JP6258445B2 - Crosshead type 2-stroke engine cylinder liner - Google Patents

Description

  The present disclosure relates to a cylinder liner for an internal combustion engine, in particular, a bottom dead center where the scavenging port of the cylinder liner wall is exposed above the top surface of the piston, and a top dead center where the piston is at the highest position in the cylinder liner. The present invention relates to a cylinder liner for a cross-head type two-stroke engine having a piston that moves in the longitudinal (axial) direction within the cylinder liner.

  In a large crosshead type compression ignition type two-stroke internal combustion engine, the upper part of the cylinder liner, which usually protrudes upward from the cylinder frame and is clamped by the cylinder cover, depends on the combustion process. Due to the heat and pressure generated, they are exposed to very large loads, both thermally and mechanically. The temperature level of the internal working surface of the cylinder liner piston is of decisive importance in terms of the life of the cylinder liner and therefore also in terms of the operating economy of the engine. If the operating surface temperature is too high, thermal cracks may occur in the cylinder liner, and if the temperature is too low, sulfuric acid derived from combustion products may condense on the operating surface, which is the liner material. This leads to increased wear due to corrosive erosion of the cylinder, and also causes the cylinder oil to disassemble the lubricating oil film on the operating surface, leading to an increase in consumption of (expensive) cylinder oil.

  The operating surface temperature usually varies with the engine load, and liners have traditionally been subjected to the maximum load on the engine because the engine must be able to operate at high and low loads for extended periods of time. It is manufactured so that the temperature of the operating surface is close to the maximum allowable temperature. A high temperature level makes it possible to maintain a sufficiently high temperature even with partial loads, thereby preventing acid condensation on the working surface.

  Cylinder lubricating oil and cylinder liner materials are affected by high temperatures at full engine load, which can lead to degradation of the lubricant and permanent damage to the cylinder liner material in the form of thermal cracks. There is sex.

  Known cylinder liners for engines with large internal diameters, for example engines with an internal diameter of more than 50 cm, include the axial cross-section of the cylinder liner closest to the cylinder cover, i.e. the large crosshead type 2 Cooling means including a cooling inner diameter portion is provided in an upper part of the axial region when the stroke engine cylinder liner is always in the upright position. This upper part of the axial region of the cylinder / liner near the cylinder / cover has the highest compression ratio and the combustion chamber part that is the starting point of combustion, and therefore the upper part of the cylinder / liner is the axis of the cylinder / liner. Surrounds the portion of the combustion chamber that is exposed to the maximum temperature and pressure compared to the rest of the directional area. Therefore, the upper part of the cylinder liner must correspond to the maximum pressure and temperature, while the other lower part of the axial region of the cylinder liner is only exposed to lower temperatures and pressures. Therefore, the wall of the upper part of the cylinder liner is particularly thick and requires the most cooling. The temperature and pressure drop when moving axially away from the cylinder cover is gradual, but for practical reasons the cylinder liner wall thickness is typically largely divided into two or three levels. The thinnest wall thickness is provided at the axial end of the cylinder liner closer to the scavenging port, and the thickest wall thickness is provided at the axial end of the cylinder liner having a boundary with the cylinder cover.

  In the upper part of the axial area of the cylinder / liner that is directly below the boundary with the cylinder / cover, a plurality of cooling inner diameter parts are provided at relatively close intervals from the outer recesses on the wall of the thicker cylinder / liner. The longitudinal axis of the linear cooling bore takes a path that is inclined or biased relative to the longitudinal axis of the liner. Each cooling inner diameter portion is inserted with a pipe or guide plate for guiding the flowing coolant from the recess to the top dead center of the inner diameter portion. As it flows into the chamber, it travels through the tube to the upper cylinder cover. The inclined cooling inner diameter portion is uniformly distributed over the circumferential region of the upper portion of the cylinder liner. However, the temperature of the liner material is not uniformly distributed over the circumferential region of the upper part of the cylinder liner. This is because the cylinder liner material immediately adjacent to the cooling inner diameter portion has a lower temperature than the material between the two cooling inner diameter portions. For this reason, the temperature of the material in the upper part of the cylinder liner varies when viewed in the circumferential direction. This non-uniform circumferential temperature distribution in the upper part of the cylinder liner causes stress in the cylinder liner material due to non-uniform thermal expansion of the cylinder liner material, resulting in movement of the upper part of the cylinder liner. This causes uneven wear on the cylinder liner and piston ring because the surface is no longer a perfect circle. Cylinders and liners may become slightly rounder as they become more accustomed, and will undergo new deformations when subjected to new loads, so it cannot be perfect with known cylinders and liners. .

  The portion directly below the upper portion of the cylinder liner is provided with one or more cooling jackets that completely surround the outer surface of the cylinder liner to provide a circumferentially extending space for the coolant. Typically, the cooling jacket extends downwardly from the upper portion of the cylinder liner, with a cooling inner diameter that extends a substantial length toward the cylinder frame and sometimes extends completely to the cylinder frame.

  A cylinder liner of the type described above is known from WO 97/42406.

  GB1219532 has an upper flange with an annular groove, which acts as a water cooling duct and is closed from the outside by a two-part ring having a height slightly larger than the corresponding part of the groove An engine cylinder is disclosed. The steel ring is shrunk on the flange and water is fed and drained through the inner diameter.

WO97 / 42406 GB1219532

  One object of the present invention is to overcome or at least reduce the above-mentioned drawbacks.

  According to a first aspect, this object is achieved by providing a cylinder liner for an internal combustion engine, in particular for a crosshead two-stroke engine. The cylinder liner includes a first end configured to engage the cylinder cover, a scavenging port, and a circumferential cooling for the coolant in the cylinder liner wall near the first end. A circumferential cooling recess having an opening extending in the circumferential direction on the outer surface of the cylinder liner wall, and an axial support member inserted at least partially in the circumferential recess, And an axial support member having an opening that bridges the opening extending in the direction and serves as a coolant passage.

  By using cooling recesses extending in the circumferential direction, the circumferential distribution of the coolant is substantially uniform throughout, eliminating problems due to non-uniform temperature distribution and associated stress and non-uniform wear to a considerable extent. The By providing an axial support member inside the circumferential opening of the cooling recess extending in the circumferential direction, the depth and width of the cooling recess is ensured and the extraordinary compressive force applied to the top of the cylinder liner is reduced. A robust structure that can be accommodated is possible.

  In a first embodiment possible as a first aspect, the axial support member is configured to provide axial support to the circumferential cooling recess.

  In a second embodiment, which is possible as the first aspect, the axial support member fills the axial space between the surfaces of the opening facing each other in the axial direction.

  In the third embodiment, which is possible as the first aspect, the axial space between the axially opposed surfaces of the opening of the cylinder liner is free of the axial surface of the axial support member when there is no load. Slightly larger than the axial distance h between them, so that there is a slight axial clearance between the opening and the axial support member.

  In a fourth embodiment possible as a first aspect, the axial support member is a split ring comprising two or more sections.

  In a fifth embodiment possible as a first aspect, the circumferential cooling recess comprises an upper leaf portion and optionally a lower leaf portion.

  In a sixth embodiment that is possible as the first aspect, the circumferential cooling recess includes a cylindrical surface that connects the upper leaf portion to the lower leaf portion.

  In a seventh embodiment possible as a first aspect, the axial support member comprises an inwardly facing annular recess, and a space for the coolant is defined between the inwardly facing annular recess and the cylindrical surface.

  In an eighth embodiment possible as a first aspect, the circumferential cooling recess is deep enough to receive the axial support member without causing the axial support member to protrude from the circumferential cooling recess. Have

  In a ninth embodiment possible as a first aspect, the cylinder liner is a plurality of cylinders distributed along the circumference of the cylinder liner, preferably at substantially the same level, on the cylinder liner wall. A lubrication supply hole is further provided.

  The above-described object is also achieved as a second aspect by providing a crosshead type two-stroke engine based on the first aspect and including at least one cylinder liner according to any implementation thereof.

  These and other aspects of the invention will be apparent from the detailed description and embodiments set forth below.

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

1 is a front view of a large two-stroke diesel engine according to one embodiment. FIG. FIG. 2 is a side view of the large two-stroke engine of FIG. 1. FIG. 2 is a block diagram of the large two-stroke engine of FIG. 1 is a cross-sectional view of a cylinder frame and a cylinder liner according to an embodiment, with a cylinder cover and an exhaust valve attached. FIG. It is a side view of the cylinder liner by one Example. It is a fragmentary sectional view of the cylinder liner of FIG. It is sectional drawing of the detail of the upper part of the cylinder liner of FIG. 5, Comprising: It is the figure which showed the recessed part for circumferential cooling. FIG. 8 is a detailed view of FIG. 7 in a state in which an axial support member is inserted into a cooling recess on the outer periphery. FIG. 9 is a detail view of FIG. 8 with a circumferential support member surrounding the upper portion of the cylinder liner. It is detail drawing of an axial direction supporting member. FIG. 10 is a detailed view of FIG. 9 with piping for supplying coolant to the circumferential cooling recess. FIG. 10 is a detailed view of FIG. 9, with a pipe for discharging the coolant from the circumferential cooling recess. It is sectional drawing of a circumferential direction support member. FIG. 6 is an exploded view of the cylinder liner of FIG. 5 with the circumferential support member removed. FIG. 6 is a three-dimensional view of the cylinder liner of FIG. 5, excluding a circumferential support member. It is a figure of an axial direction supporting member. FIG. 6 is a cross-sectional view of the top of the cylinder liner of FIG. 5. It is the graph which showed the temperature of the operating surface of the cylinder liner of FIG. 6, and the cylinder liner of a prior art.

  In the detailed description below, an internal combustion engine will be described with reference to a turbocharged crosshead compression ignition large low-speed two-stroke internal combustion engine in some embodiments. FIGS. 1, 2 and 3 show a turbocharged large low speed two stroke diesel engine with a crankshaft 8 and a crosshead 9. FIG. 3 is a block diagram of a large low speed two-stroke diesel engine with a turbocharger along with its intake and exhaust systems. In this embodiment, the engine has four cylinders arranged in series. A turbocharged large low speed two stroke diesel engine typically has 4 to 14 cylinders in series, which are supported by an engine frame 11. The engine can be used, for example, as a main engine in a ship or as a fixed engine for moving a generator at a power plant. The overall power output of the engine can be in the range of 1000 to 110,000 kW, for example.

  In this embodiment, the engine is a two-stroke uniflow type compression ignition engine having a scavenging port 18 in the lower region of the cylinder liner 1 and a central exhaust valve 4 at the top of the cylinder liner 1. The scavenging passes from the scavenging receiver 2 to the scavenging port 18 of each cylinder 1. When the piston 10 compresses scavenging in the cylinder liner 1, fuel is injected from the fuel injection valve in the cylinder cover 22, and then combustion occurs to generate exhaust.

  When the exhaust valve 4 is opened, the exhaust flows through the exhaust duct attached to the cylinder 1 to the exhaust receiver 3, and further reaches the turbine 6 of the turbocharger 5 through the first exhaust pipe 19, from which the exhaust is the second exhaust. Go through the pipeline to the exit 21 via the economizer 20 and into the atmosphere. The turbine 6 drives, via a shaft, a compressor 7 that is supplied with outside air through an air intake 12. The compressor 7 sends the compressed scavenging gas into the scavenging line 13 connected to the scavenging receiver 2. The scavenging of line 13 passes through an intercooler 14 that cools the scavenging (about 200 ° C. when leaving the compressor) to a temperature of 36-80 ° C.

  The cooled scavenging air is driven by the electric motor 17 when the compressor 7 of the turbocharger 5 cannot supply sufficient pressure to the scavenging receiver 2, that is, when the engine is in a low load or partial load state, and the scavenging air flow. Through an auxiliary blower 16 which applies pressure to If the engine load is high, the turbocharger compressor 7 supplies a sufficiently compressed scavenging, in which case the auxiliary blower 16 is bypassed via the check valve 15.

  4, 5 and 6 show a cylinder liner of a large two-stroke crosshead engine, which is given a reference numeral 1 as a whole. Depending on the size of the engine, the cylinder liner 1 can be made in various dimensions, with a cylinder inner diameter typically in the range of 250 mm to 1000 mm and a corresponding typical length of 1000 mm to 4500 mm. The cylinder liner 1 is usually made of cast iron and may be integrated or may be divided into two or more parts that assemble the ends. In the case of a split liner, the upper part can be made of steel. The crosshead type large two-stroke engine has been developed to have a very high effective compression ratio such as 1:16 to 1:20. Therefore, the cylinder liner 1, the piston 10, the piston ring (not shown) A large load is applied to elements that must withstand the pressure in the combustion chamber.

  In FIG. 4, the cylinder liner 1 is shown in a state where it is incorporated in the cylinder frame 23, and the cylinder cover 22 is attached to the top of the cylinder liner 1 with an airtight boundary surface interposed therebetween. . The piston 10 is not shown in FIG. 4 so that the cylinder liner 1 can be seen well together with its cylinder lubrication hole 25 and cylinder lubrication line 24. The cylinder lubrication hole 25 and cylinder lubrication line 24 are not shown in FIG. In order to allow the cylinder lubricating oil to be supplied when the piston 10 passes through the lubrication line 24, the piston ring distributes the cylinder lubricating oil over the entire operating surface of the cylinder liner after the passage.

  The pipe 26 serves to supply a cooling liquid such as water to the cooling / reinforcing mechanism 30 located above the cylinder liner 1. The pipe 28 serves to transport the coolant from the cooling / reinforcing mechanism 30 to the cylinder cover 22. The pipe 27 serves to discharge the coolant from the cylinder cover 22 to the cooling system. The cooling liquid supplied to the cooling / reinforcing mechanism 30 is provided by a cooling system (not shown) well-known as providing a cooling liquid whose supply temperature is controlled, and is discharged from the cylinder cover 22. The material is returned to the cooling system for reconditioning. The thickness of the wall 29 of the cylinder liner 1 varies in the axial direction of the cylinder liner 1. In the illustrated embodiment, the thinnest part of the wall 29 is at the bottom of the cylinder liner 1, ie below the scavenging port 18. The thickest part of the wall 29 of the cylinder liner 1 is at an upper part in the axial region of the cylinder liner 1. The rapid transition of the thickness of the cylinder liner 1 around the middle of the axial direction of the cylinder liner 1 serves as a shoulder portion on which the cylinder can be placed on the cylinder frame 23. The cylinder cover 22 is pressed against the upper surface of the cylinder liner 1 by a large force given by tightening the bolts.

  5 and 6 show the cylinder liner 1 in more detail, and the cooling / support mechanism 30 surrounded by the axis X in the axial direction and the dotted rectangle in FIG. 6 can be seen. The uppermost part of the cylinder liner 1, that is, the part of the cylinder liner 1 that is closest to the longitudinal end of the cylinder liner that forms the boundary with the cylinder cover 22, is indicated by the arrow U from the top of the cylinder liner 1. Extend over distance. This area closest to the upper end of the cylinder liner 1 is the area of the cylinder liner that is exposed to maximum pressure and maximum temperature from the combustion process. This area must therefore have the most effective cooling and the most robust structure compared to the rest of the cylinder liner 1.

  The uppermost portion U extends upward from a shoulder portion 89 formed by a section in which the diameter of the cylinder / liner body is increased toward the upper end of the cylinder / liner 1.

  FIG. 7 shows the cooling / supporting mechanism 30 in more detail. The cooling / supporting mechanism 30 is provided at a portion U of the cylinder liner 1 that is closest to the axial end of the cylinder liner 1 that forms a boundary with the cylinder cover 22. This portion U is also a portion of the cylinder liner that is exposed to the maximum pressure and the highest temperature due to the combustion process. Therefore, the cylinder liner wall 29 in the cylinder liner 1 at this portion is relatively thick.

  However, forced cooling is necessary to keep the temperature of the operating surface of this part of the cylinder liner 1 at an acceptable level, and forced cooling is relatively close to the operating surface of this part of the cylinder liner 1. (Depending on the material type of the cylinder liner 1, the maximum operating surface temperature must be, for example, less than about 300 ° C., and in some cases less than about 280 ° C.). Here, a circumferential recess 31 for providing a space for receiving the coolant is provided in the upper portion U of the cylinder liner 1. The recess 31 opens toward the outer surface of the cylinder liner 1, and in one embodiment, an upper leaf portion 32 and a lower leaf portion 33 are provided there. The opening of the recess has an axial region H between the downward support surface 34 and the upward support surface 35.

  The recess 31 can also be created by milling or as part of the casting process if the liner is a cast product. In the latter case, the recess is machined into a precisely defined shape after casting.

  The curved surfaces of the upper leaf portion 32 and the lower leaf portion 33 follow a shape calculated so that the stress in the material of the cylinder liner 1 is minimized.

  An arrow F in FIG. 7 represents a force applied to the upper surface of the cylinder liner 1 by the cylinder cover 22. The magnitude of the force F is so great that the cylinder liner 1 is deformed if there is no axial support in the gap between the downward support surface 34 and the upward support surface 35. This axial support is shown in FIG. An axial support member 36 is inserted into the annular recess 31 to substantially fill the gap having an H span between the downwardly facing support surface 34 and the upwardly facing support surface 35. As shown in FIG. 8, the axial support member 36 supports the structure of the cylinder liner wall and transmits a substantial portion of the force F, thereby deforming the upper portion of the cylinder liner 1 as indicated by the vertical arrows. prevent. FIG. 10 shows details of the axial support member 36. The axial support member can be in the form of a ring, such as a split ring consisting of two or more parts (shown is a split ring consisting of two parts, but for those skilled in the art, The axial support member can be formed by a plurality of more than two members, and the plurality of members do not necessarily form a continuous ring. Obviously, a plurality of columns or the like suitable for providing directional support could be used). The axial support member 36 has an axial range h between the upward support surface 39 and the downward support surface 40. The axial range h of the axial support member 36 is a gap in the opening of the circumferential recess 31 so that there is a gap between the axial support member and the gap when no force F is applied by the cylinder cover 22. It is preferably slightly smaller than the axial direction region H. This clearance ensures that the cylinder liner 1 is slightly deformed until the downward support surface 34 and the upward support surface 35 abut against the upward support surface 39 and the downward support surface 40 of the axial support member 36, respectively. to enable. This slight deformation of the material in the upper part of the cylinder liner 1 pretensions the liner material around the upper lobe 32 and around the lower lobe 33, thereby the risk of crack formation in the respective leaves 32, 33. Diminish

  It is also possible to use zero or negative clearance to control tension in another way.

  14, 15 and 16 show the circumferential support member 36 and its assembly in more detail. In this embodiment, the axial support member 36 includes two halves 48, 49 that together form a ring. The two halves 48 and 49 are loosely inserted into the circumferential recess 31 and are not connected to each other. FIG. 14 shows the two halves 48, 49 when assembled, and FIG. 15 shows the two halves 48, 49 after assembly.

  Each half 48, 49 is provided with a slot forming a coolant inlet opening 43 and a slot forming a coolant outlet opening 42. The slot forming the coolant outlet opening 42 is T-shaped with rounded edges to prevent cracks due to stress in the material.

  As shown in FIG. 9, a circumferential support member 37 is provided around the upper portion of the cylinder liner 1. The downward surface of the circumferential support member 37 is placed on the upward shoulder portion 38 of the upper portion U of the cylinder liner 1. The circumferential support member 37 provides radial support to the upper portion U of the cylinder liner 1 as indicated by the horizontal arrows in FIG. In one embodiment, the circumferential support member 37 is an integral annular body of high strength steel. In order to improve the capability of radial support by the circumferential support member 37, the circumferential support member 37 is shrink fit around the upper part of the cylinder liner 1 so that the cylinder liner material and the circumferential support member 37 The material is pretensioned. As shown by the pair of opposing upper arrows in FIG. 9, the circumferential support member 37 is pretensioned around an axial region above the circumferential cooling recess 31 of the cylinder, and further in FIG. As indicated by a pair of opposing lower arrows, the circumferential support member 37 is pretensioned around the axial region below the circumferential cooling recess 31 of the cylinder liner 1.

  In another embodiment, a loose fit of the circumferential support member 37 (strong back) is used. The thermal expansion of the cylinder liner causes contact with the circumferential support member (strong back).

  In one embodiment, the circumferential support member 37 has a significant wall thickness and can itself be considered a strong back.

  Between the cylinder liner 1 and the circumferential support member 37, as indicated by a pair of horizontal arrows in FIG. 9, the upper part of the circumferential support member 37, and the lower pair of horizontal support members in FIG. As indicated by the arrow, a radial force is transmitted at a lower portion of the circumferential support member 37. No significant radial force is applied to the intermediate section of the circumferential support member 37, and no significant radial force exists between the axial support member 36 and the circumferential support member 37.

  The circumferential support member 37 is provided with an annular recess 47 for providing a space through which the cooling liquid passes. A gasket (not shown) for sealing the transition between the cylinder liner 1 and the circumferential support member 37 is prepared to ensure a liquid-tight seal. FIG. 13 shows the circumferential support member 37 in more detail in a sectional view.

  As shown in FIG. 11, the circumferential support member 37 is provided with an inflow opening 46. The inflow opening 46 is generally disposed in a region where the stress level of the circumferential support member is low (such as an intermediate height), that is, in a portion of the circumferential support member 37 where no significant radial force is applied. . The inflow opening 46 is connected to the inward circumferential recess 47 of the circumferential support member 37. There may be a plurality of inflow openings 46, but this does not seem necessary or advantageous. The inflow opening 46 is connected to a coolant supply line 26 that supplies coolant from the cooling system. The coolant can flow into the circumferential recess 31 through the inflow opening 43 of the axial support member 36. The coolant can directly enter the lower leaf portion 33 through the inflow opening 43, and the coolant can flow toward the upper leaf portion 32 through the inward radial recess 41 of the axial support member 36. The arrows in FIG. 11 schematically indicate the direction of the coolant flow.

  As shown in FIG. 12, the inclined outflow pipe 44 extends from the upper leaf portion 32 toward the connection block 50 outside the circumferential support member 37. The inclined outlet pipe 44 passes through the outlet opening 42 of the axial support member 36 and further extends through the inclined inner diameter portion 45 provided at a substantially intermediate height of the circumferential support member 37. The inclined configuration of the outflow pipe 44 is such that the inlet to the outflow pipe 44 is located at the uppermost portion of the circumferential recess 31, that is, the position in the upper leaf portion 32, and the inclination direction of the outflow pipe 44 is It is possible to dispose the inclined inner diameter portion 45 at the intermediate height of the circumferential support member 37, that is, at a portion of the circumferential support member 37 where no significant radial force is applied. The outlet of the inclined outflow pipe 44 is connected to the connection block 50 through a welding flange at the end of the outflow pipe 44.

  The connection block 50 is fixed to the outer peripheral surface of the circumferential support member 37. The connection block 50 has a chamfered inner diameter portion, and a cooling water transport pipe 28 extending upward is connected to the upper side of the connection block 50. The cooling water transport line 28 serves to guide the coolant toward the cylinder cover 22 for cooling the cylinder cover 22. The arrows in FIG. 12 schematically show the direction of the coolant flow.

  FIG. 17 is a cross-sectional view of the upper portion U of the cylinder liner 1 showing both the entrance and exit mechanisms of the cooling / support mechanism 30. The structure of the cooling / supporting mechanism 30 is that of the cylinder wall material of the upper part U of the cylinder liner 1 in contrast to the large fluctuation of the temperature of the cylinder liner material in the upper part of the cylinder liner according to the design of the prior art. This results in a substantially uniform circumferential temperature distribution.

  FIG. 18 is a graph showing the temperature of the operating surface of the cylinder liner 1 in comparison with the distance to the mating surface (top surface) of the cylinder cover 22. The solid line shows the temperature curve of the cylinder cover according to the present design, ie the embodiment described herein. The dashed curve shows the temperature curve of a cylinder liner of the prior art such as the example well known from US Pat. In the upper part U of the cylinder liner 1, the temperature curves of the present design and the prior art design are virtually overlapping, i.e. identical. This is expected because the upper part U of the cylinder liner 1 is forcibly cooled both in this design and in the prior art design. The difference is that this design uses a circumferential cooling recess to provide uniform cooling in the entire circumferential direction, while multiple inclined inner diameters in prior art designs provide uniform cooling in the circumferential direction. As a result, the temperature fluctuates along the circumferential region of the upper portion of the cylinder liner 1. However, this situation cannot be seen in FIG. This is because the temperature is plotted not in the circumferential direction but in the axial direction. The two curves are significantly different in the part immediately below the upper part U in the axial region of the cylinder liner 1 (in the graph, the upper part is in the range from 0 to about 0.3 m and the temperature is significantly different. The area underneath is in the range of about 0.3m to 1.3m, but these numbers are only valid for cylinder liners 1 of specific shape and dimensions, and differ significantly in other designs. Need to keep in mind that it may be).

  In the axial region immediately below the upper part U of the cylinder liner 1 of the present design, there is no forced cooling, so the temperature of the operating surface becomes extremely high, and the temperature difference reaches 50 ° C. The high temperature of the working surface in the area directly below the upper part U of the cylinder liner 1 reduces the condensation of acidic combustion products, thereby reducing the corrosion of the cylinder liner 1 and the consumption of cylinder oil. (Cylinder oil contains basic components that compensate for the acidity of the combustion products). Below the operating surface, i.e. about 1.3 m or more from the cylinder cover, the temperature of the operating surface is the same in both this design and the prior art design, where the temperature need not be high. This is because the combustion chamber expansion does not reach this portion of the cylinder liner operating surface to reach high concentrations of acidic combustion products. The advantage due to the absence of forced cooling of the cylinder / liner except for the upper portion U of the cylinder / liner is similarly significant even at an engine load of less than 100% of the maximum continuous rating. The fact that the operating surface temperature in the axial cylinder liner 1 immediately below the upper part U of the cylinder liner results in a higher value applies even when the engine load is relatively low.

The invention has been described in connection with various embodiments set forth herein. However, one of ordinary skill in the art may understand and implement other variations of the disclosed embodiments by examining the drawings, the disclosure, and the appended claims in order to implement the claimed patent. it can. In the claims, the word “comprising” does not exclude other elements or steps, and the indefinite article “a” or “an” does not exclude a plurality. The mere fact that certain measures are recited in mutually different dependent claims does not indicate that a combination of these measures cannot be used to advantage. Any reference signs used in the claims shall not be construed as limiting the scope.

Claims (11)

A cylinder liner (1) for a crosshead type two-stroke engine,
A first end configured to engage a cylinder cover (22);
In proximity to the second end and a scavenging port (18) in the wall (29) of the cylinder liner (1);
A circumferential cooling recess (31) for coolant in the wall of the cylinder liner (1) proximate to the first end, circumferentially on the outer surface of the wall of the cylinder liner (1) A circumferential cooling recess (31) having an opening extending to
An axial support member (36) inserted at least partially in the circumferential recess, bridging the circumferentially extending opening, and an outlet opening (42) serving as a coolant passage and the coolant Cylinder liner (1), comprising an axial support member (36) with an inlet opening (43) serving as a passage.   The cylinder liner (1) of claim 1, wherein the axial support member (36) is configured to provide axial support to the circumferential cooling recess.   The cylinder liner (1) according to claim 1 or 2, wherein the axial support member (36) fills an axial space between axially opposed surfaces (34, 35) of the opening.   When the axial space (H) between the axially opposed surfaces (34, 35) of the opening of the cylinder liner is in an unloaded state, the opposed axial surfaces of the axial support member (36) Cylinder liner (1) according to claim 3, wherein there is a slight axial clearance between said opening and said axial support member (36), so that there is a slight axial clearance h between them. .   Cylinder liner (1) according to any of the preceding claims, wherein the axial support member (36) is a split ring consisting of two or more sections (49, 48).   Cylinder liner (1) according to any of the preceding claims, wherein the circumferential cooling recess (31) also comprises an upper leaf part (32) and optionally a lower leaf part (33).   The cylinder liner (1) according to claim 6, wherein the circumferential cooling recess (31) comprises a cylindrical surface (51) connecting the upper leaf portion (32) to the lower leaf portion (33).   The axial support member (36) comprises an inwardly facing annular recess (41), and a space for coolant is defined between the inwardly facing annular recess (41) and the cylindrical surface (51); Cylinder liner (1) according to claim 7.   The circumferential cooling recess (31) is sufficient to receive the axial support member (36) without projecting the axial support member (36) from the circumferential cooling recess (31). Cylinder liner (1) according to any of the preceding claims, having a depth. To the wall of the cylinder liner (1), before Symbol further comprising a plurality of cylinders lubricant supply holes distributed along the circumference of the cylinder liner (1) (25), to any of claims 1 to 9 Cylinder liner (1) as described.   A crosshead type two-stroke engine comprising at least one cylinder liner (1) according to any one of the preceding claims.