JP2010032055A - Cross head bearing for large-sized two cycle diesel engine - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To provide the cross-head bearing for large-sized two cycle engine which has a large effective bearing face in the bearing part most highly loaded. <P>SOLUTION: A cross-head journal 4 has an axial hole 5 for passing the lubricating oil supplied under the pressure and a prolonged horizontal hole towards the axial hole to a face of the journal 4 facing to the lower bearing shell 12 from the axial hole. In one point of the shaking process of a connecting rod 7 at least, the prolonged hole in the horizontal direction is connected with at least one of the line hole prepared on the circumference of the lower bearing shell 12 or allotted so that it may be connected with the slit of the circumferential direction which is established in either the lower bearing shell 12 or the journal 4. At least one lubrication groove which runs in the axial direction is prepared in the bearing face of the lower bearing shell 12 or the face of the journal 4 facing the lower bearing shell 12, and a slit intersects with a lubrication groove of the circumferential direction. <P>COPYRIGHT: (C)2010,JPO&INPIT

Description

  The present invention relates to a cross head for a large two-cycle diesel engine, and more particularly to an arrangement for supplying lubricating oil to the bearing surface of the cross head.

  The crosshead is a component of an engine that receives an important and heavy load, and requires high reliability during operation. For this reason, the conventional crosshead is a relatively heavy moving part, and as a result, a dynamic load is applied to other engine parts.

  EP 0 199 906 discloses a cross-head bearing for a large two-cycle diesel engine, which is designed to be lubricated with lubricating oil supplied under pressure through an oil supply line connected to the top of the connecting rod. The flow path inside the upper part of the connecting rod leads to an oil supply hole of the bearing shell that opens to a lubrication pocket formed on the bearing surface of the shell. The lubrication pocket requires a supply of lubricating oil at a relatively high pressure (ie, about 12 bar). However, the main lubrication supply (system oil) of large two-cycle diesel engines is only done at a pressure of about 3 bar. Therefore, when the lubrication pocket is used, a dedicated high-pressure lubrication supply system and a pump are required in addition to the normal lubrication supply system. Both high and low pressure systems need to be connected to the crosshead from fixed engine parts, such as through flexible tubing. That is, a flexible connection having a double pipe system is required. Oil pocket type bearings are designed to be small. That is, the radius of the cross head pin is smaller than the bearing surface of the bearing shell. As a result, lubricating oil can be pumped out of the pocket at a supply pressure of 12 bar during a low or negative combustion cycle on the bearing. However, if the crosshead journal surface and the bearing shell surface deviate and the gap between these surfaces is too large at a given radial distance from the center of the effective bearing area, a bearing oil film cannot be formed, The range that can be designed to be small limits the maximum radial extension that can be obtained in the effective bearing area. From a practical standpoint, it has been shown that the radial extension of the effective bearing area cannot extend beyond 40 °. Another disadvantage in the use of lubrication pockets is the inherent tendency for dirt to enter due to the slow flow area.

  MAN B & W Diesel's MC series marine diesel engines use crosshead bearings. It is designed to lubricate by supplying lubricant under pressure through a lubrication line connected to a central axial hole located in the crosshead journal. The upward radial hole leads to a supply hole in the piston rod that supplies cooling oil to the piston. The downward hole leads to a transverse slit in the journal. The transverse slit supplies lubricating oil to the lower bearing surface through an axial lubricating groove on the bearing surface of the lower bearing shell. The transverse slit intersects a large diameter hole in the lower bearing shell that connects to a longitudinally extending oil supply hole to supply lubricating oil to the crankpin bearing. The central axial hole of the crosshead journal is supplied with system oil, usually 3 bar, from a lubricating oil system via a single flexible tube, and does not require a dedicated high-pressure oil supply. The crosshead journal with this structure is designed to be large. That is, the radius of the journal of the crosshead is larger than the radius of the bearing surface of the bearing shell. This design is also referred to as an “embedded arc” because it provides a narrow gap between the bearing surface of the shell and the entire journal surface of the crosshead journal. Therefore, the effective radial extension of the bearing surface can be up to 120 °.

The disadvantage of the transverse slit and the large diameter oil hole in the center of the maximum load part of the bearing is the division of the bearing oil film, i.e. the oil film is split axially, with higher peak pressure and steeper pressure gradient Give rise to
GB1524757 and GB2020783 disclose crosshead bearings comprising two separate lower bearing shells and an axial lubrication slit located in the heavily loaded area of the bearing shell. The oil film shape is not a single large arc shape in these structures, but rather a group of small arc shapes. Therefore, the maximum hydraulic pressure at the same load is very high when compared with the pressure curve of a bearing having a single arc-shaped oil film.
European Patent Publication EP0199906

  In view of this background, an object of the present invention is to provide a crosshead having a large and effective bearing surface in a portion of the bearing that receives the most load.

This object is achieved by claim 1 which provides a crosshead bearing for a large two-cycle engine. The bearing includes a bearing saddle integral with a connecting rod, a lower bearing shell having a single bearing surface supported by the bearing saddle, a bearing surface of the lower bearing shell, or a journal facing the lower bearing shell. Provided with at least two lubrication grooves or linear lubrication openings provided on the surface and running in the axial direction; and a bearing cap fixed to the bearing saddle,
Further, the bearing is rotatable around a crosshead journal, and the journal is formed with an axial hole for passing lubricating oil supplied under pressure, and from the axial hole. A bore extending substantially transversely to the axial bore to the surface of the journal associated with the bearing cap, wherein at least a portion of the swinging of the connecting rod during operation, the lower bearing At least one radial hole is formed which is arranged to connect to at least one flow path reaching the axial lubrication groove of the shell;
However, the flow path from the axial hole to the axial lubrication groove or linear lubrication opening is substantially adjacent to the bearing surface and / or above or below the bearing shell. It is formed so as to be substantially adjacent to any back surface.

  The flow path includes at least one circumferential groove extending from the bearing cap to the saddle.

  The bearing surface at the maximum load portion of the bearing is not divided over a wide angle. By using lubrication grooves on the bearing surface, an embedded arc design is possible. Combining these two features results in a bearing oil film in a wide range at the maximum load portion of the bearing. The lower maximum pressure of the oil film of the bearing can reduce the size and weight of the bearing, resulting in lower dynamic load on other engine parts such as the small end, and the average main bearing of the crankshaft It has a positive effect on the pressure.

  The radial hole preferably opens into a circumferential slit in the bearing cap or upper bearing shell, the slit at least partially overlapping the circumferential groove. Accordingly, the lubricating oil can flow from the radial hole to the circumferential groove.

  The saddle includes an axial hole that intersects both the circumferential groove and a circumferential groove extending to the saddle, and the circumferential groove of the saddle is the axial groove. In order to supply lubricating oil to the bearing of the crank pin through the lubricating groove, at least two oil supply holes intersecting with the oil supply hole extending through the connecting rod are opened.

The above objective is accomplished according to claim 10 which provides a cross head bearing for a large two cycle engine. The bearing includes a bearing saddle integral with a connecting rod, a lower bearing shell having a single bearing surface supported by the bearing saddle, and a bearing cap fixed to the bearing saddle.
Further, the bearing is rotatable around a crosshead journal, and the journal is formed with an axial hole for passing lubricating oil supplied under pressure, and from the axial hole. A bore extending substantially transverse to the axial bore to the surface of the journal associated with the lower bearing shell, wherein at least part of the swinging of the connecting rod in operation, the lower portion Connected to at least one of the row holes extending on the circumference of the bearing shell, or connected to at least one of the circumferential slits located in either the lower bearing shell or the journal. At least one radial hole is formed, and the transverse slit is a bearing surface of the lower bearing shell or of the journal facing the lower bearing shell. Are arranged on the surface, at least one intersection of the axial lubrication grooves.

  The effect is the same as that described for the crosshead bearing according to claim 1. The bearing surface at the maximum load portion of the bearing is not divided over a wide angle. By using lubrication grooves on the bearing surface, an embedded arc design is possible. Combining these two features results in a bearing oil film in a wide range at the maximum load portion of the bearing. The lower maximum pressure of the bearing oil film reduces the size and weight of the bearing, resulting in lower dynamic loads on other engine components.

  A circumferential groove extending to the saddle is disposed under the circumferential slit, and the circumferential groove is connected to the connecting rod to supply lubricating oil to a crank pin bearing. It preferably crosses the oiling holes extending longitudinally therethrough.

  Further objects, features, advantages and characteristics of the crosshead according to the present invention will become apparent from the following detailed description.

  In the following detailed portion of the description, the invention will be described in more detail with reference to the exemplary embodiments shown in the drawings.

  FIG. 1 shows a crosshead bearing 1 for a large two-cycle diesel engine according to a first embodiment. The piston rod 2 is connected by a hydraulic clamping stud to a crosshead journal 4 with an axial hole 5 closed at its axial end. An integral crosshead bearing cap 6 for the piston rod 2 having an angle cutout is fixed to the connecting rod 7 by a stud 8 and a nut 9 which are tightened by a hydraulic jack. The bearing cap 6 includes a thin-walled upper steel shell 10, and white metal is lined on the inner surface of the bearing. The connecting rod 7 includes an integrated saddle 11 that holds a thin-walled lower steel shell 12, and the inner surface of the bearing is lined with white metal or the like. The lower shell 12 of the saddle 11 functions essentially as an integral component, but can also be formed of two or more closely stacked parts that form a continuous bearing surface. That is, the movement between the parts forming the shell is suppressed and the level is maintained. The saddle 11 and the bearing cap 6 together form a crosshead bearing housing. The bearing surface on the lower shell 12 forms a bearing hole for receiving the crosshead journal 4 in cooperation with the bearing surface of the upper shell 10. This bearing is designed to be large. That is, the radius of the crosshead journal 4 is larger than the radius of the bearing shell, and the front surface of the journal and the bearing surface of the shell can be made sufficiently close to form a complete oil film on the entire outer periphery of the bearing. This design is also referred to as an embedded arc.

  The crosshead is made of forged steel, and includes a guide shoe (not shown) made of cast steel lined with white metal on the operation surface. The telescopic fitting tube (not shown) descends from the uppermost system oil line (not shown) of the cylinder frame toward the crosshead and is placed on one of the guide shoes. Extends down towards a bracket (not shown) for oil to be injected from.

  As shown in FIG. 2, the axial hole 5 of the journal 4 is connected to a telescoping fitting tube via a radial hole 28 and a groove and hole (not shown) in the crosshead, about 3 bar. A relatively low pressure lubricating oil is supplied from an engine lubricating system (system oil). However, the connection between the lubrication system and the axial hole 5 does not require the use of a telescopic fitting tube, and it is also possible to use a hinged tube and / or a flexible tube which are known in the art. A further radial hole 29 supplies lubricating oil to the guide shoe.

  In order to cool the piston (not shown), lubricating oil flows from the axial hole 5 to the piston through the upward radial hole 13 towards the hollow piston rod 2. Oil returning from the piston through the piston rod 2 is received in two upward holes 14 leading to the oil reservoir.

  A total of four holes 15 extending in the radial direction from the axial hole 5 to the surface of the journal 4 on the bearing cap side are provided on each side of the hole 14 directed upward.

  As shown in FIG. 3, two grooves 16 that run in the circumferential direction are provided in the axial direction of the bearing surface of the upper shell 10 at an interval. The groove 16 is disposed so as to face the opening of the radial hole 15 and receives lubricating oil flowing out from the hole of the radial hole 15. One circumferential groove 16 is provided on each side of the upwardly facing radial hole 13 in the upper shell 10. The circumferential groove 16 is provided so as to run over the entire circumference of the upper shell 10. The central portion of the circumferential groove 16 is deep enough to form a slit through the bearing shell, but the end of the circumferential groove 16 is shallow, and the bearing of the upper bearing shell 12 It goes to the lubricating groove 17 in the axial direction formed on the surface. Two grooves 18 running in the circumferential direction are formed in the bearing cap 6 and the saddle 11 at the back of the circumferential groove 16 at intervals in the axial direction (FIGS. 4 and 5). Lubricating oil flows through the central portion of the circumferential groove 16 and into each circumferential groove 18. It is also possible to omit the upper bearing shell. In this case, the surface of the upper bearing cap functions as the upper bearing surface, and the lubricating oil flows directly from the radial hole 15 to the circumferential groove 18.

  The length of the circumferential groove 18 extends over the entire circumference of the bearing cap 6, and its end extends to the saddle 11. The end of the circumferential groove 18 in the saddle 11 intersects with an axial hole 19 embedded in the saddle 11.

The axial hole 19 connects the ends of two grooves 18 formed at intervals in the axial direction to a circumferential groove 20 provided at the axial center of the saddle 11.
The length of the circumferential groove 20 extends over the entire circumference of the saddle 11. It is also possible to locate the axial hole 19 in the bearing cap 6. In this case, it is not necessary to extend the groove 18 provided at an interval in the axial direction to the saddle 11, but instead, the circumferential groove 20 at the center in the axial direction extends to the bearing cap 6 and the axial hole 19. Connect to. Alternatively, the hole 19 may be reduced by reducing the length of either the axially spaced groove 18 or the central circumferential groove 20 by hanging the hole 19 circumferentially a length. May extend diagonally between these grooves (not shown).

  The circumferential groove 20 opens into the oil supply hole 21 of the lower shell 12 (FIG. 3), and the oil supply hole 21 of the lower shell 12 is formed in the axial lubrication groove 22 disposed on the bearing surface of the lower shell 12. Communicates. As shown in the figure, it is preferable that there are two axial lubrication grooves 22, but it may be four, for example, depending on the situation. Part of the lubricating oil flowing from the axial hole 19 to the circumferential groove 20 flows to the axial lubricating groove 22 through the oil supply hole 21. Most of the oil in the lubrication groove 22 is pumped from its end and received in an oil sump (not shown), while some of the lubricant flowing through the axial lubrication groove 22 is transverse. To help form an oil film carrying the journal 4, substantially preventing direct contact between the journal surface of the lower shell 12 and the bearing surface and providing lubrication.

  Most of the lubricating oil flowing from the axial hole 19 to the circumferential groove 20 does not flow into the oil supply hole 21, but instead to supply the lubricating oil to a crank pin bearing (not shown). Then, it intersects with the groove 20 extending in the radial direction at the center of the saddle 11 and further flows through the connecting rod 7 to the large-diameter oil supply hole 23 extending in the longitudinal direction.

  The axial lubrication groove 22 can be replaced by a row of bearing surface openings (not shown) in all of the described embodiments. The opening is provided with an axial oil supply passage in the lower part of either the back surface of the bearing shell 12 or the saddle 11.

  Therefore, the flow path from the opening of the axial hole 5 to the lubricating groove 22 or the linear lubricating opening running in the axial direction is substantially adjacent to the bearing surface, or any bearing. It extends along the back of the shell. Although the channel 19 is formed in the saddle, it is still considered that this portion of the channel is substantially adjacent to the back of the bearing shell.

  FIG. 6 shows the pressure distribution in the radial direction of the oil film of the crosshead bearing according to the first embodiment. It has a single peak with a wide base and a relatively low maximum amplitude. FIG. 8 shows the corresponding radial pressure distribution of a prior art structure with a lubricious pocket with a narrow base and a very high maximum amplitude.

  FIG. 7 shows the axial pressure distribution of the bearing oil film, with a wide base and a relatively low maximum amplitude. FIG. 9 shows the corresponding radial pressure distribution of a prior art structure with transverse slits in the crosshead journal, with two separate peaks where the maximum pressure is very high.

  As shown in FIGS. 1 and 3, the axial lubrication groove 22 is disposed in a boundary region of a portion where a large load is applied. The angular distance of the lubricating groove 22 can be a maximum of 120 °. This provides the crosshead bearing with an effective bearing area in the heavily loaded part of the bearing, which is designed to make this type of bearing smaller so that a crosshead bearing with a lubrication pocket can be created. Significantly wider than what can be provided. Smaller dimensions limit the maximum radial extension of the bearing oil film to about 40 ° in the heavily loaded portion of the bearing.

  FIG. 10 shows a second embodiment of the crosshead bearing 1. The piston rod 2 is connected to a crosshead journal 4 with an axial hole 5 by a hydraulic clamping stud (not shown). An integral crosshead bearing cap 6 for the piston rod 2 with an angle cutout is fixed to the connecting rod 7 by a stud and nut 9 which are tightened by a hydraulic jack. The bearing cap 6 includes a thin-walled upper steel shell 10, and white metal is lined on the inner surface of the bearing. The connecting rod 7 includes an integrated saddle 11 that holds a thin-walled lower steel shell 12, and the inner surface of the bearing is lined with white metal. The lower shell 12 of the saddle 11 functions essentially as an integral component, but can also be formed of two or more elements that are closely stacked to form a continuous bearing surface. In this case, the elements forming the shell are restrained from moving between the elements and kept horizontal. The saddle 11 and the bearing cap 6 form a housing for the crosshead bearing. The bearing surface on the lower shell 12 forms a bearing hole for receiving the crosshead journal 4 in cooperation with the bearing surface of the upper shell 10. This bearing is designed to be large. That is, the radius of the crosshead journal 4 is larger than the radius of the bearing shell, and the front surface of the journal and the bearing surface of the shell can be made sufficiently close to form a complete oil film on the entire outer periphery of the bearing. This design is also referred to as an embedded arc.

  The crosshead is made of forged steel, and includes a guide shoe (not shown) made of cast steel lined with white metal on the operation surface. The telescopic fitting tube (not shown) descends from the uppermost system oil line (not shown) of the cylinder frame toward the crosshead and is placed on one of the guide shoes. Extends down towards a bracket (not shown) for oil to be injected from.

  As shown in FIG. 11, the axial hole 5 of the journal 4 is connected to a telescopic fitting tube through a radial hole 28 and a groove and hole (not shown) in the crosshead, about 3 bar. A relatively low pressure lubricating oil is supplied from an engine lubricating system (system oil). However, the connection between the lubrication system and the axial hole 5 does not have to be formed by a telescopic fitting tube, and it is also possible to use hinged tubes and / or flexible tubes, which are known in the art. A further radial hole 29 supplies lubricating oil to the guide shoe.

  Lubricating oil flows from the axial bore 5 to the piston through the upward radial bore 13 towards the hollow piston rod 2 to cool the piston (not shown). Oil returning from the piston through the piston rod 2 is received by the two upward holes 14. The oil is led from the hole 14 to an oil reservoir (not shown).

  Two diagonally downward holes 24 extend from the axial hole 5 to the surface of the journal 4 with the lower bearing shell 12.

  As shown in FIG. 12, two circumferential slits 25 (in the center in the axial direction) are provided in the bearing surface of the lower shell 12, one of which faces the respective opening of the radial hole 24. Then, the lubricating oil flowing out from the radial holes 24 is received. The circumferential slit 25 extends from the upper edge of the lower bearing shell 12 toward the lower side of the two axial lubricating grooves 22. Part of the lubricating oil flows through the circumferential slit 25 into the axial lubricating groove 22. Alternatively, the circumferential slit 25 can be located in the saddle 11 directly below the lower bearing shell. Further, the lower bearing shell includes an opening (not shown) that connects the circumferential slit 25 of the saddle 11 to the obliquely downward hole 24.

  Part of the lubricating oil that flows from the radial hole 24 to the circumferential slit 25 flows to the axial lubricating groove 22. Most of the oil in the lubricating groove 22 is pumped from its end and received in an oil reservoir (not shown). A portion of the lubricating oil flowing through the axial lubrication groove 22 is pumped in the transverse direction to assist in the formation of the oil film carrying the journal 4 and substantially directly between the journal surface of the lower shell 12 and the bearing surface. Prevent contact and provide lubrication. As shown in the figure, it is desirable that there are two axial lubrication grooves 22, but with two axial lubrication grooves intersecting with each of the circumferential slits 25, for example, four according to the situation. And so on.

  As shown in FIGS. 13 and 14, the saddle 11 is provided with a groove 26 provided from the end to the end in the circumferential direction of the saddle 11 at the center in the axial direction. The circumferential groove 26 has a varying width and is disposed below the circumferential slit 25. A part of the circumferential groove 26 that opens to the circumferential slit 25 is wider than the central portion in the radial direction. Most of the lubricating oil flowing from the radial hole 24 to the circumferential slit 25 does not flow into the lubricating groove 22, but instead, via a radial groove 26, a crankpin bearing (not shown). In order to supply the lubricating oil to the large diameter oil supply hole 23 that intersects the central portion of the radial groove 26 and extends in the longitudinal direction through the connecting rod 7.

  The pressure distribution state of the oil film of the bearing according to the second embodiment is substantially the same as that of the first embodiment shown in FIGS. The resulting radial extension of the bearing oil film reaches a maximum of 120 ° in the second embodiment as well.

  15 and 16 show a third embodiment of the present invention. Similar to the first embodiment, the third embodiment includes an upward flow path 15 of the crosshead journal, and a groove 18 provided on the bearing cap 6 at an interval in the axial direction via a slit 16. Guide lubricating oil. The axially spaced grooves 18 intersect two grooves 20 ′ that are arranged obliquely in the saddle 11 (in the saddle, or in the bearing cap as shown). This groove 20 ′ intersects the large-diameter oil supply hole 23 in the center of the saddle. The oblique groove 20 ′ opens in two oil supply holes 21 spaced in the axial direction in each of the axial lubrication grooves 22, and supplies lubricating oil to the lower bearing surface.

  According to another embodiment (not shown), the axial lubrication groove 22 can be arranged in the journal 4. The journal axial lubrication groove 22 is lubricated via a circumferential groove extending from the opening of the radial hole 24 along the bearing surface towards the axial lubrication groove 22 of the journal 4. Is possible. The circumferential groove can be received on the surface of the journal surface or the lower bearing shell.

  For all the embodiments described above, the axial lubrication groove 22 can be replaced by a row of lubrication openings (not shown) spaced apart by the lower bearing shell 12. An axial groove (not shown) on the rear surface of the bearing shell can supply lubricating oil to the row of openings.

  While the present invention appears to be most advantageous for larger designed bearings, it can also be used with smaller designed bearings.

  Although the present invention has been described in detail for purposes of illustration, it is to be understood that such details are merely for that purpose and that one skilled in the art can make changes without departing from the scope of the invention.

1 is a perspective sectional view of a first embodiment of a crosshead according to the present invention. FIG. 2 is a detailed perspective and cutaway view of the crosshead journal of FIG. 1. FIG. 3 is a detailed perspective cutaway view of the upper and lower bearing shells. FIG. 4 is a detailed cutaway view of a bearing cap and saddle. FIG. 5 is a perspective view of the crosshead with the crosshead journal and bearing shell removed, showing the saddle grooves and oiling holes. The pressure distribution of the cross direction in the oil film of the crosshead bearing by 1st Embodiment is shown. The pressure distribution of the axial direction in the oil film of the crosshead bearing by 1st Embodiment is shown. Fig. 2 shows the transverse pressure distribution in the oil film of a prior art crosshead bearing of the type using oil pockets. Fig. 3 shows the axial pressure distribution in the oil film of a prior art crosshead bearing of the type using cross-slip journal cross oil. It is a perspective sectional view of a 2nd embodiment of a crosshead by the present invention. FIG. 11 is a detailed cutaway view of the crosshead journal of FIG. 10. FIG. 5 is a detailed perspective view of the upper and lower bearing shells. FIG. 4 is a detailed cutaway view of a bearing cap and saddle. FIG. 5 is a perspective view of the crosshead with the crosshead journal and bearing shell removed, showing the saddle grooves and oiling holes. 3 shows a third embodiment of the present invention. 3 shows a third embodiment of the present invention.

Claims (4)

A bearing saddle (11) integral with the connecting rod (7);
A lower bearing shell (12) having a single bearing surface supported by the bearing saddle (11);
A bearing cap (6) fixed to the bearing saddle (11);
A cross-head bearing (1) for a large two-cycle engine comprising:
The crosshead bearing (1) is rotatable around a crosshead journal (4),
The cross head journal (4) has an axial hole (5) through which lubricating oil supplied under pressure is passed, and is opposed to the lower bearing shell (12) from the axial hole (5). A hole (15) extending laterally with respect to the axial hole (5) to the surface of the journal, wherein the laterally extending hole (15) is in contact with the connecting rod (7) ) At least at one point in the swinging process, or connected to at least one of the row holes provided on the circumference of the lower bearing shell (12), or of the lower bearing shell (12) or the journal (4). Arranged to connect to at least one of the circumferential slits (25) provided on either
On the bearing surface of the lower bearing shell (12) or the surface of the journal (4) facing the lower bearing shell (12), at least one lubricating groove (22) running in the axial direction is provided,
The circumferential slit (25) and the lubricating groove (22) are arranged so as to intersect with each other.
Cross head bearing.   In the bearing saddle (11), a circumferential groove (26) is provided under the circumferential slit (25), provided that the circumferential groove (26) lubricates the crank pin with lubricating oil. 2. The crosshead bearing according to claim 1, wherein the crosshead bearing intersects with an oiling hole (23) extending longitudinally through the connecting rod (7) for feeding.   The crosshead bearing according to claim 1 or 2, wherein the diameter of the bearing surface of the bearing shell is designed to be larger than the diameter of the crosshead journal.   The crosshead bearing according to claim 1 or 2, wherein the diameter of the bearing surface of the bearing shell is designed to be smaller than the diameter of the crosshead journal.

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