, the bearing metal (crosshead bearing) 101 is a bearing body 71, a bearing surface 72, and an axial oil groove. 74, a slit opening (communication part) 102, and an inclined groove (inclined part) 103 are provided.

In the bearing metal 101, a plurality of axial oil grooves 74 are formed in the bearing surface 72 at predetermined intervals along the axial direction A in the circumferential direction C. In the bearing metal 101, a slit opening 102 penetrating in the thickness direction is formed along the circumferential direction C. The end portions of the plurality of axial oil grooves 74 are in communication with the slit openings 102 in the longitudinal direction. The slit opening 102 is formed along the circumferential direction C in the central portion of the bearing body 71 in the axial direction A, and has a width larger than the width of each axial oil groove 74, but the axial oil groove (74) You may make it the same as the width of, or you may make it small.

In addition, the bearing metal 101 has a slit opening (from the outside of the bearing body 71 in the width direction (axial direction A) on the bearing surfaces 72 on both sides of the slit opening 102 in the width direction (axial direction A)). A plurality of (two in the present embodiment) inclined grooves 103 that increase in depth toward 102) are formed. Each inclined groove 103 has a depth at a position shifted by a predetermined length from an end portion of the bearing body 71 in the width direction, and from a position outside the width direction of the connecting rod 27 toward the slit opening 102 Got bigger. In each of these inclined grooves 103, each end of the axial direction A is located in the middle part of the longitudinal direction of each axial oil groove 74, and each end of the circumferential direction C is in the circumferential direction C of the bearing body 71. It is located at the end. Therefore, each inclined groove 103 is formed on both sides of each axial direction oil groove 74 in the width direction.

In the bearing metal 101, the slit opening 102 is formed in the bearing surface 72 of the bearing main body 71, and inclined grooves 103 are formed on both sides thereof, respectively. The slit opening 102 is formed along the circumferential direction C at the center position O1 of the axial direction A, and penetrates in the plate thickness direction of the bearing body 71. The inclined groove 103 shifts from the end portion in the width direction of the bearing body 71 by a predetermined length and increases in depth toward the slit opening 102 from the outer position P in the width direction of the connecting rod 27 It communicates with the slit opening 102. Therefore, the width (length in the axial direction A) W2 of the inclined groove 103 including the slit opening 102 is a dimension larger than the width (length in the axial direction A) W1 of the connecting rod 27.

Therefore, when the piston rod 23 and the connecting rod 27 (both see Fig. 1) are operated, the bearing metal 101 receives a load from the outer peripheral surface of the crosshead pin 52 and receives a surface pressure, and the oil film pressure It rises. At this time, the bearing metal 101 having the slit opening 102 formed on the inner surface and the inclined grooves 103 formed on both sides thereof has an oil film pressure from the end side in the width direction (axial direction A) toward the center. It gradually increases and becomes maximum at the edge periphery of the slit opening 102, but the convex shape of the bearing surface becomes gentle as compared to the conventional bearing metal in which the inclined groove 103 is not formed, and the oil film pressure is reduced. It is said to be low. Therefore, in the bearing metal 101, the deformation of the bearing surface shape is reduced by the inclined groove 103, and local increase in oil film pressure and decrease in oil film thickness at the edge periphery of the slit opening 102 are suppressed. , The risk of damage is reduced.

In this way, in the crosshead bearing (bearing metal 101) of the second embodiment, the bearing body 71 forming a semi-cylindrical shape, the bearing surface 72 formed on the inner surface of the bearing body 71, and the bearing A slit opening 102 penetrating in the thickness direction of the bearing body 71 along the circumferential direction C in the central portion of the body 71 in the axial direction, and the inner surface of the bearing body 71 in the axial direction. An inclined groove (inclined portion) 103 that increases in depth from both ends toward the slit opening 102 is formed.

Therefore, when the crosshead 29 is operated, when the bearing surface 72 of the bearing metal 101 receives surface pressure from the outer circumferential surface of the crosshead pin 52, the inclined groove 103 causes the central portion of the axial direction or An increase in local oil film pressure and a decrease in oil film thickness at the edge portion of the slit opening 102 can be suppressed. As a result, damage due to the bearing load can be suppressed, and the crosshead pin 52 can be satisfactorily supported.

[Third Embodiment]

Fig. 16 is a plan view showing a crosshead according to a third embodiment, and Fig. 17 is a cross-sectional view taken along XVII-XVII in Fig. 16. In addition, members having the same functions as those in the above-described embodiment are denoted by the same reference numerals, and detailed descriptions are omitted.

In the crosshead of the third embodiment, as shown in Figs. 16 and 17, the bearing metal (crosshead bearing) 111 is a bearing body 71, a bearing surface 72, and an axial oil groove. (74), a communication hole (communication part) 112, and an inclined groove (inclined part) 113 are provided.

The bearing metal 111 has a plurality of (four in this embodiment) axial oil grooves 74 on each end side of the circumferential direction C in the bearing surface 72 along the axial direction A along the axial direction C. Are formed at predetermined intervals. In the bearing metal 111, communication holes 112 penetrating in the thickness direction are formed along the circumferential direction C on each end side of the circumferential direction C. The end portions of the plurality of axial oil grooves 74 communicate with the communication holes 112 in the longitudinal direction. The communication hole 112 is formed along the circumferential direction C in the central portion of the bearing body 71 in the axial direction A.

In addition, the bearing metal 111 is an inclined groove 113 whose depth increases from the outer side of the bearing body 71 in the width direction (axial direction A) toward the center of the bearing surface 72 between the communication holes 112. Is formed. The inclined groove 113 has a greater depth from a position shifted by a predetermined length from an end portion of the bearing body 71 in the width direction and from a position outside the width direction of the connecting rod 27 toward the central portion. Each of these inclined grooves 113 is located between the axial oil groove 74 and the communication hole (communication part) 112 formed on each end side in the circumferential direction C.

The bearing metal 111 has an inclined groove 113 whose depth increases toward the center position in the axial direction A of the bearing surface 72 of the bearing body 71. The inclined groove 113 shifted from the end portion in the width direction of the bearing body 71 by a predetermined length and increased in depth from the outer position P in the width direction of the connecting rod 27 toward the center position. Therefore, the width (length in the axial direction A) W2 of the inclined groove 113 becomes a dimension larger than the width (length in the axial direction A) W1 of the connecting rod 27.

In addition, the shape of the inclined groove 113 is not limited to the thing mentioned above. Fig. 18 is a cross-sectional view showing a detailed shape of a first modified example of the bearing metal, and Fig. 19 is a plan view of a crosshead showing a second modified example of the bearing metal.

As shown in Fig. 18, the bearing metal 111A shifts from the end of the bearing body 71 in the width direction by a predetermined length, and has a depth from the outer position P in the width direction of the connecting rod 27 toward the center position. An inclined groove 121 that becomes larger is formed. The inclined groove 121 is an inclined curved surface curved so that the bottom surface is convex toward the crosshead pin 52 in the radial direction R, and there is no step from the position P of the bearing surface 72 to the center position in the axial direction A. It has a continuous curved surface. In addition, as shown in FIG. 19, the bearing metal 111B shifts from the end of the bearing body 71 in the width direction by a predetermined length, and moves from the outer position P in the width direction of the connecting rod 27 toward the center position. Inclined grooves 122 that increase in depth are formed. The inclined groove 122 is an inclined curved surface curved so that the bottom surface becomes concave toward the crosshead pin 52 in the radial direction R, and there is no step from the position P of the bearing surface 72 to the center position in the axial direction A. It has a continuous curved surface. In addition, a first inclined curved surface curved so as to be convex toward the crosshead pin 52 side and a second inclined curved surface curved so as to be concave toward the crosshead pin 52 may be formed in succession without a step difference. .

Fig. 20 is a schematic diagram showing an oil film pressure and a bearing surface shape when a maximum load is applied to the bearing metal. When the piston rod 23 and the connecting rod 27 (both refer to Fig. 1) are operated, the bearing metal 111 receives a load from the outer peripheral surface of the crosshead pin 52 and receives a surface pressure, so that the oil film pressure rises. . At this time, in the conventional bearing metal in which the inclined groove 113 is not formed on the inner surface, the oil film pressure gradually increases from the end side in the width direction (axial direction A) toward the center as shown by the dotted line in FIG. 20, It becomes the maximum in this center. Therefore, in the conventional bearing metal, there is a risk that the central portion in the axial direction at which the oil film pressure is maximized is damaged.

On the other hand, in the bearing metal 111 of the third embodiment in which the inclined groove 113 is formed on the inner surface, as shown by the solid line in Fig. 20, the oil film pressure is from the end side in the width direction (axial direction A) to the center. It gradually rises toward the direction and becomes the maximum in this central part, but is lower than the oil film pressure of the conventional bearing metal in which the inclined groove 113 is not formed. Therefore, in the bearing metal 111 of the third embodiment, the convex shape of the bearing surface is smoothed by the inclined groove 113, and local increase in oil film pressure and decrease in oil film thickness at the center are suppressed, resulting in damage. The risk of becoming is lowered.

As described above, in the crosshead bearing (bearing metal 111) of the third embodiment, the bearing body 71 forming a semi-cylindrical shape, the bearing surface 72 formed on the inner surface of the bearing body 71, and the bearing Communication holes 112 penetrating in the thickness direction to each end portion of the main body 71 in the circumferential direction, and an inclined groove extending in depth from both ends in the axial direction toward the center on the inner surface of the bearing main body 71 ( Inclined portion) 113 is formed.

Therefore, during the operation of the crosshead 29, when the bearing surface 72 of the bearing metal 111 receives surface pressure from the outer circumferential surface of the crosshead pin 52, the inclined groove 113 at the center of the axial direction It is possible to suppress a local increase in oil film pressure or decrease in oil film thickness. As a result, damage due to the bearing load can be suppressed and the crosshead pin can be satisfactorily supported.

In addition, the circumferential oil groove 73, the axial oil groove 74, the communication hole 75, the inclined groove 76, 77, 91, 92, 103, 113, 121, 122 described in the above-described embodiment. The number, shape, size, position, etc. of are not limited to the embodiment.

In addition, in the above-described embodiment, the bearing metals 53, 53A, 101, 111, 111A, and 111B as a crosshead bearing are constituted by one plate material, but may be constituted by a plurality of plate members. In this case, for example, it may be divided into two from the center position O1 in the axial direction A.

10: Diesel engine (crosshead type internal combustion engine)
11: large plate
12: furniture
13: cylinder jacket
14: tie bolt (connection member)
15: nut
16: cylinder liner
17: cylinder cover
18: piston
19: combustion chamber
21: moving device
22: exhaust pipe
23: piston rod
24: crankshaft
25: bearing
26: crank
27: connecting rod
28: guide plate
29: crosshead
31: top plate
32: bottom plate
33: side plate
34: bulkhead
35: space part
51: guide shoe
52: crosshead pin
53, 53A, 101, 111, 111A, 111B: Bearing metal (crosshead bearing)
61: connecting rod body
62: lower bearing part
62a: support surface
64: upper bearing part
71: bearing body
72: bearing surface
73: circumferential oil groove
74: axial oil groove
75, 112: communication hole (communication department)
76, 77, 91, 92, 103, 113, 121, 122: Inclined groove (inclined part)
102: slit opening (communication part)

Claims (12)

In the crosshead bearing that is supported on the support surface of the connecting rod and supports the outer peripheral surface of the crosshead pin so that it can slide freely,
A bearing body forming a semi-cylindrical shape,
A bearing surface formed on the inner surface of the bearing body,
A communication part penetrating in the thickness direction of the bearing body,
A circumferential oil groove formed along the circumferential direction on the bearing surface at the center of the bearing body in the axial direction,
A plurality of axial oil grooves formed at predetermined intervals in the circumferential direction along the axial direction of the crosshead pin on the bearing surface;
An inclination that increases in depth toward the circumferential oil groove at a position shifted by a predetermined length from both ends in the axial direction to the center side on both sides of the width direction of the plurality of axial oil grooves on the inner surface of the bearing body Crosshead bearing, characterized in that it has a portion. The method of claim 1,
The inclined portion is a crosshead bearing, wherein a depth of the inclined portion increases from an outer side in a width direction of the connecting rod toward a central portion in an axial direction of the bearing body. The method of claim 1,
The inclined portion is a crosshead bearing, characterized in that the bottom surface is a flat inclined plane. The method of claim 1,
The inclined portion is a crosshead bearing, characterized in that the inclined curved surface is formed in a convex shape or concave shape toward the crosshead pin on the bottom surface. The method of claim 1,
The inclined portion is a crosshead bearing, characterized in that the bearing surface receives a load through an oil film when a maximum load is received from the crosshead pin. The method of claim 1,
The communication portion is formed along a circumferential direction at a central portion of the bearing body in an axial direction, and the inclined portion increases in depth toward the communication portion from both ends of the bearing body in the axial direction. . Crosshead pins,
A bearing portion on which a curved support surface is formed to form a semicircular shape,
A crosshead comprising the crosshead bearing according to any one of claims 1 to 6, which is supported on the support surface of the bearing unit and supports the outer circumferential surface of the crosshead pin so that it can slide freely. With a top plate placed on the top,
A floor plate disposed on the floor,
A side plate disposed on a side and having one end connected to the top plate and a tartan portion connected to the bottom plate;
A partition wall in which a plurality of spaces are partitioned by being connected to the top plate, the bottom plate, and the side plate,
A guide plate fixed to each of the partition walls,
A furniture comprising the crosshead according to claim 7 supported so as to be freely movable on each of the guide plates. With the big plate,
The furniture according to claim 8 formed on the base plate,
A cylinder jacket formed on the furniture,
A crosshead type internal combustion engine comprising: a connecting member passing through the base plate, the furniture, and the cylinder jacket.
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