CN1207164A - Gas seals for internal combustion engines - Google Patents

Abstract

A gas seal for sealing high pressure gas in at least one cylinder of an internal combustion engine comprises a cylinder block (15), a cylinder head (11) having a groove (17) formed in its underside, a cylinder liner (13) having a complementary groove (19) formed in its top surface, an O-ring of ductile metal disposed between the groove formed in the cylinder head and the complementary groove formed in the cylinder liner and in contact with respective edges of the grooves, the O-ring being compressed to form a plurality of radial contact constraints with the edges when the cylinder head is fastened to the cylinder.

Description

Gas seals for internal combustion engines

This application is a continuation-in-part of US Patent Application Serial No. 714,766 filed September 16,1996.

invention technical field

The invention relates to a high-pressure sealing device, in particular to a gas sealing device of an internal combustion engine, comprising an O-ring arranged between a cylinder head and a cylinder liner to effectively seal high-pressure gas.

Background of the invention

In order to operate an internal combustion engine economically and efficiently, it is necessary to have various suitable sealing arrangements to prevent the escape of gases or liquids which could impair the performance of the engine. In particular, sealing the high-pressure gas inside the cylinder is essential for the efficient operation of internal combustion engines, especially diesel engines. Proper sealing between the cylinder liner and the cylinder head is necessary for a diesel engine, which relies on the most appropriate pressure and temperature conditions in order to ignite the fuel. If the cylinder head of the cylinder liner is not properly sealed, gas may escape from the cylinder during engine operation, causing loss of engine power and efficiency. Various devices and methods have been developed in an attempt to provide effective sealing means at the cylinder liner and cylinder head interface. An example of this attempt can be found in U.S. Patent No. 4,917,062 to Tapper et al., which discloses the use of a complementary rectangular groove pressed into the cylinder head and engine block when the cylinder head is fastened to the cylinder block. Elastomeric polymeric "O" ring for sealing. However, the device of Tapper et al. is not designed to effectively seal high pressure gases in internal combustion engines. For example, Tapper et al. employ an elastic polymeric "O" ring that can fail due to the high pressure gases generated in an internal combustion engine.

Another kind of combustion sealing structure can be found in the Russian patent application of Butov serial number SU1,481,45/A1, and it discloses the sealing device that connects internal combustion engine cylinder head and cylinder liner. The seal comprises a seal ring made of deformable material, while the cylinder head and cylinder liner have a series of concentric grooves formed therein. When the cylinder head is tightened, the ridges between the concentric grooves press into the sealing rings, thereby forming a seal between the cylinder head and the cylinder liner. The multiple grooves in the cylinder head and cylinder liner add to the manufacturing cost of the sealing joint by requiring precise positioning to ensure that the corresponding grooves fit properly.

German patent application No 35 30 372 A1 to Heitjohann discloses a sealing device for a pressure ring gap between two cylindrical surfaces. The sealing means includes a ring held in an annular groove provided on one of the two cylindrical surfaces. The reference refers to the ring as a "soft link", which means that it is made of a soft material. In this sense, the structure disclosed in the Heitjohann document suffers from the same disadvantages as in the above-mentioned Topper et al. patent.

Another combustion seal arrangement is found in US Pat. No. 2,553,222 to Wallgren et al. which utilizes a seal ring which is pressed into a groove formed in the cylinder section when the cylinder head is installed and secured. The seal ring consists of copper and deforms within the cylinder groove. When the cylinder head is removed and then reinstalled, the sealing ring can be turned upside down so that the ring is again pressed into the groove formed in the cylinder section. However, the seal ring of Wallgren et al. forms only a one-site seal between the cylinder head and the cylinder section, which increases the chance of high pressure gas escaping from the cylinder during engine operation. As mentioned above, this problem can impair engine performance and efficiency.

US 5,275,139 to Rosenqnist discloses a sealing arrangement comprising a deep groove in the cylinder head and a complementary deep groove formed in the cylinder body. A loose fitting surrounding fire ring is disposed in the groove of both the cylinder head and the cylinder block. The Rosenquist arrangement is complex in that the seal requires a deep groove in the cylinder head and cylinder block, which increases manufacturing costs. In addition, this arrangement does not utilize cylinder liners and is therefore impractical for many types of engines that utilize cylinder liners that are press fit within the cylinder bore. A loose fit ferrule is also undesirable because it adds cost to the manufacturing process and has limited sealing performance.

Based on the limited teachings of the aforementioned references, there is a need for a gas seal that is simple to manufacture, yet durable and effective, in order to withstand the extremely high gas pressures that act on the seal during engine operation. Improved seals increase the engine's efficiency at peak performance. Destruction of combustion seals at high gas pressures can lead to undesired shutdowns and costly repairs of the internal combustion engine. Therefore, the gas seal must be able to withstand the day-to-day operation of the engine without damage at high pressure and temperature.

Summary of the invention

In view of the foregoing, it is an object of the present invention to provide an improved gas seal which is simple to manufacture, durable and effective so as to withstand the extremely high combustion gas pressures acting on the seal during engine operation.

Another object of the present invention is to achieve the above object and to provide an improved gas sealing device between the cylinder head and the cylinder liner of the internal combustion engine.

Yet another object of the present invention is to achieve one or more of the above objects, and also to provide a gas seal structure provided with radial restraint points to secure the seal ring at the between the cylinder head and the cylinder liner.

Yet another object of the present invention is to provide a gas seal in which secondary forces acting on the O-ring are minimized during engine operation to protect the O-ring and seal the O-ring and An O-ring seal is used between the cylinder heads, and the interface between the O-ring and the cylinder head and between the O-ring and the cylinder liner is sealed.

These and other objects of the present invention are achieved by a gas sealing device for sealing high-pressure gas in at least one cylinder of an internal combustion engine comprising a cylinder block in which one or more cylinder barrels are formed; A cylinder head has a top surface and a bottom surface. The cylinder head is rigidly connected to the cylinder block, and a groove is formed on the bottom surface of the cylinder head. In addition, the sealing device comprises a cylinder liner having a top surface and being fitted into at least one cylinder barrel made in the cylinder body, the cylinder liner having a complementary groove formed on its top surface, an O-shaped The ring is arranged between the grooves made in the cylinder head and the complementary grooves made in the cylinder liner, and is in contact with the edges of these grooves, wherein when the cylinder head is fastened to the cylinder, the O-ring is Compression causes the O-ring to form multiple radial contact constraints with these edges, and a part of the O-ring is flattened and deformed against the bottom surface of the cylinder head and the top surface of the cylinder liner. The grooves formed on the cylinder head and cylinder liner can have a V shape, a rectangle or a semicircle. Furthermore, the O-ring comprises a deformable material such as carbon steel, alloy steel and steel alloys. In addition, the alloy may be heat treated using known heat treatment processes, such as annealing. When the cylinder head is fastened to the cylinder block, the O-rings are between these grooves on the cylinder head and cylinder liner before pressure is applied. Upon application of compressive force, the O-ring deforms within these grooves so that a portion of the O-ring protrudes into the grooves and a portion of the O-ring deforms flat against the surface of the cylinder head and cylinder liner. Where the O-ring contacts the edges of the grooves, high contact stresses occur to provide a seal against the high pressure gas generated by the engine.

Preferably, a gas seal according to the invention comprises a cylinder liner having a groove formed in its upper plane, the wall of which extends to contact the plane of the cylinder head. When a mounting load is applied to the cylinder head, the cross-sectional thickness of the metal O-ring is compressed to the depth of the groove formed in the cylinder liner. The sealing load applied to the cylinder head is determined by the depth of the groove formed in the cylinder liner and the load deflection characteristics of the metal O-ring. Additionally, the radially outward groove wall includes a first substantially vertical portion and an inclined portion extending radially outward from the first portion. An edge is formed in between, which constitutes a radial constraint on the O-ring and ensures a reliable gas seal. Moreover, during engine operation, the thermal displacement of the cylinder head and the cylinder liner generates and increases the distance between the cylinder liner and the cylinder head. contact force between them. Since the walls of the groove formed in the cylinder liner extend to the cylinder head during assembly, thermal stress on the O-ring seal is minimized, thereby protecting the O-ring seal.

These and other advantages of the invention will become apparent from the following detailed description when the specification is read with the aid of the several drawings.

Brief description of the drawings

Fig. 1 is the top view of cylinder head gasket structure of the present invention;

Fig. 2 is a cross-sectional side view of the gas sealing device of the present invention before being compressed;

Fig. 3 is a cross-sectional side view of the gas sealing device of the present invention after being compressed;

Figure 4 is an enlarged cross-sectional side view of a gas seal including a coated O-ring in accordance with an alternate embodiment of the present invention;

Figure 5 is a cross-sectional side view of an O-ring and semi-circular groove structure according to an alternate embodiment of the present invention;

Figure 6 is a cross-sectional side view of an O-ring and rectangular groove arrangement according to an alternative embodiment of the present invention;

Figure 7 is a cross-sectional side view of a gas seal according to an alternative embodiment of the present invention wherein the cylinder liner is recessed into the cylinder block;

Figure 8 is a cross-sectional side view of a gas seal in accordance with an alternative embodiment of the present invention wherein an O-ring is seated within a root of the cylinder liner prior to being compressed;

Figure 9 is a cross-sectional side view of a gas seal according to an alternative embodiment of the present invention, wherein the O-ring of Figure 8 is seated in a groove in the cylinder liner after being compressed;

Figure 10 is a side cross-sectional view of a gas seal in accordance with a preferred embodiment of the present invention wherein an O-ring is mounted in a groove in the cylinder liner and compressed by the cylinder head.

Detailed Description of Preferred Embodiments

Referring to the drawings, the invention will now be described in terms of several alternative embodiments. The present invention is an improved gas seal for sealing the high pressures developed in an internal combustion engine by creating multiple radial contact constraints in the seal to overcome the thermal and mechanical stresses on the seal during engine operation gas.

Figure 1 shows a top view of the gas sealing device of the present invention. The gas seal 1 shown passes through the cylinder head gasket 3 which consists of a body sheet or plate with a plurality of holes, as shown in FIG. 1 . Specifically, the cylinder head gasket 3 includes a cylinder bore 2 which defines the contour of a cylinder bore within which a piston (not shown) reciprocates during engine operation. The cylinder head gasket 3 also includes cooling passages 5 , bolt holes 7 and oil passages 9 . Sealing coolant in these holes provides for securing the cylinder head to the engine (not shown) and for sealing the lubricating oil. The head gasket itself provides a seal against gas or fluid leakage during engine operation.

FIG. 2 shows a cross-sectional side view of the gas seal. This figure shows the state of each gas sealing member before the actual sealing of the engine cylinder in order to clearly illustrate the relationship among the various parts of the present invention.

Referring now to Figure 2, the gas seal 1 is made of a wire mesh ring, which is sometimes referred to as a "fire ring". The fire ring has the shape of an O-ring 4, which will be explained in the remainder of this description. The O-ring 4 seals the high-pressure gas between the surface of the cylinder head and the top surface of the cylinder liner. O-rings are subjected to high pressure gas pressure and extremely high temperatures.

Besides the O-ring 4 , the gas sealing device 1 includes a cylinder head 11 , a cylinder liner 13 , a cylinder block 15 and a cylinder head gasket 3 . The cylinder head 11 comprises a metal plate which is fastened to the cylinder block 15 by means of bolts (not shown). The cylinder block 15 is fabricated from billet metal and includes one or more cylinder barrels into which the cylinder liners 13 are mounted. The cylinder liner 13 is in frictional engagement with the cylinder block 15 so that the cylinder liner does not loosen due to the load generated by the reciprocating movement of the piston (not shown) therein or the extremely high temperature and pressure acting thereon. To achieve this frictional relationship, cylinder liner 13 may be press fit within the cylinder bore of cylinder block 15 or secured by some other means. Once installed in the cylinder block 15 , the top surface or flat surface of the cylinder liner is flush with the top surface of the cylinder block 15 . The cylinder liner comprises a metallic material, such as steel, and may be made of a different material than the cylinder block. Although the gas sealing structure is shown as having a wet cylinder liner without an upper flange, however, the above sealing concept of the present invention is also applicable to top flange wet cylinder liners, dry cylinder liners, mid-stop cylinder liners And the original cylinder block without a separate cylinder liner.

The cylinder head 11 includes an annular groove 17 formed in its bottom surface. The annular groove 17 is machined into the cylinder head and can have various geometric features, which will be discussed in detail with respect to FIGS. 4, 5 and 6. An important feature of the present invention is that the annular groove 17 made in the cylinder head is very simple. The groove can be easily machined due to the loose tolerance requirements. Additional advantages include durability since stresses generated within the cylinder head are minimal and the slots can be re-machined in use.

The cylinder liner 13 includes a complementary groove 19 machined in its top surface, similar to the annular groove 17 formed in the cylinder 11 . The annular groove 17 and the complementary groove 19 are mirror images of each other, such that the complementary groove 19 is the inverse geometry of the annular groove 17 . Furthermore, both the annular groove 17 and the complementary groove 19 are precisely aligned, and these grooves match each other when fixing the cylinder head to the cylinder block. O-rings 4 are placed between these grooves to achieve a seal therebetween. The cylinder head gasket 3 is installed between the cylinder head 11 and the cylinder body 15, and also constitutes a seal.

To form an effective gas seal to prevent high pressure gas from escaping the cylinders during engine operation, the cylinder head 11 is bolted (not shown) to the cylinder block 15 . When the cylinder head 11 is initially installed, the O-ring 4 is in line contact at the edges of the annular groove 17 and the complementary groove 19 . As load is applied to the cylinder head mounting bolts, the O-ring deforms.

O-type 4 is made of deformable material such as metal. Preferably, the O-ring 4 may comprise carbon steel, alloy steel or copper alloy. O-rings can be manufactured by one of several methods, such as forming a length of drawn wire into a torus, welding the ends together, and smoothing the wire joints to eliminate loose metal contact pieces of silk. In addition, O-rings can be fully machined from solid stock, either cold or hot worked. Preferably, the alloy from which the O-ring is made is annealed, however, any known suitable heat treatment may be used.

Referring to Fig. 3, after the cylinder head 11 is fixed on the cylinder block 15, a part of the O-ring 4 protrudes in the annular groove 17 and the complementary groove 19, and a part of the O-ring 4 is flattened and deformed against the On the first cylinder liner surface 25 of the first cylinder head surface 23 . The same deformation occurs on the opposite side of the O-ring 4, as shown in this figure. The deformation on both the head and liner surfaces acts to secure and seal the O-ring between the head and liner. This deformation also plays a role in preventing the high-pressure gas from leaking through the gas sealing device 1 .

When securing the cylinder head to the cylinder block, the O-ring is further deformed to form a gas seal. This deformation takes place at the edges of the annular groove 17 and the complementary groove 19 . Specifically, FIG. 3 shows that the deformation occurs at the first cylinder liner edge 27 , the first cylinder head edge 29 , the second cylinder liner edge 31 and the second cylinder head edge 33 . This sharp load concentration produces close contact between the gas cover 11 and the O-ring 4 and between the cylinder liner 13 and the O-ring 4, thereby forming an effective seal for the high-pressure gas. The final compressed height of the O-ring 4 may be different from the compressed thickness of the cylinder head gasket 3 . The height of deformation of the O-ring 4 depends on the size and deflection of the mating part and can vary slightly around the circumference of the O-ring 4 .

FIG. 4 shows an enlarged circular groove 17 , complementary groove 19 and O-ring 4 . Both the head and liner grooves have a triangular or concave V shape. The concave V-shaped grooves allow the O-rings 4 to deform in some way into a portion of these grooves in order to form a reliable seal between the cylinder head and cylinder liner. According to the structural relationship between the O-ring 4 , the circular groove 17 and the complementary groove 19 , the original diameter of the O-ring 4 can be in the range of 1.2 to 2 times the thickness of the cylinder head gasket 3 . For example, if the thickness of the cylinder head gasket body is 0.25 inches, the diameter of the O-ring 4 is in the range of 0.3 inches to 0.5 inches. Also, the width of the concave V-groove (measured from groove edge to edge on the cylinder head and cylinder liner faces) may be in the range of 0.3 to 1.2 times the diameter of the O-ring 4 . For example, if the diameter of the O-ring is 0.5 inches, the width of the concave V-groove is in the range of 0.15 to 0.6 inches. Furthermore, the angle 35 of the concave V-groove may be in the range of 60° to 120°. Of course, as the angle of the concave V-shaped groove increases, the aforementioned width also increases. The groove width and angular ranges provided above produce a gas seal which is able to withstand the extremely high temperatures and gas pressures acting on the seal during engine operation.

The O-ring in FIG. 4 includes a coating 37, such as metal plating or similar material, which may be applied to the O-ring to better accommodate the surface finish and improve its sealing properties. Coating 37 may include zinc plating as an inexpensive and effective plating material, however, any known material including silver may be used. The coating of the O-ring 4 is an alternative embodiment of the present invention that can be used in specific applications requiring additional properties of structural features.

In further alternative embodiments, the head and liner slots may have different shapes. Figures 5 and 6 show circular and rectangular grooves, respectively, which may be used in the present invention. These grooves can be made in the cylinder head and cylinder liner in a manner similar to the concave V-shaped grooves described above. The radius of the circular groove 39 shown in Figure 5 can be in the range of 0.3 to 0.8 times the diameter of the O-type 4, for example, if the diameter of the O-ring is 0.5 inches, the radius of the circular groove 39 can be in the range of 0.15 inches to 0.4 inches Inside. The width of the circular groove 39 measured at the groove edges of the two planes of the cylinder head and the cylinder liner should be less than twice its radius.

With respect to FIG. 6 , the width of the rectangular groove 41 measured at the groove edge of the two planes of the cylinder head and the cylinder liner is in the range of 0.3 to 1.0 times the diameter of the O-ring 4 . For example, if the diameter of the O-ring 4 is 0.5 inch, the width of the rectangular groove 41 is in the range of 0.15 inch to 0.5 inch. The depth of the rectangular groove 41 may be 0.1 to 0.3 times the diameter of the O-ring 4 . Thus, for an O-ring diameter of 0.5 inches, the depth of the rectangular groove 41 will be in the range of 0.05 inches to 0.15 inches. The grooves in the cylinder head and cylinder liner do not have to be identical. The shape and dimensions of these grooves must be selected relative to the O-ring diameter and head gasket thickness to obtain the correct deformation and contact characteristics of the present invention.

In the present invention, the top surface of the cylinder liner 13 is represented as being substantially flush with the top surface of the cylinder block 15, as shown in FIG. 2 . Figure 7 shows an alternative embodiment in which the cylinder liner 13 is recessed a predetermined amount 45 below the surface of the cylinder block. In this case, a larger diameter O-ring 4 would be used to produce different deformation characteristics. Certain application types may require large cylinder liners to be recessed into the cylinder block. This alternative provides an effective high pressure gas seal for these applications.

Another alternative embodiment of the present invention is shown in FIGS. 8 and 9 . Figure 8 shows the original loose assembled components of this embodiment, while Figure 9 shows the deformed O-ring cross-section after application of head bolt preload. The structure of this embodiment of the invention has eliminated the groove on the bottom surface of the cylinder head 50 and has only one groove 51 on the top surface of the cylinder sleeve 52 . The construction of the cylinder liner 52 is different from that of the cylinder liner of the preferred embodiment. The cylinder sleeve 52 has a structure comprising a slot 51, a first side wall 53 of the slot and a second side wall 55 of the slot, the latter being shorter and wider than the former. Although the first side wall 53 of the groove is optional in this embodiment, this element will be discussed as part of the present invention.

Another feature of this alternative embodiment discussed with respect to FIG. 8 is that the cylinder sleeve 52 is slightly offset from the cylinder block 15 where the second side wall 55 of the groove abuts the cylinder block 15 . The relationship between the top surface of the cylinder sleeve 52 and the top surface of the cylinder block 15 depends on the selection of the diameter of the O-ring, the deformation of the O-ring groove section, the depth of the cylinder liner groove and the thickness of the cylinder head gasket body. However, the dimensions of the side walls of the groove and the relationship to the cylinder block can be changed in any manner that simplifies the gas seal structure and features of the present invention.

Referring now to FIG. 9 , when a clamping load is applied, the O-ring groove cross-section becomes flattened and deforms to lean against the surface of the cylinder head 50 with interface 63 and lean against the cylinder liner groove 51 with interface 65 . The tight contact at the fit-in-place interfaces 63 and 65, combined with the radial constraint at edge point 61, provides an effective seal for the high pressure gas in this alternative embodiment. The depth of the cylinder liner groove 51 can be in the range of 0.4 to 0.9 times the diameter of the O-ring 4. For example, if the diameter of the O-ring 4 is 0.5 inches, the depth of the cylinder liner groove 51 is between 0.2 inches and 0.45 inches. between. The width of the cylinder liner groove 51 is slightly larger than the diameter of the O-ring 4 to allow the O-ring 4 to rest in the cylinder liner groove 51 without contacting the two side walls of the groove.

Referring now to Fig. 10, this has represented a priority gas sealing device of the present invention, comprises a cylinder liner 102 installed in the cylinder block 103, is shaped on a groove 104 on its upper plane 106, the two side walls 108 and 110 of groove Extends from the bottom wall 107 and contacts the face 112 of the cylinder head 114 . As in the previous embodiments, a cylinder head gasket 105 and an O-ring 116 are installed, and the O-ring 116 is installed in the groove 104 to form a gas seal around the upper periphery of the cylinder liner 102 . When an assembly load is applied to the cylinder head 114 , the thickness of the cross-section of the metal O-ring 116 is compressed to the depth of the groove 104 formed in the cylinder liner 102 . The sealing load applied to the cylinder head 114 is determined by the depth of the groove 104 formed in the cylinder liner 102 and the load deflection characteristics of the metal O-ring 116 . Additionally, the radially outward slot wall 110 includes a first substantially vertical portion 118 and an inclined portion 120 extending radially outward from the first portion. Formed therebetween is a rib 122 which provides radial restraint to the O-ring 116 and ensures a positive gas seal.

With the configuration shown in FIG. 10 , thermal displacement of the cylinder head 114 and cylinder liner 102 during engine operation creates and increases the contact force between the cylinder liner and cylinder head. When assembled, thermal stresses on the O-ring seals are minimized as the respective side wall portions 108 and 110 of the groove 104 formed by the extensions 109 and 111 of the cylinder liner 102 stretch and contact the cylinder head 114 , thereby preventing excessive deformation of the O-ring seal, which could lead to leakage of the seal.

Thus, the gas seal discussed above with respect to several embodiments provides an effective high pressure gas seal which is durable and easy to manufacture. Furthermore, in the case of the gas seal shown in Figure 10, the seal itself is protected from excessive stress due to thermal expansion of the cylinder liner and cylinder head during operation of the internal combustion engine. Accordingly, the present invention has certain features and advantages not found in the prior art sealing arrangements described above.

Industrial Applicability

Wire mesh ring seals can be used in any environment where an effective seal is primarily required. This special gas seal is even more suitable for high-pressure applications where there is a possibility of leakage. This mechanism can be applied in any environment where the main purpose is to prevent the leakage of gas or liquid at extremely high temperature and pressure.

Claims (38)

1. A gas sealing device for sealing high-pressure gas in at least one cylinder of an internal combustion engine, comprising: a cylinder block in which one or more cylinder barrels are formed; a cylinder head having a top surface and a bottom surface rigidly connected to the cylinder block and having a groove formed in its bottom surface; a cylinder liner having a top surface mounted in at least one cylinder bore formed in the cylinder body, said cylinder liner having a complementary groove formed in the top surface; a deformable metal seal, having a generally circular cross-section, positioned between a groove formed in the cylinder head and a complementary groove formed in the cylinder liner, and in contact with the edges of said groove; a cylinder head gasket positioned between the cylinder head and the cylinder block; When the cylinder head is fastened on the cylinder, the sealing device is compressed, forming a plurality of radial contact constraints with the edge, and a part of the sealing device is flattened and abuts against the cylinder head The bottom surface of the cylinder liner and the top surface of the cylinder liner have a compressed height different from the compressed thickness of the cylinder head gasket. 2. Sealing arrangement according to claim 1, characterized in that said groove formed in the cylinder head is in the shape of an inverted V and the complementary groove formed in the cylinder liner is in the shape of a V. 3. The sealing device according to claim 1, characterized in that said groove formed on the cylinder head is an inverted rectangle, and the complementary groove formed on the cylinder liner is rectangular. 4. The sealing device according to claim 1, characterized in that the groove formed on the cylinder head is an inverted semicircle, and the complementary groove formed on the cylinder liner is semicircular. 5. The sealing device of claim 1, wherein said cylinder liner is mounted lower than the top plane of the cylinder block. 6. The sealing device of claim 1, wherein said sealing device is an O-ring made of a deformable metal. 7. The sealing device of claim 6, wherein said deformable metal comprises at least one of carbon steel, alloy steel and copper alloy. 8. The sealing device of claim 7, wherein said deformable metal is heat-treated. 9. The sealing device of claim 6, further comprising a cylinder head gasket mounted between the cylinder head and the cylinder block. 10. The sealing device according to claim 9, characterized in that the diameter of the sealing device is in the range of 1.2 to 2.0 times the thickness of the cylinder head gasket. 11. The sealing device of claim 2, wherein said V-groove and inverted V-groove comprise an angle of 60° to 120°. 12. The sealing device of claim 1, wherein the shape of the groove on the cylinder head is different from the shape of the groove on the cylinder liner. 13. The seal of claim 6, wherein said O-ring includes an outer coated core. 14. The sealing device of claim 13, wherein the outer coating is a metal coating. 15. A gas sealing device for sealing high-pressure gas in at least one cylinder of an internal combustion engine, comprising: a cylinder block in which one or more cylinder barrels are formed; a cylinder head having a top surface and a bottom surface rigidly connected to the cylinder block; a cylinder head gasket, which is installed between the cylinder block and the cylinder head to enhance the seal therebetween; A cylinder liner having a top surface press fit into at least one cylinder bore formed in the cylinder block, said cylinder liner having a groove on its top surface, said groove having a first side wall and a second side wall, the height of the latter is greater than the height of the latter, and the second side wall is against the cylinder body and deviates from the cylinder body; a metal O-ring seated in a groove formed on the cylinder liner and abutting against the second side wall of the groove; When the cylinder head is fastened on the cylinder, the O-rings are compressed, forming at least a three-point seal. 16. The seal of claim 15 wherein said O-ring comprises a deformable metal. 17. The sealing device of claim 16, wherein said deformable metal comprises at least one of carbon steel, alloy steel and copper alloy. 18. The sealing device of claim 16, wherein said deformable metal is heat treated. 19. The sealing device of claim 15, wherein the diameter of the O-ring is 1.2 to 2.0 times the thickness of the cylinder head gasket. 20. The seal of claim 15 wherein said O-ring includes an outer coated core. 21. The sealing device of claim 20, wherein said outer coating is a metal coating. 22. A gas sealing device for sealing high-pressure gas in at least one cylinder of an internal combustion engine, comprising: a cylinder block in which one or more cylinder barrels are formed; a cylinder head having a top surface and a bottom surface rigidly connected to the cylinder block; a cylinder head gasket installed between the cylinder block and the cylinder head to enhance the seal therebetween; A cylinder liner having a top surface press fit into at least one cylinder bore formed in the cylinder block, said cylinder liner having a groove in its top surface, said groove having a second side of a first side wall wall, the second sidewall is located radially outward of the first sidewall and has a first substantially vertical portion and a second inclined portion; a metal O-ring seated in a groove formed on the cylinder liner, said O-ring abutting at least one of the side walls of said groove; When the cylinder head is fastened to the cylinder, the O-rings are compressed, forming at least a three-point seal. 23. The seal of claim 21 wherein said O-ring comprises a deformable metal. 24. The sealing device of claim 23, wherein said deformable metal comprises at least one of carbon steel, alloy steel and copper alloy. 25. The sealing device of claim 24, wherein said deformable metal is heat treated. 26. The sealing device of claim 22, wherein the diameter of the O-ring is 1.2 to 2.0 times the thickness of the cylinder head gasket. 27. The seal of claim 22, wherein said O-ring includes an outer coated core. 28. The sealing device of claim 27, wherein said outer coating is a metal coating. 29. The seal of claim 22, further comprising a peripheral edge between the first section and the second section of the second side wall. 30. The seal of claim 22 wherein one of said three points of contact is between said O-ring and said edge. 31. The sealing device of claim 22, wherein the top surface of the cylinder liner is in contact with the bottom surface of the cylinder head. 32. The sealing arrangement of claim 31 wherein said groove divides the top surface of the cylinder liner into first and second portions. 33. The sealing arrangement of claim 32 wherein said first and second portions of said top surface are in contact with the cylinder head. 34. The seal of claim 22 wherein said second portion is angled radially outwardly relative to the first portion. 35. In an internal combustion engine, a gas sealing device for sealing high-pressure gas, comprising: an inner core having a generally circular cross-section, said inner core being made of a first deformable metallic material; an outer coating, made of a different material than the inner core; The outer coating is adapted to a part of the internal combustion engine to seal the gas. 36. The seal of claim 35, wherein said deformable metal comprises at least one of carbon steel, alloy steel and copper alloy. 37. The sealing device of claim 36, wherein said deformable metal is heat treated. 38. The sealing device of claim 35, wherein said outer coating is a metal coating.

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