A piston ring groove and ring land structure

Abstract

This utility model discloses a piston ring groove and ring land structure, which is disposed on the piston. The piston head has a first ring groove and a second ring groove arranged sequentially from top to bottom. A ring land is formed between the first and second ring grooves. A row of first oil storage holes is arranged at the same radial spacing at the center of the outer circumference of the ring land. A row of second oil storage holes is arranged at the same radial spacing on the outer circumference of the ring land near the second ring groove. The first and second oil storage holes are arranged in a staggered manner. This utility model uses equidistant circular and arc-shaped oil storage holes to buffer engine oil and reduce turbulence, thereby reducing downward combustion gas pressure and temperature, optimizing lubrication performance, reducing wear, and improving engine efficiency and lifespan. Simultaneously, the addition of baffles and staggered openings within the ring groove ensures sealing, and the upper inner ring and lower outer ring are stabilized by a retainer to prevent rotation caused by vibration, ensuring airtightness. The air passage formed within the ring groove controls the amount of combustion gas leakage and ensures the continuous circulation and renewal of engine oil.

Description

Technical Field

[0001] This utility model relates to the field of engine piston technology, specifically a piston ring groove and ring land structure. Background Technology

[0002] One of the main problems currently facing existing internal combustion engine pistons is insufficient airtightness between the piston and cylinder. The piston's multiple compression rings and oil rings all leak to varying degrees, leading to insufficient cylinder pressure, reduced combustion efficiency, excessive oil entering the combustion chamber, and excessive combustion gases leaking into the crankcase. Under low cylinder pressure, oil participates in combustion, and the resulting carbon black and gum adhere to form carbon deposits. These carbon deposits contaminate the entire engine cavity. Carbon deposits adhering to the ring grooves and ring bodies cause cylinder scoring; carbon deposits adhering to the crankshaft and eccentric shaft block oil passages, leading to crankshaft seizure. Unburned combustion gases pollute the environment and increase fuel consumption.

[0003] The first compression ring groove and compression ring of the piston are key to blocking the downward flow of combustion gas. The existing compression ring's flat-cut opening design results in a large amount of combustion gas leakage, which causes the piston head to be excessively scavenged, leading to insufficient and uneven oil distribution. Furthermore, the oil is excessively sheared due to vaporization at high temperatures, severely reducing the oil's lubricating performance, increasing oil consumption, and aggravating the wear of various moving parts of the engine.

[0004] Some existing designs improve the first piston ring, enhancing its airtightness, but fail to achieve the same level of oil circulation and lubrication. Because they only consider complete sealing without setting a flow guiding structure, the oil is trapped in the piston head and cannot flow back and renew itself, reducing lubrication, shortening oil life, and increasing wear on the piston, piston rings, and cylinder walls. Utility Model Content

[0005] This invention proposes a piston ring groove and ring land structure to solve the problems mentioned in the background art.

[0006] To achieve the above objectives, the present invention adopts the following technical solution:

[0007] A piston ring groove and ring land structure is provided on a piston. The piston head has a first ring groove and a second ring groove arranged sequentially from top to bottom. The space between the first and second ring grooves forms a ring land, which has an oil storage structure. Specifically, based on the axial thickness of the ring land, several rows of oil storage holes are arranged around it. Taking two rows of oil storage holes as an example, one row of first oil storage holes is arranged radially at equal intervals in the middle of the outer circumference of the ring land, and another row of second oil storage holes is arranged radially at equal intervals near the second ring groove. For ease of manufacturing, the first oil storage hole in the middle of the ring land is circular, while the second oil storage hole near the second ring groove is arc-shaped. All first and second oil storage holes are arranged in staggered positions.

[0008] Preferably, an oil ring groove is provided below the second air ring groove, the first air ring is provided in the second air ring groove, the second air ring is provided in the second air ring groove, and an oil ring is provided in the oil ring groove; the second air ring groove and the oil ring groove are recessed ring lands.

[0009] Preferably, the depth of the first oil storage hole does not exceed the depth of the first gas ring groove, while the depth of the second oil storage hole is 30% to 50% of the depth of the second gas ring groove, and the second oil storage hole is axially connected to the second gas ring groove.

[0010] The oil storage structure increases the space around the land, increases the oil buffer capacity, improves the upward oil collection speed, and slows down the upward movement of oil around the land towards the first piston ring groove. At the same time, it buffers, turbulents, depressurizes, and cools the combustion gas, slowing down the downward speed of the combustion gas. This ensures that after the combustion gas is purged downwards, the oil retained around the land meets the stable supply to the contact surfaces between the outer surfaces of the first and second piston rings and the cylinder wall, improving piston lubrication.

[0011] Preferably, the first compression ring is a double-layered, semi-enclosed, staggered, fully sealed ring, comprising an upper inner ring and a lower outer ring. The upper inner ring has a mating surface, and one side of the inner circumferential surface of the mating surface has a retaining edge. The lower outer ring is in contact with the mating surface, and the width of the lower outer ring is the same as the width of the mating surface. After the lower outer ring and the upper inner ring are combined, the outer circumferential surface of the lower outer ring and the outer circumferential surface of the upper inner ring are located in the same vertical plane, thereby ensuring the sealing performance between the first compression ring and the cylinder wall.

[0012] Preferably, both the open ends of the upper inner ring and the lower outer ring are flat-mouth structures. When the open ends of the upper inner ring are joined together, a locking groove is formed between the open ends of the retaining edges. The lower outer ring is provided with a locking tenon, which engages with the locking groove. The connection between the locking groove and the locking tenon enhances the stability of the upper inner ring and the lower outer ring after assembly, preventing the upper inner ring and the lower outer ring from rotating due to vibration caused by the impact of the combustion gas during piston operation. Such rotation could cause the open ends of the upper inner ring and the lower outer ring to face each other, thereby reducing the sealing performance and causing combustion gas leakage.

[0013] Preferably, after the upper inner ring and lower outer ring are fitted into the air inlet groove, an air inlet is formed on the upper side of the overlap of the upper inner ring.

[0014] Preferably, the upper part of the piston is the piston head and the lower part of the piston is the piston skirt. The piston is installed in the cylinder, the upper part of the piston head is the combustion chamber, and the lower part of the piston skirt is the crankcase.

[0015] Preferably, the air inlet formed on the upper side of the overlap of the upper inner ring is located on the upper side of the air ring groove, and the metering air outlet is located on the lower side of the air ring groove, and the air inlet and the metering air outlet are connected to the bottom of the air ring groove.

[0016] Preferably, the upper part of the combustion chamber is provided with a valve intake surface and a valve exhaust surface, the position of the piston top circular surface perpendicular to the middle of the valve intake surface is set at 6 o'clock, and the position of the piston top circular surface perpendicular to the middle of the valve exhaust surface is set at 0 o'clock.

[0017] Preferably, the air inlet can be located at any position from 9 o'clock to 0 o'clock or from 0 o'clock to 3 o'clock on the upper side of the air ring groove, and the air inlet is preferably located at the position of 9 o'clock, 0 o'clock or 3 o'clock on the upper side of the air ring groove. The metering air outlet should be located at the position of 0 o'clock or 6 o'clock on the lower side of the air ring groove.

[0018] Preferably, the size of the quantitative gas outlet can be customized according to the requirements of different vehicle engines, so as to achieve a customizable amount of gas entering the ring. The amount of gas leakage is not affected by the wear of the gas ring, and a fixed amount of gas flow can be maintained for a long time.

[0019] Preferably, the second gas ring of the second gas ring groove can be either a fully sealed gas ring or an existing flat-mouth gas ring with an undercut structure.

[0020] Preferably, the oil ring groove and the oil ring are existing structures, and the oil ring is a combined oil ring or an integral oil ring.

[0021] Preferably, the second gas ring of the second gas ring groove is selected to be a flat gas ring with a lower outer tangent structure, and the oil ring of the oil ring groove is selected to be a combined oil ring or an integrated oil ring. These are all existing mature technologies and are not limited to one type here.

[0022] Compared with the prior art, the present invention has the following beneficial effects:

[0023] This invention firstly increases the space of the ring by setting up an oil storage structure around the gasket, thereby increasing the oil buffer capacity, improving the upward oil collection speed, and slowing down the upward movement of the oil from the ring to the first gasket groove. At the same time, it buffers and turbulents the combustion gas, improving the cooling and pressure reduction effects, while slowing down the downward speed of the combustion gas. This ensures that after the combustion gas purges downward, the ring releases the remaining oil, which satisfies the stable supply to the contact surfaces between the outer surfaces of the first and second gaskets and the cylinder wall, optimizes the lubrication performance of the first and second gaskets, ensures uniform oil distribution, and avoids abnormal wear of the first and second gaskets.

[0024] Secondly, by setting up a fully sealed gas ring, the overall sealing performance of the gas ring is ensured, effectively blocking 90% of the gas in the upper part of the gas ring groove. Moreover, the sealing performance of the gas ring does not decrease with the wear of the outer surface of the ring.

[0025] Third, by forming an arc-shaped extended path through the air inlet formed by the upper inner ring joint and the quantitative air outlet of the ring groove, the flow of downward combustion gas and oil, and upward air and oil are limited and guided, effectively preventing excessive oil from entering the combustion chamber and excessive gas from leaking into the crankcase, and realizing the up and down circulation and buffering of oil in the piston head, ensuring the oil supply between the piston rings and the cylinder wall working surface.

[0026] The resulting arc-shaped extended path lengthens the travel distance of the gas and oil, increases the travel distance of the upward air and oil, expands the oil storage space, slows down the upward speed of the oil, and improves the effects of flow restriction, flow guidance, buffering, and caching. Attached Figure Description

[0027] Figure 1 A schematic diagram of the piston structure of this utility model;

[0028] Figure 2 Another front view of the piston structure having this utility model;

[0029] Figure 3 This is a schematic diagram of the structure of the gas ring of this utility model when the upper inner ring and the lower outer ring are not combined;

[0030] Figure 4 This is an enlarged schematic diagram of the gas ring and the locking tenon of this utility model;

[0031] Figure 5 This is a schematic diagram of the structure of the gas ring, the snap-fit, and the tenon of this utility model when they are interlocked.

[0032] Figure 6 This is a schematic diagram of an existing flat-mouth gas ring structure.

[0033] Figure 7 A schematic diagram of an existing oil ring structure;

[0034] 1. Piston; 11. Upper inner ring; 12. Lower outer ring; 13. Assembly surface; 14. Flange; 15. Bayonet; 16. Tenon; 17. Outer circular surface; 18. Back side; 2. Ring land; 21. Compression ring one; 22. Compression ring two; 23. Oil ring; 24. Compression ring groove one; 25. Compression ring groove two; 26. Oil ring groove; 3. Recessed ring land; 35. Inlet one; 32. Metering outlet one; 41. Upper scraper of oil ring; 42. Lower scraper of oil ring; 43. Oil ring cavity; 44. Oil return hole; 51. Oil reservoir one; 52. Oil reservoir two; 6. Flat-mouth compression ring; 61. Valve inlet surface; 62. Valve exhaust surface; 72. Lower outer tangent structure. Detailed Implementation

[0035] The technical solutions of the present utility model will be clearly and completely described below with reference to the accompanying drawings of the embodiments. Obviously, the described embodiments are only some embodiments of the present utility model, and not all embodiments. Based on the embodiments of the present utility model, all other embodiments obtained by those of ordinary skill in the art without creative effort are within the protection scope of the present utility model.

[0036] Reference Figures 1-7 A piston ring groove and ring land structure includes a piston 1. The piston 1 has a ring groove 24 and a ring groove 25 arranged sequentially from top to bottom on its head. The ring land 2 is located between the ring groove 24 and the ring groove 25. The ring land 2 is provided with an oil storage structure, that is, according to the axial thickness of the ring land 2, several rows of oil storage holes or oil storage grooves are arranged around the ring land 2.

[0037] Taking the arrangement of two rows of oil storage holes as an example, a row of oil storage holes 51 is arranged radially at equal intervals in the middle of the outer periphery of the ring 2, and a row of oil storage holes 52 is arranged radially at equal intervals near the gas ring groove 25. For ease of processing, the oil storage holes 51 in the middle of the ring 2 are circular, and the oil storage holes 52 near the gas ring groove 25 are arc-shaped. The oil storage holes 51 and 52 are arranged in staggered positions.

[0038] Below the second gas ring groove 25, there is an oil ring groove 26. The first gas ring groove 24 is fitted with a first gas ring 21. The second gas ring groove 25 is fitted with a second gas ring 22. The oil ring groove 26 is fitted with an oil ring 23. The second gas ring groove 25 and the oil ring groove 26 are connected by a recessed ring bank 3.

[0039] The depth of the first oil reservoir 51 does not exceed the depth of the first ring groove 24, while the depth of the second oil reservoir 52 is 30% to 50% of the depth of the second ring groove 25, and the second oil reservoir 52 is axially connected to the second ring groove 25. The size, shape, and number of the first oil reservoir 51 and the second oil reservoir 52 need to be determined according to the actual needs of different engines.

[0040] The oil storage structure of the ring 2 increases the space of the ring 2, increases the oil buffer capacity, improves the upward oil collection speed, and slows down the upward movement of oil from the ring 2 to the piston ring groove 24. At the same time, it buffers, turbulents, depressurizes, and cools the combustion gas, slows down the downward speed of the combustion gas, and ensures that after the combustion gas is purged, the oil retained in the ring 2 meets the stable supply of oil to the contact surface between the outer circular surface 17 of piston ring 21 and piston ring 22 and the cylinder wall, thereby improving the lubrication of piston 1.

[0041] The gas ring 21 is a double-layered, semi-enclosed, staggered, fully sealed ring, comprising an upper inner ring 11 and a lower outer ring 12. The upper inner ring 11 has a mating surface 13, and a retaining edge 14 is provided on one side of the inner circumferential surface of the mating surface 13. The lower outer ring 12 is connected to the mating surface 13, and the width of the lower outer ring 12 is the same as the width of the mating surface 13. After the lower outer ring 12 is combined with the upper inner ring 11, the outer circumferential surface of the lower outer ring 12 and the outer circumferential surface of the upper inner ring 11 are located in the same vertical plane, thereby ensuring the sealing between the gas ring 21 and the cylinder wall.

[0042] Both the open ends of the upper inner ring 11 and the lower outer ring 12 are flat-mouth structures. When the open ends of the upper inner ring 11 are joined together, a locking groove 15 is formed between the open ends of the retaining edge 14. The lower outer ring 12 is provided with a locking tenon 16, which engages with the locking groove 15. The connection between the locking groove 15 and the locking tenon 16 enhances the stability of the upper inner ring 11 and the lower outer ring 12 after assembly, preventing the upper inner ring 11 and the lower outer ring 12 from rotating due to vibration caused by the impact of the combustion gas when the piston 1 is working. Such rotation may cause the open end of the upper inner ring 11 to face the open end of the lower outer ring 12, thereby reducing the sealing performance and causing combustion gas leakage.

[0043] After the upper inner ring 11 and the lower outer ring 12 are fitted into the air ring groove 24, an air inlet 35 is formed on the upper side of the overlap of the upper inner ring 11 (e.g., Figure 5 (As shown).

[0044] The upper part of the piston 1 is the head of the piston 1 and the lower part of the piston 1 is the skirt of the piston 1. The piston 1 is installed in the cylinder. The combustion chamber is above the head of the piston 1 and the crankcase is below the skirt of the piston 1.

[0045] The air inlet 35 formed on the upper side of the overlap of the upper inner ring 11 is located on the upper side of the air ring groove 24, and the metering air outlet 32 ​​is located on the lower side of the air ring groove 24. The air inlet 35 and the metering air outlet 32 ​​are connected to the bottom of the air ring groove 24.

[0046] The upper part of the combustion chamber is provided with a valve intake surface 61 and a valve exhaust surface 62. The position of the top circular surface of the piston 1 perpendicular to the middle of the valve intake surface 61 is set at 6 o'clock, and the position of the top circular surface of the piston 1 perpendicular to the middle of the valve exhaust surface 62 is set at 0 o'clock.

[0047] The air inlet 35 can be located at any position from 9 o'clock to 0 o'clock or from 0 o'clock to 3 o'clock on the upper side of the air ring groove 24, but the air inlet 35 is preferably located at the 9 o'clock, 0 o'clock or 3 o'clock position on the upper side of the air ring groove 24, and the metering air outlet 32 ​​should be located at the 0 o'clock or 6 o'clock position on the lower side of the air ring groove 24.

[0048] Based on the above structure, using a piston with the aforementioned defined structure, the air, mixture, or fuel gas in the combustion chamber is restricted and guided to several circulation paths on the annular 2:

[0049] 1. When the air inlet 35 is set at the 0 o'clock position and the metering outlet 32 ​​is staggered and set at the 6 o'clock position, the air inlet 35, the gap between the back of the air ring 21 and the bottom of the air ring groove 24, and the metering outlet 32 ​​form two new arc-shaped extension paths of equal length for air, mixed gas or fuel gas to descend.

[0050] 2. When the air inlet 35 is set at the 3 o'clock position and the metered air outlet 32 ​​is set at the 0 o'clock position, the air inlet 35, the gap between the back of the air ring 21 and the bottom of the air ring groove 24, and the metered air outlet 32 ​​form two new arc-shaped extension paths of one long and one short for the downward flow of air, mixed gas or fuel gas.

[0051] 3. When the air inlet 35 is set at the 9 o'clock position and the metering outlet 32 ​​is set at the 0 o'clock position, the air inlet 35, the gap between the back of the air ring 21 and the bottom of the air ring groove 24, and the metering outlet 32 ​​form two new arc-shaped extension paths, one short and one long, for the downward flow of air, mixed gas, or fuel gas.

[0052] When piston 1 enters the compression, power and exhaust strokes, part of the air, mixture or combustion gas enters the back of the ring from the upper side gap of the ring-21 to establish side pressure, and the other part passes through the new arc-shaped extension path of the ring groove-24. While establishing the back side pressure of the ring-21, the air, mixture or combustion gas entering the back of the ring from the upper side gap is introduced into the ring land 2.

[0053] The gas-blocking and flow-guiding method based on the above-mentioned double-layer semi-enclosed misaligned fully sealed ring includes the following:

[0054] When piston 1 enters the compression, power, and exhaust strokes, the air, mixture, or combustion gas in the combustion chamber impacts piston 1. The upper inner ring 11 and lower outer ring 12 of the compression ring 21 are compressed face-to-face. The outer bottom surface of the upper inner ring 11 is in close contact with the front surface of the lower outer ring 12. The lower bottom surface of the upper inner ring 11 flange 14 and the lower bottom surface of the lower outer ring 12 are in close contact with the lower side of the compression ring groove 24. A small portion of the air, mixture, or combustion gas enters the back clearance from the upper side gap of the upper inner ring 11, and together with another portion, is introduced into the back clearance from the intake port 35 at the 0, 3, or 9 o'clock position on the upper side of the compression ring groove 24. The space establishes lateral pressure, and a large amount of air, air-fuel mixture or fuel gas is blocked by the combination of the air ring 21 and the air ring groove 24. A portion of the air, air-fuel mixture or fuel gas leaks downward into the ring land 2 through the radial wave-like bouncing of the inner ring 11 and the outer ring 12 of the air ring 21 from the outer circular surface 17 of the ring body and the cylinder wall and the gap of the ring body. The rest of the air, air-fuel mixture or fuel gas is introduced into the ring land 2 through the metered air outlet 32 ​​at the 0 o'clock or 6 o'clock position on the lower side of the air ring groove 24. At the same time, the oil buffered in the air ring groove 24 and the ring land 2 is blown downward and driven away.

[0055] When piston 1 enters the intake stroke, the oil moves upward in the opposite direction along the path of air, air-fuel mixture, or fuel gas. Due to the difference between oil and air, the low-density, highly fluid air is quickly drawn into the combustion chamber through the lower side gap of the piston ring 21, the metering outlet 32, and the intake port 35. The high-density, viscous oil is mostly blocked at the bottom of the small metering outlet 32. The oil that struggles to pass through the narrow lower side gap and metering outlet 32 ​​is then buffered and retained by the back of the piston ring 21 and the bottom space of the piston ring groove 24. Only a very small amount of oil can escape through the intake port 35 and enter the combustion chamber. When this very small amount of oil is introduced into the ring surface of the piston ring 21, piston 1 switches to the compression stroke, and the oil is promptly blown downward by the air or air-fuel mixture.

[0056] Sufficient oil is quickly returned to the oil ring cavity 43, the recessed ring land 3 and the ring land 2 to meet the lubrication supply in a timely manner, while preventing excessive oil from rising into the combustion chamber.

[0057] The oil that rises to the ring 2 and the cylinder wall groove 24 is coated onto the cylinder wall working surface by the piston moving up and down with the piston rings 21 and 22. The path through which the combustion gases drive the oil downwards is also the path through which the oil is drawn upwards to return and renew itself.

[0058] The size of the quantitative gas outlet hole 32 can be customized according to the requirements of different vehicle engines, so as to achieve a customizable gas intake volume into the ring 2. The gas leakage volume is not affected by the wear of the gas ring 21, and a fixed gas flow volume can be maintained stably for a long time.

[0059] The second gas ring 22 of the second gas ring groove 25 can be either a fully sealed gas ring or an existing flat-mouth gas ring with an undercut structure.

[0060] The flat-mouth gas ring, such as Figure 6 The existing flat-mouth gas ring 6 has two flat ends, and the lower bottom surface is close to the lower side of the outer ring surface with a lower outer tangent structure 72.

[0061] The oil ring groove 26 and the oil ring 23 are existing structures, and the oil ring 23 is a combined oil ring or an integral oil ring.

[0062] For example, the gas ring 22 of the gas ring groove 25 can be selected as a flat gas ring 6 with a lower outer tangent structure, and the oil ring 23 of the oil ring groove 26 can be selected as a combined oil ring or an integrated oil ring. These are all existing mature technologies, and no single limitation is made here.

[0063] If a combined oil ring is used, the oil ring 23 includes an upper scraper 41, an inner liner, and a lower scraper 42. The upper and lower scrapers clamp the inner liner in the middle to form an oil ring cavity 43.

[0064] If an integral oil ring is used, the oil ring 23 consists of an outer frame and a support spring. The internal space of the outer frame and the support spring together form the oil ring cavity 43.

[0065] Example 2 is a further refined example based on the structure of Example 1.

[0066] The gas ring 21 is a double-layer, semi-enclosed, misaligned, fully sealed ring, because as... Figure 5 As shown, the upper inner ring 11 port forms an air inlet 35, so there is no need to set a quantitative air inlet 31 on the upper side of the 0, 3 or 9 o'clock position of the air ring groove 24; instead, a quantitative air outlet 32 ​​is set on the lower side of the 0 or 6 o'clock position.

[0067] The installation method and requirements for the gas ring 21 of the gas ring groove 24 are as follows:

[0068] ① If the air inlet 35 is set (aligned) at the 0 o'clock position and the metering outlet 32 ​​is set at the 0 o'clock position, this air ring is not suitable for use;

[0069] ② If the air inlet 35 is set (aligned) at the 0 o'clock position and the metering outlet 32 ​​is set at the 6 o'clock position, then the upper inner ring 11 port must be aligned with the 0 o'clock position.

[0070] ③ If the air inlet 35 is set (aligned) at the 3 o'clock position and the metering outlet 32 ​​is set at the 0 o'clock position, then the upper inner ring 11 port must be aligned with the 3 o'clock position.

[0071] ④ If the air inlet 35 is set (aligned) at the 9 o'clock position and the metering outlet 32 ​​is set at the 0 o'clock position, then the upper inner ring 11 port must be aligned with the 9 o'clock position.

[0072] When selecting an existing flat-mouthed gas ring 6 with a lower external tangent structure for gas ring 22, the method and requirements for installing it into gas ring groove 25 are as follows:

[0073] The flat-mouth air ring 6 is an existing mature technology, and its installation method is the same as the existing method.

[0074] ①If the metering outlet 32 ​​of the air ring groove 24 is set at the 0 o'clock position, then the port 6 of the flat air ring must be aligned with the 6 o'clock position.

[0075] ②If the metering outlet 32 ​​of the air ring groove 24 is set at the 6 o'clock position, then the 6 port of the flat-mouth air ring must be aligned with the 0 o'clock position.

[0076] When the oil ring 23 of the oil ring groove 26 is selected to use an existing combined oil ring or an integrated oil ring, the installation method and requirements are as follows:

[0077] The combined oil ring or the integrated oil ring mentioned above are both existing mature technologies, and their installation methods are the same as existing methods.

[0078] ① If the oil ring 23 uses the existing combined oil ring, the port of the upper scraper 41 of the oil ring 23 should be aligned with the left and right sides of the 0 o'clock or 6 o'clock position opposite to the port of the flat-mouth air ring 6 of the second air ring 22; the port of the lower scraper 42 should be aligned with the left and right sides of the 6 o'clock or 0 o'clock position opposite to the port of the upper scraper 41.

[0079] ②If the oil ring 23 uses the existing integrated oil ring, the port of the integrated oil ring should be aligned with the left and right sides of the 0 point or 6 o'clock position opposite to the port of the flat ring 4 of the second gas ring 22.

[0080] Detailed working principle of the combined use of gas ring groove 24 and gas ring 21:

[0081] First, when piston 1 enters the power and exhaust strokes, some of the combustion gas leaks downwards through the gap between the outer surface 17 of the ring body and the cylinder wall, as well as the ring body overlap gap, due to the radial wave-like bouncing of the ring body during its up-and-down movement. The remaining combustion gas enters the bottom of the ring groove 24 through the upper side gap of the ring body and the intake port 35 at the 0, 3, or 9 o'clock position. At this time, the front and back surfaces 18 of the upper inner ring 11 and the lower outer ring 12 are pressure surfaces, causing the upper inner ring 11 and the lower outer ring 12 to... The downward pressure and radial expansion cause the bottom surface of the upper inner ring 11 to be in close contact with the front surface of the lower outer ring 12, and the bottom surface of the lower outer ring 12 to be in close contact with the lower side surface of the gas ring groove 24. The outer circular surfaces 17 of the upper inner ring 11 and the lower outer ring 12 are in close contact with the cylinder wall, thereby preventing the gas from leaking from the outer circular surfaces 17 or the bottom surface of the upper inner ring 11 and the lower outer ring 12. Since the upper inner ring 11 and the lower outer ring 12 are staggered and overlapped, the sealing degree of the gas ring 21 is significantly increased, thereby blocking more than 90% of the gas in the upper part of the gas ring 21.

[0082] The staggered arrangement of the air inlet 35 and the metered air outlet 32 ​​creates a new arc-shaped extended path between the air inlet 35 and the metered air outlet 32, increasing the flow path of the gas and improving the effects of limiting, guiding, cooling, and reducing the pressure of the gas. Only a small amount of gas can enter the ring bank 2 through this multi-bend arc-shaped extended channel.

[0083] The high-temperature, high-pressure gas flame passes through the narrow gap between the top bank 7 and the cylinder wall, as well as the narrow upper side gap and the intake port 35, and is extinguished due to heat loss and temperature reduction.

[0084] Because the size of the metering outlet 32 ​​is customizable through drilling, the amount of gas entering the ring 2 can be customized. A stable, consistent gas leakage rate can be maintained over a long period, unaffected by wear on the gas ring 21. Only less than 10% of the gas can bypass the seal of the gas ring 21 and enter the outer space of the ring 2.

[0085] The sealing structure of the first ring groove 24 and the first ring 21 connects to the second ring groove 25 and the second ring 22, and then to the oil ring groove 26 and the oil ring 23. The sealing structure of the first ring groove 24 and the first ring 21 has the functions of limiting and guiding flow, while also enhancing the buffering effect of the ring land 2, the recessed ring land 3, and the oil ring cavity 43 on the engine oil. This ensures that after each combustion gas purging, some engine oil is still retained in the bottom gap of the first ring groove 24, the ring land 2, the bottom gap of the second ring groove 25, the recessed ring land 3, and the oil ring cavity 43, thus meeting the lubrication requirements of the piston head 1.

[0086] The piston ring 21 adopts a thickened design, that is, the thickness of piston ring 21 is 1.5 to 2 times thicker than the existing piston ring. This greatly improves the heat conduction of the contact surface between piston ring 21 and cylinder wall, avoiding high temperature at the piston head. At the same time, combined with the structural design of piston ring groove 24, the combustion gas passes through the new arc-shaped extended path formed by intake port 35, the gap between the back of piston ring 21 and the bottom of piston ring groove 24, and metered outlet port 32. The combustion gas entering the ring land 2 has become more gentle, avoiding the violent scavenging of combustion gas when piston ring 21 is a traditional flat-mouth piston ring 6. The oil storage structure of the ring 2 can buffer more oil when the oil is drawn upward, delaying the upward movement of the oil from the ring 2 towards the compression ring groove 24. When the oil is blown downward, the buffered oil is released while causing turbulence. Together with the oil buffered at the bottom of the compression ring groove 24, this alleviates the "oil-deficient" state of the piston head and ensures the oil supply to compression rings 21 and 22. The oil storage structure's buffering and turbulence of the combustion gas and the release of oil are beneficial for the combustion gas to decelerate, cool, and depressurize, and improve the oil distribution amount, oil distribution speed, and uniformity of compression rings 21 and 22, thereby improving the smoothness of piston 1's operation.

[0087] Secondly, after being sealed by the sealing structures of gas ring groove 24 and gas ring 21, about 8%-10% of the gas flows downward into the ring bank 2. It is necessary to rely on gas ring 22 to continue to bear the pressure of the gas and achieve sealing again to block the gas from flowing downward, thus blocking less than 10% of the gas in the upper part of gas ring groove 25.

[0088] The combustion gas, after being blocked by the second gas ring 22, descends to the recessed annular land 3, where it becomes smoother. The recessed structure of the recessed annular land 3 and the lower outer tangent structure 72 of the second gas ring 22 increase the space of the recessed annular land 3, which is beneficial for the expansion and cooling of the descending combustion gas, and further reduces the flow rate of the combustion gas. At the same time, the recessed structure of the recessed annular land 3 and the lower outer tangent structure 72 of the second gas ring 22 help to buffer more engine oil, increase the amount and speed of oil adhesion to the second gas ring 22, and its torsional effect allows the engine oil to be more timely and evenly coated on the cylinder wall working surface when the piston 1 moves upward; when the piston 1 moves downward, it scrapes off excess engine oil from the cylinder wall, improving the oil distribution effect.

[0089] The gas gently blows the recessed ring land 3, which on the one hand blows the buffered oil into the oil ring cavity 43 and then returns it to the crankcase through the oil return hole 44; on the other hand, the gas ring 22 and the oil ring 23 evenly spread the oil buffered in the ring land 2, the recessed ring land 3 and the oil ring cavity 43 onto the cylinder wall working surface to ensure the smooth operation of the piston 1.

[0090] The combustion gas entering the concave ring lander 3 is then blocked by the oil ring 23. Finally, only a trace amount of combustion gas, about 0.01%, can reach the crankcase through the oil ring groove 26.

[0091] For example, if the second compression ring 22 uses a flat-mouth compression ring 6, its port is an open structure. A small amount of combustion gas is introduced into the recessed ring land 3 from the 6 o'clock or 0 o'clock position through the port of the flat-mouth compression ring 6, and then enters the oil ring cavity 43 from the 0 o'clock or 6 o'clock position through the scraper 41 port on the combined oil ring or the integrated oil ring port, blowing the oil in the oil ring cavity 43 back to the crankcase, completing one cycle of oil return and renewal process from the gap between the back of the first compression ring 21 and the bottom of the first compression ring groove 24 → ring land 2 → recessed ring land 3 → oil ring cavity 43 → oil return hole 44 → crankcase.

[0092] During the intake stroke, the engine oil is drawn upward once, and then blown downward three times by air, air-fuel mixture or fuel gas during the compression stroke, power stroke and exhaust stroke.

[0093] The gas ring 21 with the above-mentioned fully sealed structure ensures that the ring body retains sufficient expansion elastic space when blocking gas, and at the same time keeps the opening and closing in a continuous sealing state, ensuring the overall sealing performance of the gas ring 21, effectively blocking 90% of the gas in the upper part of the gas ring groove 24, and the sealing degree of the gas ring 21 does not decrease with the wear of the outer circular surface 17 of the ring.

[0094] Secondly, by forming an arc-shaped extended path through the intake port 35 formed by the upper inner ring 11 and the quantitative exhaust port 32 of the ring groove 24, the flow of downward combustion gas and oil, and upward air and oil is limited and guided, effectively preventing excessive oil from entering the combustion chamber and excessive combustion gas from leaking into the crankcase. It also realizes the up-and-down circulation and buffering of oil in the piston head, ensuring the oil supply of ring 21, ring 22 and oil ring 23 to the cylinder wall working surface. The arc-shaped extended path extends the circulation path of combustion gas and oil, increases the circulation path of upward air and oil, expands the oil storage space, slows down the upward speed of oil, and improves the flow limiting, guiding, buffering and buffering effects.

[0095] Thirdly, by setting up an oil storage structure in the ring 2, the space of the ring 2 is increased, the oil buffer capacity is increased, the upward oil collection speed is improved, and the upward movement of oil in the ring 2 is slowed down. At the same time, the combustion gas is buffered and turbulent, improving the cooling and pressure reduction effect, while slowing down the downward speed of the combustion gas. This ensures that after the combustion gas is purged downwards, the ring 2 releases the reserved oil, which meets the stable supply to the contact surface between the outer circular surface 17 of the first and second rings 22 and the cylinder wall. This optimizes the lubrication performance of the first and second rings 22, ensures uniform oil distribution, and avoids abnormal wear of the first and second rings 22.

[0096] The combination of the first gas ring 21, the second gas ring 22, and the oil ring 23 allows the piston 1 to be used as a whole, achieving a high degree of sealing of the combustion gas. The amount of combustion gas leaking downward into the crankcase is not affected by the wear and outward elasticity of the first gas ring 21, the second gas ring 22, and the oil ring 23, and can maintain a fixed flow of combustion gas and engine oil for a long time, so as to maintain a constant high cylinder pressure in the combustion chamber for a long time.

[0097] Under high cylinder pressure, a very small amount of engine oil is introduced into the combustion chamber and participates in combustion with fuel that is closest to complete combustion. This completely avoids the formation of carbon black and gum, thus completely preventing the adhesion of carbon deposits to the piston head and crankcase. This eliminates the risk of cylinder scoring and crankshaft seizure caused by carbon deposits. The controlled and reduced leakage of combustion gases prevents the engine oil buffered in the labyrinthine channel of the piston head from being excessively sheared due to high-temperature vaporization, significantly extending the life of the engine oil and ensuring its lubricating performance. This, in turn, significantly increases the service life of piston 1, compression ring 21, compression ring 22, and oil ring 23, while achieving energy saving and emission reduction, significantly improving engine efficiency, and extending engine life.

[0098] The aforementioned sealing structure of the air ring is applicable to piston air compressors, piston refrigeration machines, piston-type lifting equipment, i.e., a piston air compressor or air compressor piston or piston refrigeration machine or refrigeration machine piston or piston-type lifting equipment or other equipment piston.

[0099] It will be apparent to those skilled in the art that this invention is not limited to the details of the exemplary embodiments described above, and that it can be implemented in other specific forms without departing from the spirit or essential characteristics of this invention. Therefore, the embodiments should be considered illustrative and non-limiting in all respects, and the scope of this invention is defined by the appended claims rather than the foregoing description. Thus, it is intended that all variations falling within the meaning and scope of equivalents of the claims be included within this invention. No reference numerals in the claims should be construed as limiting the scope of the claims.

[0100] Furthermore, it should be understood that although this specification describes embodiments, not every embodiment contains only one independent technical solution. This narrative style is merely for clarity. Those skilled in the art should consider the specification as a whole, and the technical solutions in each embodiment can also be appropriately combined to form other embodiments that can be understood by those skilled in the art.

Claims

1. A piston gas-ring groove and land structure provided on a piston (1), characterized in that, The piston (1) head is provided with a first gas ring groove (24) and a second gas ring groove (25) from top to bottom. The space between the first gas ring groove (24) and the second gas ring groove (25) is a ring lander (2). A row of oil storage holes (51) is arranged radially at the same interval in the middle of the outer periphery of the ring lander (2). A row of oil storage holes (52) is arranged radially at the same interval near the second gas ring groove (25) at the lower part of the ring lander (2). Each of the first oil storage holes (51) and each of the second oil storage holes (52) are arranged in an alternating position.

2. The piston ring groove and land structure of claim 1 wherein, Below the second gas ring groove (25) is an oil ring groove (26), the first gas ring groove (24) is fitted with a first gas ring (21), the second gas ring groove (25) is fitted with a second gas ring (22), the oil ring groove (26) is fitted with an oil ring (23), and there is a recessed ring bank (3) between the second gas ring groove (25) and the oil ring groove (26).

3. The piston ring groove and land structure of claim 2 wherein, The depth of the first oil storage hole (51) does not exceed the depth of the first gas ring groove (24), the depth of the second oil storage hole (52) is 30% to 50% of the depth of the second gas ring groove (25), and the second oil storage hole (52) is axially connected to the second gas ring groove (25).

4. The piston ring groove and land structure of claim 2 wherein, The air ring (21) is a double-layer semi-enclosed misaligned fully sealed ring, including an upper inner ring (11) and a lower outer ring (12). The upper inner ring (11) is provided with a combination surface (13). A retaining edge (14) is provided on one side of the inner circumferential surface of the combination surface (13). The lower outer ring (12) is connected to the combination surface (13), and the width of the lower outer ring (12) is the same as the width of the combination surface (13).

5. The piston ring groove and land structure of claim 4 wherein, The opening ends of the upper inner ring (11) and the lower outer ring (12) are both flat structures. When the opening ends of the upper inner ring (11) are joined together, a snap (15) is formed between the opening ends of the side guard (14). The lower outer ring (12) is provided with a tenon (16), and the tenon (16) and the snap (15) are engaged with each other.

6. The piston ring groove and land structure of claim 5 wherein, After the upper inner ring (11) and the lower outer ring (12) are fitted into the air ring groove (24), an air inlet (35) is formed on the upper side of the overlap of the upper inner ring (11).

7. The piston ring groove and land structure of claim 1 wherein, The upper part of the piston (1) is the head of the piston (1) and the lower part of the piston (1) is the skirt of the piston (1). The piston (1) is installed in the cylinder. The upper part of the piston (1) head is the combustion chamber and the lower part of the piston (1) skirt is the crankcase.

8. The piston ring groove and land structure of claim 6 wherein, The air inlet (35) formed on the upper side of the upper inner ring (11) is located on the upper side of the air ring groove (24), and the metered air outlet (32) is located on the lower side of the air ring groove (24). The air inlet (35) and the metered air outlet (32) are connected to the bottom of the air ring groove (24).

9. The piston ring groove and ring land structure according to claim 7, characterized in that, The combustion chamber is provided with a valve intake surface (61) and a valve exhaust surface (62) at the top. The position of the top circular surface of the piston (1) perpendicular to the middle of the valve intake surface (61) is set at 6 o'clock, and the position of the top circular surface of the piston (1) perpendicular to the middle of the valve exhaust surface (62) is set at 0 o'clock.

10. The piston ring groove and land structure of claim 8 wherein, The air inlet (35) can be located at any position between 9 o'clock and 0 o'clock or between 0 o'clock and 3 o'clock on the upper side of the air ring groove (24). The air inlet (35) is located at 9 o'clock, 0 o'clock or 3 o'clock on the upper side of the air ring groove (24). The metering outlet (32) should be located at 0 o'clock or 6 o'clock on the lower side of the air ring groove (24).

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