Rolling-sliding linkage friction piston ring and internal combustion engine

Abstract

The invention discloses a rolling and sliding linkage friction piston ring and an internal combustion engine, the piston ring comprises an elastic piston ring body, the outer circle working face of the piston ring body is provided with ball grooves or ball holes which are distributed in the annular direction, and balls are embedded in the ball grooves or the ball holes; and parts of the balls are flush with the outer circular surface of the ring body and are used for being in contact with the cylinder sleeve to form rolling-sliding linkage friction. According to the scheme, the elastic arrangement mode of the ring body of the piston ring guarantees the structural strength and elasticity of the piston ring, the ring body can be tightly attached to the cylinder sleeve, and therefore the beneficial effects of stably achieving the core functions of gas sealing and heat transferring are achieved, and basic guarantee is provided for the power output efficiency of an internal combustion engine. Besides, hard contact and local stress concentration of traditional pure sliding friction are avoided through a rolling and sliding linkage friction mode formed by the balls and the cylinder sleeve, and meanwhile, the beneficial effects of reducing the adhesive abrasion risk and prolonging the service life of the piston ring and the cylinder sleeve are achieved by matching with the rolling characteristic of the balls.

Description

TECHNICAL FIELD

[0001] The present application generally relates to the technical field of key components of internal combustion engines. More particularly, the present application relates to a rolling and sliding linkage friction piston ring; further, the present application also provides an internal combustion engine. BACKGROUND

[0002] As the core power source of large mechanical equipment such as railway locomotives, shipping vessels, engineering equipment, and generator sets, the performance of internal combustion engines directly determines the operating efficiency and reliability of the main equipment. With the upgrading of power demand in the industrial field, heavy-duty high-power low-speed internal combustion engines are widely used. Such internal combustion engines generally have the characteristics of high strengthening coefficient, high explosion pressure, high average effective pressure, and large single-cylinder power. For example, the explosion pressure of some new medium-speed diesel engines has reached 23 MPa, the average effective pressure is more than 2.7 MPa, and the strengthening coefficient is as high as 35 MPa m / s, far exceeding the performance indicators of traditional internal combustion engines. At the same time, to meet the increasingly stringent emission regulations, new technologies such as high-pressure combustion, fuel multi-point injection, and EGR exhaust gas recirculation are gradually introduced, further intensifying the working load of internal combustion engine core components.

[0003] As a key vulnerable part of internal combustion engines, the piston ring bears the core functions of sealing gas, transferring heat, supporting the piston, and uniformly distributing oil, and its working state directly affects the power output, fuel consumption, and service life of the internal combustion engine. Under the above high load and high strengthening conditions, the traditional piston ring faces severe technical challenges.

[0004] Firstly, the traditional piston ring adopts pure sliding friction form to cooperate with the cylinder sleeve, and its friction coefficient is relatively high. The higher friction resistance not only causes a large amount of power loss, but also causes a large amount of heat on the friction surface, which aggravates the deterioration of lubricating oil. Secondly, high explosion pressure and high mechanical load significantly increase the local stress of the friction surface of the piston ring and the cylinder sleeve. The surface contact form of pure sliding friction easily causes the oil film of the friction surface to break, causing adhesive wear between the piston ring and the cylinder sleeve, and even causing the cylinder to be pulled out in severe cases, directly shortening the service life of the piston ring and the cylinder sleeve.

[0005] Therefore, it is a technical problem to be solved in the field of internal combustion engine components to develop a piston ring structure that can break through the limitations of traditional design in terms of friction form, and has low friction coefficient, high wear resistance, and stable sealing effect.

[0006] Therefore, it is a technical problem to be solved in the field of internal combustion engine components to develop a piston ring structure that can break through the limitations of traditional design in terms of friction form, and has low friction coefficient, high wear resistance, and stable sealing effect. SUMMARY

[0007] In order to at least solve one or more technical problems as mentioned above, the present application proposes a rolling and sliding linkage friction piston ring and an internal combustion engine scheme in multiple aspects to reduce frictional resistance.

[0008] In a first aspect, the present application provides a rolling and sliding linkage friction piston ring, comprising an elastic piston ring body, an outer circular working surface of the piston ring body is provided with a rolling ball groove or a rolling ball hole arranged in a ring direction, and a rolling ball is embedded in the rolling ball groove or the rolling ball hole; part of the rolling ball is flush with the outer circular surface of the ring body, and is used to contact a cylinder liner to form rolling and sliding linkage friction.

[0009] In some embodiments, the rolling ball groove or the rolling ball hole is provided with at least one groove in a height direction of the piston ring body; and the particle size of the rolling ball arranged in each groove in the height direction is the same or in a step distribution.

[0010] In some embodiments, the rolling ball is directly installed or installed through an elastic element in the rolling ball groove or the rolling ball hole, wherein the elastic element is a spring.

[0011] In some embodiments, the rolling ball groove or the rolling ball hole stores lubricating oil or lubricating grease, and can accommodate abrasive particles generated in a friction process.

[0012] In some embodiments, an inner wall of the rolling ball groove or the rolling ball hole is provided with a microporous oil storage structure, and the microporous oil storage structure is filled with engine lubricating grease or phase change lubricating material.

[0013] In some embodiments, the phase change lubricating material is a paraffin-based composite phase change material or a polymer gel phase change material, which releases lubricating oil when a solid-liquid phase change occurs at a predetermined temperature.

[0014] In some embodiments, a material of the piston ring body is selected from one of vermicular graphite cast iron, nodular graphite cast iron, alloy cast iron or steel material.

[0015] In some embodiments, a material of the rolling ball is selected from one of high-carbon chromium bearing steel, ceramic, stainless steel or carburizing bearing steel.

[0016] In some embodiments, a particle size of the rolling ball is 0.1 mm to 10 mm.

[0017] In some embodiments, a diameter of the piston ring ranges from 50 mm to 1000 mm.

[0018] In some embodiments, an outer circular surface of the piston ring body and / or a spherical surface of the rolling ball is subjected to surface strengthening treatment, and the surface strengthening treatment includes at least one of electroplating, spraying, laser cladding and vapor deposition.

[0019] In a second aspect, the application provides an internal combustion engine comprising the rolling and sliding linkage friction piston ring described above.

[0020] By the rolling and sliding linkage friction piston ring provided as above, by setting the piston ring body into an elastic form, the structural strength and elasticity of the ring body are ensured, so that the ring body can be tightly attached to the cylinder liner, thereby achieving the beneficial effect of stably realizing the core functions of sealing fuel gas and transferring heat, providing basic guarantee for the power output efficiency of the internal combustion engine. In addition, the scheme of the application avoids the hard contact and local stress concentration of traditional pure sliding friction through the rolling and sliding linkage friction form formed by the rolling ball and the cylinder liner, and cooperates with the rolling characteristics of the rolling ball, thereby achieving the beneficial effect of reducing the risk of adhesive wear and prolonging the service life of the piston ring and the cylinder liner. BRIEF DESCRIPTION OF DRAWINGS

[0021] The above and other objects, features and advantages of the example embodiments of the present application will be more apparent from the following detailed description taken in conjunction with the accompanying drawings, in which several embodiments of the present application are shown by way of example, and wherein like or corresponding elements show like or corresponding parts, by referring to which; and in which: Fig. 1 A structure diagram showing the rolling ball groove provided on the piston ring body in the present application is shown; Fig. 2 A structure diagram showing the rolling ball hole provided on the piston ring body in the present application is shown; Fig. 3 A structure diagram showing the rolling and sliding linkage friction piston ring and the cylinder liner combination in the present application is shown.

[0022] 1, piston ring body; 2, rolling ball; 3, cylinder liner. DETAILED DESCRIPTION

[0023] The technical solutions in the embodiments of the present application will be described clearly and completely below by referring to the drawings in the embodiments of the present application. Obviously, the described embodiments are part of the embodiments of the present application, rather than all the embodiments of the present application. Based on the embodiments in the present application, all other embodiments obtained by those skilled in the art without creative labor fall within the scope of protection of the present application.

[0024] It should be understood that the terms "include" and "contain" used in the specification and claims of the present application indicate the presence of the described features, whole, steps, operations, elements and / or components, but do not exclude the presence or addition of one or more other features, whole, steps, operations, elements, components and / or sets thereof.

[0025] It is also to be understood that the terminology used herein is for the purpose of describing particular embodiments only and is not intended to be limiting. As used in this specification and in the claims, the singular forms "a," "an," and "the" include plural referents unless the context clearly dictates otherwise. It will be further understood that the terms "comprises" and / or "comprising," when used in this specification, specify the presence of stated features, integers, steps, operations, elements, and / or components, but do not preclude the presence or addition of one or more other features, integers, steps, operations, elements, components, and / or groups thereof. It will be further understood that the terms "comprises" and / or "comprising," when used in this specification, specify the presence of stated features, integers, steps, operations, elements, and / or components, but do not preclude the presence or addition of one or more other features, integers, steps, operations, elements, components, and / or groups thereof.

[0026] As used in this specification and claims, the terms "if' and "when" can each be interpreted to mean "upon a determination" or "in response to a determination" or "in response to detecting," as appropriate, depending on the context.

[0027] The specific embodiments of the present application will now be described in detail with reference to the accompanying drawings.

[0028] As Figs. 1-3 shown in some embodiments, the present application provides a rolling and sliding linkage friction piston ring, including an elastic piston ring body 1, the outer circular working surface of the piston ring body 1 is provided with a rolling ball groove or rolling ball hole arranged along the ring, and a rolling ball 2 is embedded in the rolling ball groove or the rolling ball hole; part of the rolling ball 2 is flush with the outer circular surface of the ring body, used to contact the cylinder liner 3 to form rolling and sliding linkage friction.

[0029] In the scheme of the present application, the rolling and sliding linkage friction piston ring includes an elastic piston ring body, which is a circular ring structure with an opening. The elastic piston ring body can be closely attached to the cylinder liner 3 on the basis of ensuring its own structural strength and relying on its elastic properties, laying a foundation for sealing and heat transfer functions. On the outer circular working surface of the piston ring body 1, a rolling ball groove or a rolling ball hole is uniformly or non-uniformly arranged along the ring, serving as an installation and movement carrier for the rolling ball 2. The rolling ball groove adopts a ring-shaped groove design, and the groove width and groove depth are adapted to the size of the rolling ball 2 to ensure that the rolling ball 2 is stable and does not fall off after installation. The rolling ball hole is a precisely machined circular hole, which is reasonably distributed along the circumference of the ring body to ensure balanced stress. A plurality of rolling balls 2 are correspondingly embedded in the rolling ball groove or the rolling ball hole, and part of the rolling ball 2 is flush with the outer circular surface of the ring body. When the piston ring reciprocates in the cylinder liner 3, the rolling ball 2 flush with the outer circular surface directly contacts the inner wall of the cylinder liner 3 and forms rolling and sliding linkage friction, while the piston ring body 1 relies on its own elastic force to closely attach to the cylinder liner 3 to form sliding friction. Through the linkage friction form of rolling plus sliding, the functions of friction reduction, wear resistance and sealing are synergistically optimized.

[0030] The solution in this application, by making the piston ring body 1 elastic, ensures the structural strength and elasticity of the ring body, allowing it to fit tightly against the cylinder liner 3. This achieves the beneficial effect of stably sealing the combustion gases and transferring heat, providing a fundamental guarantee for the power output efficiency of the internal combustion engine. Furthermore, the solution in this application, through the rolling and sliding linkage friction formed by the piston ring body 1, the ball bearing 2, and the cylinder liner 3, avoids the hard contact and localized stress concentration of traditional pure sliding friction. Simultaneously, combined with the rolling characteristics of the ball bearing 2, it achieves the beneficial effects of reducing the risk of adhesive wear and extending the service life of the piston ring and cylinder liner 3.

[0031] In some specific implementations, at least one ball groove or ball hole is provided along the height direction of the piston ring body 1; along the height direction, the ball 2 provided in each ball groove or ball hole has the same particle size or is distributed in a stepped manner.

[0032] In this application, to further adapt to the load changes and bearing requirements under complex working conditions such as heavy-duty high-power internal combustion engines, at least one ball groove or ball hole is provided along the height direction of the piston ring body 1. When multiple grooves or holes are provided, the multiple grooves or holes are evenly or non-uniformly distributed along the height direction of the ring body, which not only ensures the integrity and mechanical stability of the ring body structure, but also disperses the local load of the friction surface through multi-point rolling support, avoiding the stress concentration problem that may occur in a single groove or hole structure.

[0033] Of course, those skilled in the art will understand that in actual production, the number of ball grooves or ball holes is selected based on the height of the piston ring body. That is, when the piston ring height is small, only one groove is set, while when the piston ring height is large, multiple grooves can be set.

[0034] Furthermore, considering the load differences experienced by the piston rings during different stroke stages (intake, compression, power, and exhaust strokes) as they reciprocate within the cylinder liner 3, the diameter of the balls 2 in each ball groove or ball hole along the ring height direction can be flexibly configured in two ways. One method involves all balls 2 in each ball groove or ball hole having the same diameter. This configuration simplifies the machining and assembly process, ensuring that the load is evenly distributed among the balls 2, and is suitable for conditions with relatively balanced load distribution. The other method involves all balls 2 in each ball groove or ball hole having a different diameter; that is, along the ring height direction, the ball 2 diameter increases with the contact load of the corresponding stroke stage. For example, larger diameter balls 2 can be placed in the groove corresponding to the stroke range with the highest burst pressure, while smaller diameter balls 2 can be placed in the range with lower load. This precise matching achieves force balance among the balls 2, further improving the piston ring's impact resistance and service life. In another specific implementation, the diameter of all the balls 2 in each ball groove or ball hole is different. That is, along the circumferential direction of the ring, the diameter of the balls 2 increases with the increase of the radial pressure on the corresponding circumference. For example, in the high-point ring, large-diameter balls 2 are set in the groove corresponding to the opening section with the greatest radial pressure, and small-diameter balls 2 are set in the section with less radial pressure. This precise matching achieves the force balance of each ball 2, further improving the impact resistance and service life of the piston ring.

[0035] The solution in this application increases the rolling contact points between the balls 2 and the cylinder liner 3 by setting at least one ball groove or ball hole, thus dispersing the local load on the friction surface and avoiding stress concentration on the working surface of the piston ring in pure sliding friction. This achieves the beneficial effects of improving the overall load-bearing capacity of the piston ring and enhancing the structural mechanical stability. In addition, the solution in this application uses a stepped distribution of the ball size 2 in each ball groove or ball hole along the height of the ring, or different ball sizes along the circumference of the piston ring. This allows the ball size 2 to be precisely matched with the load changes at different stroke stages of the piston ring, thereby achieving balanced force on each ball 2 and improving the piston ring's impact resistance and adaptability to operating conditions.

[0036] In some specific implementations, the ball 2 is mounted in the ball groove or the ball hole by an elastic element, which is a spring.

[0037] In this application, to further optimize the contact fit between the ball bearing 2 and the cylinder liner 3, and to improve the stability and impact resistance of the piston ring under complex working conditions, the ball bearing 2 is installed in the ball groove or ball bore using an elastic element. Specifically, the elastic element can be a spring, and its installation position is adapted to the groove structure and the size of the ball bearing 2. When the piston ring body has a ball groove, the elastic element is continuously arranged circumferentially along the groove. When the piston ring body has a ball bore, each bore is equipped with an independent elastic element to ensure precise support for a single ball bearing 2.

[0038] Those skilled in the art will understand that when the elastic element is a spring, a compression spring or a wave spring is preferred, with one end abutting against the inner wall of the slot and the other end contacting the ball 2. By utilizing the elastic deformation characteristics of the spring, a continuous and adjustable preload is provided to the ball 2.

[0039] During use, when there are slight irregularities on the surface of the cylinder liner 3 or when the piston ring is subjected to instantaneous impact loads, the elastic element can compensate for the displacement by contracting or relaxing, ensuring that the ball 2 always maintains stable contact with the cylinder liner 3, and avoiding contact separation or local overload. In addition, the elastic support can also buffer the vibration generated during the rolling of the ball 2, reduce noise and wear, and further extend the service life of the ball 2 and the ring body.

[0040] In one specific implementation, the ball groove or the ball hole stores lubricating oil or grease, and the ball groove or the ball hole is capable of accommodating abrasive particles generated during friction.

[0041] In this application, lubricating oil or grease is pre-stored in the ball groove or ball bore. The structural design of the ball groove or ball bore fully considers the dual needs of oil storage and chip removal. That is, the depth, width, and clearance between the ball groove or ball bore and the ball 2 are precisely calculated to ensure that the lubricating oil or grease can be stably retained in the clearance, avoiding excessive loss due to the rapid reciprocating motion of the piston ring, while also not affecting the normal rolling of the ball 2. When the piston ring moves with the piston in the cylinder liner 3, the ball 2, together with the ring body 1, replenishes the lubricating oil from the lubrication system to the cylinder liner wall into the ball groove or ball bore. At the same time, the rolling of the ball 2 continuously and evenly carries out the lubricating oil or grease stored in the groove or ball bore, forming a stable and continuous oil film on the friction surface between the piston ring body 1 and the cylinder liner 3. This effectively fills the oil film gaps that are prone to occur in traditional sliding friction, significantly reducing the risk of adhesive wear.

[0042] Meanwhile, the extra space reserved inside the ball groove or ball hole can directly accommodate metal abrasive particles, impurities and other contaminants brought by the lubrication system and intake system and generated during the friction process, avoiding the abrasive particles from forming a grinding effect between the piston ring and cylinder liner 3, and fundamentally reducing the damage of abrasive wear to the friction surface.

[0043] The solution provided in this paper eliminates the need for additional oil reservoirs or filters. While simplifying the overall structure, it achieves a synergistic effect of enhanced lubrication and control of wear sources, further extending the service life of piston rings and cylinder liners 3.

[0044] In some specific implementations, the inner wall of the ball groove or ball hole is provided with a microporous oil storage structure, which is filled with engine lubricating grease or a phase change lubricating material. The phase change lubricating material is a paraffin-based composite phase change material or a polymer gel phase change material, which undergoes a solid-liquid phase change at a predetermined temperature to release lubricating oil.

[0045] In this application, to further upgrade the lubrication protection system and achieve long-term lubrication that adapts to temperature changes, a microporous oil storage structure is added to the inner wall of the ball groove or ball bore. This microporous oil storage structure is prepared using processes such as laser drilling, chemical etching, or powder metallurgy sintering to form densely distributed micron-sized pores. The pore diameter is controlled between 1-10 μm, and the porosity is designed to be 30%-50%, ensuring that the structural strength does not affect the bearing capacity of the groove and pores while maximizing the storage of lubricating medium.

[0046] Furthermore, the microporous oil storage structure in this solution can be filled with engine lubricating grease or phase change lubricating material. The phase change temperature of the phase change lubricating material in this solution has been precisely selected to closely match the normal operating temperature range of the engine; specifically, paraffin-based composite phase change materials or polymeric gel phase change materials are chosen. Those skilled in the art will understand that paraffin-based composite phase change materials have advantages such as high latent heat of phase change, excellent thermal conductivity, and controllable cost, while polymeric gel phase change materials have better structural stability and leak-proof performance, allowing for flexible selection based on engine operating conditions.

[0047] During use, when the engine starts, as the cylinder temperature gradually rises and reaches the predetermined phase change temperature of the phase change lubricant, the material transforms from a solid to a liquid state, releasing the internally stored lubricating oil. This lubricating oil continuously replenishes the contact interface between the ball bearing 2 and the inner wall of the slot, and between the ball bearing 2 and the cylinder liner 3, through the permeation effect of the microporous structure, forming a durable and stable lubricating film. When the engine stops and the temperature drops below the phase change temperature, the phase change lubricant re-solidifies, adsorbing and storing the unconsumed lubricating oil in the microporous structure to prevent its loss or deterioration. The microporous oil storage structure and phase change oil release intelligent lubrication design provided in this application can realize the on-demand release and circulation storage of lubricating medium without additional power drive, further improving the wear resistance and long-term stability of piston rings, and is especially suitable for extreme working conditions of heavy-duty high-power internal combustion engines with frequent start-stop and large temperature fluctuations.

[0048] In some specific embodiments, the piston ring body 1 is made of a material selected from vermicular graphite cast iron, ductile iron, alloy cast iron, or steel. The diameter of the piston ring ranges from 50 to 1000 mm.

[0049] In this application, to ensure that the piston rings can adapt to the operating conditions of various power internal combustion engines in different scenarios, the core basic parameters of the piston rings have been scientifically adapted and designed. Specifically, the material of the piston ring body 1 is selected from one of the following: vermicular graphite cast iron, ductile iron, alloy cast iron, or steel. Vermicular graphite cast iron has excellent heat resistance and thermal conductivity; ductile iron has high strength and good toughness; alloy cast iron achieves better wear resistance and corrosion resistance through alloying elements; and steel, with its high strength and good machinability, is suitable for extreme heavy-load scenarios. The flexible selection of different materials can accurately match the operating temperature, load intensity, and media environment of different engines. At the same time, the diameter range of the piston rings is set from 50 to 1000 mm, covering various specifications from small power equipment to large ships and engineering equipment internal combustion engines.

[0050] The material selection of the piston ring body 1 in this application not only ensures the structural elasticity and elasticity of the piston ring body 1, enabling stable and tight fit with the cylinder liner 3, and guaranteeing sealing and heat transfer functions, but also improves the fatigue resistance and service life of the ring body through precise matching of material and working conditions, avoiding premature damage caused by improper material selection.

[0051] In some specific embodiments, the material of the ball bearing 2 is selected from high-carbon chromium bearing steel, ceramic, stainless steel, or carburized bearing steel. The particle size of the ball bearing 2 is 0.1 mm to 10 mm.

[0052] In this application, the material of the ball bearing 2 is selected from high-carbon chromium bearing steel, ceramic, stainless steel, or carburized bearing steel. High-carbon chromium bearing steel possesses high hardness, high wear resistance, and excellent contact fatigue strength, making it the preferred material for general operating conditions. Ceramic materials are lightweight, heat-resistant, and have an extremely low coefficient of friction, making them suitable for high-end high-temperature applications. Stainless steel exhibits outstanding corrosion resistance, making it suitable for humid or corrosive environments containing chemical media. Carburized bearing steel combines high surface hardness with high core toughness, enabling it to withstand heavy-load impact conditions. Furthermore, the ball bearing 2's particle size is set from 0.1mm to 10mm, allowing for flexible adjustment based on the piston ring geometry, load-bearing capacity, and movement speed.

[0053] This solution ensures that the ball 2 has sufficient strength, wear resistance and environmental adaptability under corresponding working conditions by selecting the material of the ball 2, and avoids premature wear, breakage or corrosion of the ball 2 due to material mismatch, thus providing a core guarantee for the stable realization of the rolling and sliding linkage friction mode.

[0054] In some specific embodiments, the outer circular surface of the piston ring body 1 and / or the spherical surface of the ball 2 are subjected to surface strengthening treatment, the surface strengthening treatment including at least one of electroplating, spraying, laser cladding, and vapor deposition.

[0055] In this application, in order to further improve the wear resistance, corrosion resistance and overall service life of the piston ring to adapt to the extreme working conditions of heavy-duty high-power internal combustion engines, the outer circular surface of the piston ring body 1 is subjected to surface strengthening treatment. The strengthening process adopted includes at least one of electroplating, spraying, laser cladding and vapor deposition.

[0056] Those skilled in the art will understand that electroplating processes (such as electroplating hard chrome and chromium-based ceramic coatings) can rapidly form high-hardness, wear-resistant layers; the processes are mature and cost-controllable. Spraying processes (such as spraying molybdenum-based alloys and molybdenum-based ceramic coatings) can significantly improve surface wear resistance and high-temperature resistance. Laser cladding processes can prepare metal-ceramic coatings with extremely high bonding strength to the substrate, exhibiting excellent impact resistance and wear resistance. Vapor deposition processes (such as preparing DLC ​​diamond-like carbon coatings) can achieve a perfect combination of ultra-low friction coefficient and ultra-high hardness, making them suitable for high-end precision applications.

[0057] This solution significantly improves the hardness, wear resistance, and corrosion resistance of the outer surface of the piston ring and the spherical surface of the ball 2 by strengthening the surface of the piston ring body and the ball 2. This effectively resists adhesive wear and abrasive wear during friction, and avoids surface oxidation or corrosion caused by high temperature and high pressure conditions, significantly extending the service life of the piston ring and the ball 2. Secondly, the flexible selection and combination of different strengthening processes allows for precise performance matching according to specific operating conditions, meeting the cost-effectiveness requirements of general scenarios while adapting to special environments such as extreme high temperatures, heavy loads, and corrosion, further broadening the product's application range. Furthermore, the strengthened coating optimizes the friction and wear of the friction interface and the lubrication performance, reducing energy loss during the rolling-sliding linkage friction process. Combined with the core structure of the rolling-sliding linkage, this further reduces the overall friction coefficient and improves the engine's power output efficiency. Finally, the strengthened surface structure is more stable, reducing vibration and noise during friction, while also reducing wear on the cylinder liner 3 surface, indirectly extending the service life of the cylinder liner 3, providing dual protection for the long-term stable operation of the internal combustion engine.

[0058] It is worth noting that, to fully verify the core performance advantages of the rolling-sliding linkage friction piston ring of this invention, targeted tests were conducted. The tests used a cast iron cylinder liner 3 as the mating part, simulating the actual working conditions of a heavy-duty, high-power internal combustion engine for comparative verification. Test results show that the friction coefficient between the piston ring of this invention and the cast iron cylinder liner 3 is only about 0.02, while the friction coefficient of a traditional piston ring under the same test conditions is about 0.1. Compared to traditional products, the friction coefficient of this invention is significantly reduced. Simultaneously, a specific inspection of the piston ring wear was conducted after the test. The results showed that the working surface of the piston ring of this invention had no obvious wear marks and no quantifiable wear phenomena, while the traditional piston ring showed obvious wear marks. This test data fully confirms that, through the structural innovation of rolling-sliding linkage, this invention not only achieves a significant reduction in the friction coefficient but also fundamentally improves the wear resistance of the piston ring, effectively meeting the high-load, long-cycle operation requirements of heavy-duty, high-power internal combustion engines.

[0059] In one specific embodiment, this application provides an internal combustion engine that includes the aforementioned rolling-sliding friction piston rings.

[0060] This application provides an internal combustion engine that integrates the aforementioned rolling-sliding linkage friction piston rings. This deeply adapts the innovative piston ring structure to the power requirements of the internal combustion engine, forming a power system with synergistically optimized performance. This internal combustion engine covers various types, including diesel engines for railway locomotives, low-speed diesel engines for shipping vessels, high-power internal combustion engines for engineering equipment, and generator set power engines. It is particularly suitable for heavy-duty operating conditions with high intensification coefficients, high burst pressure, and high mean effective pressure.

[0061] The integrated application of rolling-slip friction piston rings brings significant improvements to internal combustion engines in several aspects. Specifically, the ultra-low coefficient of friction of the piston rings greatly reduces frictional losses during engine operation, reduces energy waste during power transmission, and significantly improves the power output efficiency of the engine, enabling higher power output with the same fuel consumption. Furthermore, the excellent wear resistance of the piston rings extends their service life while reducing wear on the cylinder liner, lowering the replacement frequency of the piston rings (a vulnerable component), significantly reducing maintenance costs and downtime, and enhancing the continuous operation capability of the internal combustion engine.

[0062] While numerous embodiments of this application have been shown and described herein, it will be apparent to those skilled in the art that such embodiments are provided by way of example only. Many modifications, alterations, and alternatives will arise for those skilled in the art without departing from the spirit and intent of this application. It should be understood that various alternatives to the embodiments of this application described herein may be employed in the practice of this application. The appended claims are intended to define the scope of protection of this application and therefore cover equivalents or alternatives within the scope of these claims.

Claims

1. A rolling-sliding linkage friction piston ring, characterized in that, The piston ring includes an elastic piston ring body (1), the outer working surface of which is provided with ball grooves or ball holes arranged in the circumferential direction, and balls (2) are embedded in the ball grooves or ball holes; a portion of the balls (2) is flush with the outer surface of the ring body and is used to contact the cylinder liner (3) to form rolling and sliding friction.

2. The rolling-sliding linkage friction piston ring according to claim 1, characterized in that, The ball groove or ball hole is provided at least once along the height direction of the piston ring body (1); Along the height direction, the ball (2) provided in each ball groove or ball hole has the same particle size or is distributed in a stepped manner.

3. The rolling-sliding linkage friction piston ring according to claim 1 or 2, characterized in that, The ball (2) is directly installed or installed in the ball groove or the ball hole by means of an elastic element, wherein the elastic element is a spring.

4. The rolling-sliding linkage friction piston ring according to claim 1 or 2, characterized in that, The ball groove or the ball hole contains lubricating oil or grease, and the ball groove or the ball hole can accommodate abrasive particles generated during friction.

5. The rolling-sliding linkage friction piston ring according to claim 1 or 2, characterized in that, The inner wall of the ball groove or ball hole is provided with a microporous oil storage structure, which is filled with engine lubricating grease or a modified lubricating material.

6. The rolling-sliding linkage friction piston ring according to claim 5, characterized in that, The phase change lubricating material is a paraffin-based composite phase change material or a polymer gel phase change material, which undergoes a solid-liquid phase change at a predetermined temperature to release lubricating oil.

7. The rolling-sliding linkage friction piston ring according to claim 1, characterized in that, The piston ring body (1) is made of one of the following materials: vermicular graphite cast iron, ductile iron, alloy cast iron, or steel.

8. The rolling-sliding linkage friction piston ring according to claim 1, characterized in that, The material of the ball (2) is selected from one of high carbon chromium bearing steel, ceramic, stainless steel or carburized bearing steel.

9. The piston ring according to claim 1, characterized in that, The diameter of the ball (2) is 0.1 mm to 10 mm.

10. The rolling-sliding linkage friction piston ring according to claim 1, characterized in that, The diameter of the piston rings ranges from 50 to 1000 mm.

11. The rolling-sliding linkage friction piston ring according to claim 1, characterized in that, The outer circular surface of the piston ring body (1) and / or the spherical surface of the ball (2) are subjected to surface strengthening treatment, the surface strengthening treatment including at least one of electroplating, spraying, laser cladding and vapor deposition.

12. An internal combustion engine, characterized in that, It includes the rolling-sliding linkage friction piston ring as described in any one of claims 1-11.

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