Flat and stepped double combination misloading full seal ring

Abstract

This utility model discloses a double-layer combined staggered fully sealed ring with a flat opening and a stepped overlap, comprising a first gas ring. The first gas ring includes a flat upper ring and a stepped overlap lower ring. Both the upper and lower rings are provided with elastic overlaps. The two ends of the elastic overlap of the upper ring are flat ends, and the two ends of the elastic overlap of the lower ring are a narrow tongue end and a wide tongue end, respectively. The narrow tongue end and the wide tongue end can be interlocked and sealed. The maximum opening of the narrow tongue end and the wide tongue end are joined at their very ends. The upper and lower rings are stacked vertically, and the positions of the elastic overlaps of the upper ring and the lower ring are staggered vertically. Using the structure of this utility model, more than 90% of the combustion gas in the combustion chamber is blocked in the upper part of the first gas ring, and the sealing degree of the first gas ring does not decrease with the wear of the outer circular surface of the ring. At the same time, the flow guiding channel formed by the cooperation with the first gas ring groove realizes the flow restriction and guidance control of the combustion gas leaking into the ring land, and realizes the uniform distribution of oil and the circulation and renewal of oil.

Description

Technical Field

[0001] This utility model relates to the field of engine piston ring technology, specifically a double-layer combination of flat and stepped joints for a fully sealed ring. Background Technology

[0002] The piston is one of the most important components of an engine, located inside the cylinder. During operation, it needs to reciprocate rapidly with the cylinder. A piston typically has two compression ring grooves and one oil ring groove. Compression rings are fitted into each of the two compression ring grooves, and an oil ring is fitted into the oil ring groove. The main function of the compression ring grooves, compression rings, oil ring grooves, and oil rings is to seal and block gas flow while simultaneously distributing oil to the cylinder wall working surface through the piston's reciprocating motion and scraping off excess oil from the cylinder wall. Current piston compression rings are all flat-cut open designs, installed in the two compression ring grooves. The compression rings rely on their own elasticity and the pressure of the combustion gases to achieve radial and axial sealing of the piston, thus blocking the combustion gases.

[0003] Its working principle is as follows Figure 6 As shown, when the piston and piston rings are installed in the cylinder (cylinder), three gaps are formed between the piston, piston rings and cylinder wall (cylinder wall): end gap, side gap and back gap. That is, the piston ring is not perfectly circular in its free state, and its outer dimension is slightly larger than the cylinder diameter. When the piston ring is installed in the cylinder, under its own elastic force, the outer surface of the ring body is pressed tightly against the cylinder wall to form the first sealing surface. Meanwhile, the high-pressure gas in the combustion chamber passes through the gap between the piston top (firepower) bank and the cylinder wall, and enters the back gap from the upper side gap and end gap of the ring body. This pressure makes the lower bottom surface of the ring body press tightly against the lower side surface of the ring groove, and the outer surface of the ring body press tightly against the cylinder wall to form the second sealing surface.

[0004] The minimum opening clearance of the flat-mouth piston ring, designed to accommodate thermal expansion, results in excessive combustion gas leakage and excessive oil rise during initial installation. During use, as the outer surface of the ring wears and springs outward, the end clearance gradually widens, causing a simultaneous drop in cylinder pressure. More oil rises into the combustion chamber, while more combustion gas leaks into the crankcase. Excessive scavenging of the piston head by the combustion gas causes oil vaporization and excessive shearing, with insufficient buffering, leading to poor lubrication between the outer surface of the ring and the cylinder wall. Under low cylinder pressure, oil participates in combustion, and the carbon black and gum generated from incomplete combustion leak down, adhering to the ring grooves, the ring body, and various engine components, forming carbon deposits. As the end clearance of the ring body further widens, the severity of these problems is exacerbated.

[0005] The existing flat-rimmed piston rings have a relatively low sealing performance for the first compression ring, approximately 80% or higher, with a limit of only 90%. The sealing performance for the second compression ring is about 10-20%, and the sealing performance for the oil ring is about 5%. This means that there is still a significant amount of airflow between the combustion chamber and the crankcase.

[0006] Therefore, the first piston ring groove and piston ring are the most critical air-blocking layers. Most of the combustion gases (including air and air-fuel mixture) are blocked by this structure. The existing ones are flat-cut openings, and the open structure during operation has insufficient sealing, which affects the overall piston efficiency, wastes fuel and engine oil, and increases environmental pollution. The formation and adhesion of carbon deposits will eventually lead to piston and piston ring seizure, cylinder scoring, seal failure, and blockage of crankshaft and eccentric shaft oil passages, resulting in crankshaft seizure and reduced engine life.

[0007] Some designs use a joint design, such as patent number 00248108.1, which is used in conjunction with the piston ring groove and cylinder wall. However, since only a full seal is considered, a flow guiding structure is not provided as in this utility model. This results in the oil being trapped in the piston head and unable to flow back and renew itself, reducing the lubrication effect, shortening the oil life, and increasing the wear of the piston, piston rings, and cylinder wall.

[0008] Therefore, it is necessary to provide a double-layer fully sealed gas ring with good gas sealing performance, no impact on gas sealing capability due to wear on the outer circular surface of the ring, and long service life. At the same time, it has a matching gas ring groove to limit and guide the downward gas flow, control the amount of gas leakage, and ensure that the piston head oil can be circulated and renewed. Utility Model Content

[0009] This invention proposes a double-layered, staggered, fully sealed ring with a flat opening and a stepped overlap to solve the problems mentioned in the background art.

[0010] To achieve the above objectives, the present invention adopts the following technical solution:

[0011] A double-layer composite staggered fully sealed ring with a flat opening and a stepped overlap includes a first gas ring disposed on the piston head. The first gas ring includes a flat upper ring and a stepped overlap lower ring. Both the upper and lower rings have elastic overlaps. The two ends of the elastic overlap of the upper ring are flat ends, and the two ends of the elastic overlap of the lower ring are a narrow tongue end and a wide tongue end, respectively. The narrow tongue end and the wide tongue end can be interlocked and sealed. The maximum opening of the narrow tongue end and the wide tongue end are joined at their very ends. The upper and lower rings are stacked vertically, and the positions of the elastic overlaps of the upper and lower rings are staggered vertically, forming a double-layer fully sealed piston gas ring.

[0012] Preferably, it also includes a piston, the upper part of which is the piston head and the lower part of which 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. The outer peripheral surface of the piston head is provided with a first piston ring groove, a second piston ring groove and an oil ring groove from top to bottom, and a first piston ring, a second piston ring and an oil ring are respectively fitted on it.

[0013] Preferably, the area above the first gas ring groove is a top bank, the area between the first gas ring groove and the second gas ring groove is a ring bank, and the area between the second gas ring groove and the oil ring groove is a recessed ring bank.

[0014] Preferably, the ring bank is provided with an oil storage structure, that is, several rows of oil storage holes are arranged around the ring bank according to the axial thickness of the ring bank. Taking the arrangement of two rows of oil storage holes as an example, a row of oil storage holes one is arranged at the same radial spacing in the middle of the outer circumference of the ring bank, and a row of oil storage holes two is arranged at the same radial spacing near the gas ring groove two.

[0015] For ease of processing, the first oil storage hole in the middle of the ring is circular, and the second oil storage hole near the second gas ring groove is arc-shaped; the first and second oil storage holes are arranged in staggered positions.

[0016] 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.

[0017] The oil storage structure increases the space around the gas ring, increases the oil buffer capacity, improves the upward oil collection speed, and slows down the upward movement of the oil around the gas ring groove. 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 around the gas ring can meet the stable supply of the outer circular surface of the first and second combustion rings to the cylinder wall contact surface, thereby improving the lubrication of the piston.

[0018] Preferably, the upper side of the air ring groove has an air inlet formed by the gap between the two flat ends of the flat upper ring overlap, and the lower side of the air ring groove is provided with a metering air outlet, and the air inlet and the metering air outlet are connected to the bottom of the air ring groove.

[0019] Preferably, the combustion chamber is provided with a valve intake surface and a valve exhaust surface at the top, 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.

[0020] 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.

[0021] 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.

[0022] 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.

[0023] 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.

[0024] 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.

[0025] Compared with the prior art, the present invention has the following beneficial effects:

[0026] This utility model employs a flat-mouth upper ring and a lower ring stacked together, with the upper ring port and the lower ring overlapped in a staggered arrangement to form a first fully sealed gas ring for the piston. Since the lower ring's surface is below the upper ring port, it achieves axial obstruction of the gas. The lower ring's overlap is also stepped, and even when fully open, it remains overlapped, achieving radial obstruction of the gas. This completes bidirectional sealing of the gas, allowing the gas to enter the back of this combined gas ring from the upper ring port and establish lateral pressure, preventing it from continuing downward. This ensures the overall sealing of the gas ring, effectively blocking 90% of the gas in the upper part of the gas ring groove, and the sealing of the gas ring does not decrease with wear on the outer surface of the ring.

[0027] The present invention uses a flat upper ring and a lower ring stacked together to form a gas ring groove. The upper air inlet of the gas ring groove is combined with the lower quantitative air outlet of the gas ring groove to form an arc-shaped extended path. This achieves flow restriction and guidance control of the downward combustion gas and oil, and the upward air and oil, effectively preventing excessive oil from entering the combustion chamber and excessive 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 to the piston ring and cylinder wall working surfaces.

[0028] 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.

[0029] The fully sealed structure of the piston ring reduces the pressure, temperature, and flow rate of fuel gas and oil inside and below the piston ring groove, improving the efficiency and effect of oil distribution. It completely avoids the problem of excessive leakage during initial installation of existing flat-mouth piston rings, which leads to a continuous expansion of the port as the outer circumference of the ring wears, resulting in a synchronous decline in the sealing effect of the piston ring. Attached Figure Description

[0030] Figure 1 This is a schematic diagram of the structure of this utility model;

[0031] Figure 2 A schematic diagram of the piston structure using this utility model;

[0032] Figure 3 Another front view of the piston structure using this utility model;

[0033] Figure 4 This is a schematic diagram of an existing flat-mouth gas ring structure;

[0034] Figure 5 A schematic diagram of the existing oil ring structure;

[0035] Figure 6 This is a schematic diagram illustrating the existing piston and piston ring clearance.

[0036] 1. Piston; 11. Flat-mouth upper ring; 12. Lower ring; 13. Flat-head end; 14. Narrow tongue end; 15. Wide tongue end; 16. Outer circular surface; 17. 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 port one; 32. Metering outlet port 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; 7. Top land; 72. Lower outer tangent structure. Detailed Implementation

[0037] 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.

[0038] Reference Figure 1-6 Example 1: A double-layer combined staggered fully sealed ring with a flat opening and a stepped overlap includes a gas ring 21 disposed at the head of a piston 1. The gas ring 21 includes a flat upper ring 11 and a stepped overlap lower ring 12. Both the flat upper ring 11 and the lower ring 12 are provided with elastic overlaps. The two ends of the elastic overlap of the flat upper ring 11 are flat ends 13. The two ends of the elastic overlap of the lower ring 12 are a narrow tongue end 14 and a wide tongue end 15, respectively. The narrow tongue end 14 and the wide tongue end 15 can be interlocked and sealed. The maximum opening of the narrow tongue end 14 and the wide tongue end 15 are joined at their very ends. The flat upper ring 11 and the lower ring 12 are stacked vertically, and the positions of the elastic overlaps of the flat upper ring 11 and the lower ring 12 are staggered vertically to form a fully sealed double-layer gas ring.

[0039] It also includes a piston 1, the upper part of which is the head of the piston 1 and the lower part of which is the skirt of the piston 1. The piston 1 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. The outer circumferential surface of the piston head is provided with a first piston ring groove 24, a second piston ring groove 25, and an oil ring groove 26 from top to bottom, and a first piston ring 21, a second piston ring 22, and an oil ring 23 are respectively fitted on it.

[0040] The top of the first gas ring groove 24 is the top bank 7, the space between the first gas ring groove 24 and the second gas ring groove 25 is the ring bank 2, and the space between the second gas ring groove 25 and the oil ring groove 26 is the recessed ring bank 3.

[0041] The ring bank 2 is equipped with an oil storage structure, which consists of several rows of oil storage holes or oil storage grooves arranged around the ring bank 2 according to its axial thickness. Taking two rows of oil storage holes as an example, a row of oil storage holes 51 is arranged at the same radial spacing in the middle of the outer circumference of the ring bank 2, and a row of oil storage holes 52 is arranged at the same radial spacing near the second gas ring groove 25.

[0042] For ease of processing, the oil storage hole 51 in the middle of the ring 2 is circular, and the oil storage hole 52 near the gas ring groove 25 is arc-shaped; each of the oil storage holes 51 and each of the oil storage holes 52 are arranged in an alternating position.

[0043] The depth of the first oil storage hole 51 does not exceed the depth of the first gas ring groove 24, while 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.

[0044] 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 16 of piston ring 21 and piston ring 22 and the cylinder wall, thereby improving the lubrication of piston 1.

[0045] The upper side of the air ring groove 24 has an air inlet 35 formed by the gap between the two flat ends 13 of the flat upper ring 11 (e.g., ...). Figure 1 As shown, a metering air outlet 32 ​​is provided on the lower side of the air ring groove 24, and the air inlet 35 and the metering air outlet 32 ​​are connected to the bottom of the air ring groove 24.

[0046] 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.

[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 combination of flat-mouth and stepped overlap fully sealed rings includes the following:

[0054] When piston 1 enters the compression, power, and exhaust strokes, the air, mixture, or combustion gas in the combustion chamber presses against piston 1. The upper and lower rings 11 and 12 of the compression ring 21 are compressed from the front. The bottom surface of the upper ring 11 is in close contact with the front surface of the lower ring 12, and the bottom surface of the lower ring 12 is 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 clearance of the compression ring 21, and together with another portion, is introduced into the back clearance air from the intake port 35 at the 0, 3, or 9 o'clock position on the upper side of the compression ring groove 24. A side pressure is established between the ring ring 21 and the ring groove 24, and a large amount of air, air mixture or fuel gas is blocked by the ring ring 21. A portion of the air, air mixture or fuel gas leaks downward into the ring land 2 through the radial wave-like bouncing of the ring ring 21 from the gap between the outer circular surface 16 of the ring ring and the cylinder wall and the ring body joint. The rest of the air, air 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 ring groove 24. At the same time, the oil buffered in the 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] Preferably, the second gas ring 22 of the second gas ring groove 25 can be 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 4 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 refinement of the example based on the structure of Example 1:

[0066] The gas ring 21 is a double-layer composite staggered fully sealed ring with a flat opening and a stepped overlap, due to... Figure 1 The two flat ends 13 of the flat upper ring 11 form an air inlet 35, so there is no need to set a metered air inlet 31 on the upper side of the 0, 3 or 9 o'clock position of the air ring groove 24; while a metered air outlet 32 ​​must be set at the 0 or 6 o'clock position on the lower side.

[0067] The method and requirements for inserting the gas ring 21 into 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 When 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, the port of the upper ring 11 must be aligned with the 0 o'clock position; the opening of the lower ring 12 should be aligned with the 3 o'clock or 9 o'clock position.

[0070] ③ When 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, the port of the upper ring 11 should be aligned with the 3 o'clock position; the opening of the lower ring 12 should be aligned with the 9 o'clock position.

[0071] ④ When 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, the port of the upper ring 11 should be aligned with the 9 o'clock position; the opening of the lower ring 12 should be aligned with the 3 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 selecting an existing combined oil ring or an integral oil ring for oil ring 23, the method and requirements for inserting it into the oil ring groove 26 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 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 16 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 17 of the flat-mouth upper ring 11 and lower ring 12 are pressure-bearing surfaces, causing the flat-mouth upper ring 11 and... The lower ring 12 is pressed downward and expanded radially, with its flat upper ring 11 tightly attached to the lower ring 12. The lower ring 12 is tightly attached to the lower side of the ring groove 24. The outer circular surfaces 16 of the flat upper ring 11 and the lower ring 12 are tightly attached to the cylinder wall, thereby preventing the gas from leaking from the outer circular surfaces 16 or the bottom surface of the flat upper ring 11 and the lower ring 12. Since the flat upper ring 11 and the lower ring 12 are staggered and overlapped, the sealing degree of the ring 21 is significantly increased, thereby blocking more than 90% of the gas in the upper part of the 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 annular space 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 annular space 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 aforementioned structure of the first gas ring 21 further ensures that the ring retains sufficient expansion elastic space when blocking gas flow, while keeping the expansion and contraction ports in a continuous sealing state. This achieves a high degree of sealing of the piston 1 against the downward combustion gas. In conjunction with the arc-shaped extension path formed by the first gas ring groove 24, it guides the metered combustion gas downward, purging and driving away the oil buffered in the ring land 2. Additionally, when the piston 1 enters the intake stroke, it ensures that the original path is reversed to become the upward path for oil, allowing the oil splashed or sprayed from the crankcase to enter the oil ring cavity 43, the recessed ring land 3, and the ring land 2 through the oil return hole 44. This achieves the process of oil circulation and buffer renewal at the piston head, ensuring the oil supply to the working surfaces between the first gas ring 21, the second gas ring 22, and the oil ring 23 and the cylinder wall.

[0094] 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, further achieving a high degree of sealing of the combustion gas. The amount of 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 gas and oil for a long time, so as to maintain a constant high cylinder pressure in the combustion chamber for a long time.

[0095] Under high cylinder pressure, a very small amount of oil is introduced into the combustion chamber and participates in combustion with the fuel in a manner 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 oil buffered in the labyrinthine channel of the piston head from being excessively sheared due to high-temperature vaporization, significantly extending the oil life, ensuring the lubrication performance of the oil, and significantly increasing the service life of piston 1, compression ring 21, compression ring 22, and oil ring 23.

[0096] 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.

[0097] 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.

[0098] 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 double-layer combined staggered fully sealed ring with flat opening and stepped joint, comprising an air ring (21), characterized in that, The air ring (21) includes a flat upper ring (11) and a stepped lower ring (12). Both the flat upper ring (11) and the lower ring (12) are provided with elastic joints. The two ends of the elastic joint of the flat upper ring (11) are flat ends (13). The two ends of the elastic joint of the lower ring (12) are narrow tongue end (14) and wide tongue end (15), respectively. The narrow tongue end (14) and the wide tongue end (15) can be fitted together and sealed. The maximum opening of the narrow tongue end (14) and the wide tongue end (15) is at the end of the joint. The flat upper ring (11) and the lower ring (12) are stacked on top of each other, and the position of the elastic joint of the flat upper ring (11) and the position of the elastic joint of the lower ring (12) are staggered.

2. The double-layer combined staggered fully sealed ring with flat opening and stepped overlap as described in claim 1, characterized in that, It also includes a piston (1), the upper part of which is the head of the piston (1) and the lower part of which 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. The outer circumferential surface of the piston (1) head is provided with a first gas ring groove (24), a second gas ring groove (25), and an oil ring groove (26) from top to bottom, and a first gas ring (21), a second gas ring (22), and an oil ring (23) are respectively fitted on it.

3. The double-layer combined staggered fully sealed ring with flat opening and stepped overlap as described in claim 2, characterized in that, The top of the first gas ring groove (24) is the top bank (7), the space between the first gas ring groove (24) and the second gas ring groove (25) is the ring bank (2), and the space between the second gas ring groove (25) and the oil ring groove (26) is the recessed ring bank (3).

4. The double-layer combined staggered fully sealed ring with flat opening and stepped overlap as described in claim 3, characterized in that, A row of oil storage holes (51) is arranged at the same radial spacing in the middle of the outer perimeter of the ring bank (2). A row of oil storage holes (52) is arranged at the same radial spacing in the lower part of the ring bank (2) near the gas ring groove (25). Each of the oil storage holes (51) and each of the oil storage holes (52) are arranged in an alternating position.

5. The double-layer combined staggered fully sealed ring with flat opening and stepped overlap as described in claim 2, characterized in that, The upper side of the air ring groove (24) has an air inlet (35) formed by the gap between the two flat ends (13) of the flat upper ring (11). The lower side of the air ring groove (24) is provided with a metered air outlet (32), and the air inlet (35) and the metered air outlet (32) are connected to the bottom of the air ring groove (24).

6. The double-layer combined staggered fully sealed ring with flat opening and stepped overlap as described in claim 5, 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.

7. The double-layer combined staggered fully sealed ring with flat opening and stepped overlap as described in claim 6, characterized in that, 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), and 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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