A piston first gas ring groove sealing structure

Abstract

The utility model discloses a piston first way gas ring groove sealing structure, including piston and piston head's gas ring no.

Description

Technical Field

[0001] This utility model relates to a piston ring groove structure, specifically a piston first ring groove sealing structure. 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 11 As shown in the diagram, when the piston and piston rings are installed in the cylinder (cylinder barrel), 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 round in its free state, and its outer dimension is slightly larger than the cylinder diameter. When the piston ring is installed in the cylinder barrel, 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 causes the lower bottom surface of the ring body to be pressed tightly against the lower side surface of the ring groove, and the outer surface of the ring body to be pressed 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 that is drawn upward being trapped at the piston head and unable to flow back down for renewal, which reduces the lubrication effect, shortens the oil life, and increases the wear of the piston, piston rings, and cylinder wall.

[0008] Therefore, the structure of the first piston ring groove is improved and innovated to further enhance the gas sealing effect. At the same time, it can guide and direct the downward gas flow, control the gas leakage, and block more than 90% of the air, gas mixture or gas into the first piston ring groove and the upper part of the piston ring. It also ensures that the piston head oil can circulate and renew itself, ensuring the lubrication effect. Utility Model Content

[0009] This invention proposes a piston first-stage gas ring groove sealing structure 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 piston first-stage compression ring groove sealing structure includes a piston and a piston head, a compression ring and a compression ring groove. The compression ring is fitted into the compression ring groove. The compression ring has an elastic opening and remains a fully sealed ring even when opened within the cylinder. It is a single-layer double-stepped joint with a lower incision structure, a fully sealed ring. The elastic opening has double-stepped interlocking joints at both ends. The maximum opening of the elastic opening is when the two double-stepped interlocking joints are joined together, and the minimum opening is when the two double-stepped interlocking joints overlap. The double-stepped interlocking joint is a double-layered stepped structure with staggered left and right sides and a double-layered stepped structure with staggered upper and lower parts.

[0012] Preferably, the air ring includes a front, a back, a bottom, a double-step joint one, a double-step joint two, and an outer circular surface.

[0013] Preferably, when the first air ring opens in the cylinder, its maximum elastic opening is such that the two double-step interlocking joints are joined at their very ends. The first double-step interlocking joint and the second double-step interlocking joint form an interlocking joint, which is divided into two layers. The upper and lower layers are both stepped interlocking joints, with the upper and lower steps radially offset and the left and right ends double-step interlocking.

[0014] Preferably, a concave arc-shaped hole is provided at the right angle of the upper step of the double-step joint. The arc-shaped hole facilitates the right-angle milling of the upper step of the double-step joint with a milling cutter, and its arc-shaped structure also serves as an arc-shaped gas passage for buffering and depressurizing leaked gas.

[0015] Preferably, the bottom surface of the air ring has a ring with an inner circumference near the back side.

[0016] 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 a cylinder. The upper part of the piston head is the combustion chamber, and the lower part of the piston skirt is the crankcase. Below the first piston ring groove, there is a second piston ring groove and an oil ring groove. The second piston ring groove and the oil ring groove are respectively fitted with a second piston ring and an oil ring. There is a ring land between the first piston ring groove and the second piston ring groove; there is a recessed ring land between the second piston ring groove and the oil ring groove.

[0017] Preferably, a metering air inlet is provided on the upper side of the air ring groove, and a metering air outlet is provided on the lower side of the air ring groove, and the metering air inlet and the metering air outlet are connected to the bottom of the air ring groove.

[0018] 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.

[0019] Preferably, the first quantitative air inlet can be set 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 first quantitative air inlet is preferably set at the 9 o'clock, 0 o'clock, or 3 o'clock position on the upper side of the air ring groove. The first quantitative air outlet should be set at the 0 o'clock or 6 o'clock position on the lower side of the air ring groove.

[0020] 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 two rows of oil storage holes as an example, one row of oil storage holes is arranged at the same radial spacing in the middle of the outer circumference of the ring bank, and another row of oil storage holes is arranged at the same radial spacing near the second gas ring groove. The oil storage hole one in the middle of the ring bank is circular, and the oil storage hole two near the second gas ring groove is arc-shaped; each of the oil storage holes one and each of the oil storage holes two are arranged in an alternating position.

[0021] The depth of the first oil storage hole does not exceed the depth of the first gas ring groove, 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.

[0022] Preferably, the size of the metered air inlet and metered air 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 leaking out is not affected by the wear of the air ring, and a fixed amount of gas flow can be maintained for a long time.

[0023] 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.

[0024] 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.

[0025] 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.

[0026] Compared with the prior art, the present invention has the following beneficial effects:

[0027] This invention provides a double-stepped interlocking joint in both the longitudinal and transverse directions at the elastic opening of the piston ring, ensuring that the piston ring retains sufficient expansion elastic space when blocking gas, while keeping the expansion and contraction joints in a continuous state, thus achieving complete gas sealing. This results in more than 90% of the air, gas mixture, or fuel gas being blocked in the upper part of the piston ring, and the sealing degree of the piston ring does not decrease with the wear of the outer circular surface of the ring.

[0028] At the same time, by combining the ring groove with the setting of a fixed amount of air inlet and outlet, a U-shaped path or arc-shaped extended path is formed to achieve flow restriction and guidance control of the downward combustion gas and oil, and the upward air and oil. This effectively prevents too much oil from entering the combustion chamber and too much 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 between the piston rings and the cylinder wall working surface.

[0029] Furthermore, the resulting arc-shaped extended path increases the travel distance of the downward-flowing fuel and oil, increases the travel distance of the upward-flowing air and oil, reduces the upward speed of the oil, and improves the effects of flow restriction, diversion, buffering, and caching.

[0030] The lower inner tangent structure of the first gas ring increases the gap between the back of the first gas ring and the gas ring groove, which increases the expansion space of the downward gas, which is beneficial to the pressure reduction and cooling of the gas, and increases the capacity to contain the upward engine oil, preventing too much engine oil from entering the combustion chamber, while appropriately reducing the elasticity of the first gas ring.

[0031] The fully sealed structure of the piston ring reduces the pressure, flow rate, and temperature of the combustion gas and engine oil inside and at the bottom of 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

[0032] Figure 1 A schematic reference diagram showing the flow direction of air, mixture or combustion gas (downward) in the piston head when the piston using the structure of this utility model is in the compression, power and exhaust strokes;

[0033] Figure 2 This is a schematic reference diagram showing the flow direction of air and oil (upward) at the piston head when the piston with the structure of this utility model is in the intake stroke;

[0034] Figure 3 A three-dimensional schematic diagram of a piston employing the structure of this utility model;

[0035] Figure 4 A front view of a piston employing the structure of this utility model;

[0036] Figure 5 The first air ring of this utility model is a front enlarged schematic diagram of the front of the joint of a single-layer double-step joint with an inwardly tangential structure fully sealed ring.

[0037] Figure 6 This is an enlarged schematic diagram of the bottom surface of the overlap of a single-layer double-step overlap with an inwardly tangential structure fully sealed ring, which is the air ring of this utility model.

[0038] Figure 7 This is a schematic diagram of the existing flat-mouth gas ring.

[0039] Figure 8 This is a schematic reference diagram showing the flow direction of air, mixture, or combustion gas (downward) in the piston head during the compression, power, and exhaust strokes of an existing piston.

[0040] Figure 9 This is a schematic diagram showing the flow direction of air and oil (upward) in the piston head when the piston is in the intake stroke.

[0041] Figure 10 A schematic diagram of the existing oil ring structure;

[0042] Figure 11 This is a schematic diagram illustrating the existing piston and piston ring clearance.

[0043] 1. Piston; 11. Front; 12. Back; 13. Bottom; 14. Double-step joint one; 15. Double-step joint two; 16. Outer circular surface; 17. Concave arc hole; 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. Concave ring land; 31. Metering inlet hole one; 32. Metering outlet hole one; 41. Upper scraper of oil ring; 42. Lower scraper of oil ring; 43. Oil ring cavity; 44. Oil return hole; 51. Oil reservoir hole one; 52. Oil reservoir hole two; 6. Flat-mouth compression ring; 61. Valve inlet surface; 62. Valve exhaust surface; 7. Top land; 71. Lower inner tangent structure; 72. Lower outer tangent structure. Detailed Implementation

[0044] 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.

[0045] Reference Figure 1-11 ,in: Figure 8 This is a schematic reference diagram showing the flow direction of air, mixture, or combustion gas (downward) in the piston head during the compression, power, and exhaust strokes of an existing piston. Figure 9 This is a schematic diagram showing the flow direction of air and oil (upward) in the piston head when the piston is in the intake stroke.

[0046] Example 1

[0047] A piston first-stage compression ring groove sealing structure includes a piston 1 and a compression ring 21 and a compression ring groove 24 at the piston 1 head. The compression ring 21 is fitted into the compression ring groove 24. The compression ring 21 has an elastic opening and remains a fully sealed ring even when opened within the cylinder. It is a single-layer double-stepped joint with a lower incision structure, forming a fully sealed ring. The elastic opening has double-stepped interlocking joints at both ends. The maximum opening of the elastic opening is when the two double-stepped interlocking joints are joined together, and the minimum opening is when the two double-stepped interlocking joints overlap. That is, the maximum diameter of the joint opening within the cylinder and the minimum diameter of the compression opening. The double-stepped interlocking joint is a double-layered stepped structure with alternating left and right sides, and also with alternating upper and lower parts.

[0048] The air ring 21 includes a front surface 11, a back surface 12, a bottom surface 13, a double-step joint 14, a double-step joint 25, and an outer circular surface 16.

[0049] When the air ring 21 opens in the cylinder, its maximum elastic opening is such that the two double-step interlocking joints are joined at their very ends. The double-step interlocking joint 14 and the double-step interlocking joint 15 form an interlocking joint. The interlocking joint has two layers, with both the upper and lower layers being stepped interlocking joints. The upper and lower steps are radially staggered, and the left and right ends are double-stepped and interlocked.

[0050] The double-step joint 14 has a long tongue end near the back of the ring, and the double-step joint 15 has a short tongue end near the outer circular surface 16, and the long tongue end and the short tongue end are interlocked.

[0051] A concave arc hole 17 is provided at the right angle of the upper step of the double-step joint 14. The concave arc hole 17 facilitates the milling cutter to perform right-angle milling on the upper step of the double-step joint 14, and its arc-shaped structure also serves as an arc-shaped gas passage for buffering and depressurizing leaked gas.

[0052] The bottom surface 13 of the air ring 21 is provided with a ring of inwardly tangent structure 71 on the side near the back surface 12.

[0053] 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 head is the combustion chamber, and the lower part of the piston skirt is the crankcase. The piston ring groove 24 is provided with a piston ring groove 25 and an oil ring groove 26. The piston ring groove 25 and the oil ring groove 26 are respectively fitted with a piston ring 22 and an oil ring 23. The piston ring groove 24 and the piston ring groove 25 are connected by a ring land 2; the piston ring groove 25 and the oil ring groove 26 are connected by a recessed ring land 3.

[0054] A metering air inlet hole 31 is provided on the upper side of the air ring groove 24, and a metering air outlet hole 32 is provided on the lower side of the air ring groove 24. The metering air inlet hole 31 and the metering air outlet hole 32 are connected to the bottom of the air ring groove 24.

[0055] 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.

[0056] The quantitative air inlet 31 can be set 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. The quantitative air inlet 31 is preferably set at the 9 o'clock, 0 o'clock, or 3 o'clock position on the upper side of the air ring groove 24. The quantitative air outlet 32 ​​should be set at the 0 o'clock or 6 o'clock position on the lower side of the air ring groove 24.

[0057] The ring bank 2 is equipped with an oil storage structure, which consists of several rows of oil storage holes 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. The oil storage holes 51 in the middle of the ring bank 2 are circular, and the oil storage holes 52 near the second gas ring groove 25 are arc-shaped; the oil storage holes 51 and 52 are arranged in staggered positions.

[0058] 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.

[0059] 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:

[0060] 1. When the quantitative air inlet 31 is set at the 0 o'clock position and the quantitative air outlet 32 ​​is set at the 0 o'clock position, the quantitative air inlet 31, the gap between the back of the air ring 21 and the bottom of the air ring groove 24, and the quantitative air outlet 32 ​​form a new U-shaped path for air, mixed gas or fuel gas to descend.

[0061] 2. When the quantitative air inlet 31 is set at the 0 o'clock position and the quantitative air outlet 32 ​​is staggered and set at the 6 o'clock position, the quantitative air inlet 31, the gap between the back of the air ring 21 and the bottom of the air ring groove 24, and the quantitative air outlet 32 ​​form two new arc-shaped extension paths of equal length for air, mixed gas or fuel gas to descend.

[0062] 3. When the quantitative air inlet 31 is set at the 3 o'clock position and the quantitative air outlet 32 ​​is set at the 0 o'clock position, the quantitative air inlet 31, the gap between the back of the air ring 21 and the bottom of the air ring groove 24, and the quantitative 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.

[0063] 4. When the quantitative air inlet 31 is set at the 9 o'clock position and the quantitative air outlet 32 ​​is set at the 0 o'clock position, the quantitative air inlet 31, the gap between the back of the air ring 21 and the bottom of the air ring groove 24, and the quantitative air 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.

[0064] 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, while the other part passes through the new U-shaped path of the ring groove-24 or through the new arc-shaped extended path. At the same time as 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 lander 2.

[0065] Based on the above-mentioned piston first-stage gas ring groove sealing structure and its gas-blocking sealing and flow guiding method, the following are included:

[0066] 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 front 11 of piston ring 21 is compressed, and the lower bottom 13 is in close contact with the lower side of piston ring groove 24. A small portion of air, mixture, or combustion gas enters the back clearance from the upper side gap of piston ring 21, and together with another portion, it is introduced into the back clearance space from the metered intake port 31 at the 0, 3, or 9 o'clock position on the upper side of piston ring groove 24 to establish side pressure. A large amount of air, mixture, or combustion gas is thus blocked by piston ring 21 and piston ring groove 24. A portion of air, mixture, or combustion gas leaks downward into ring land 2 through the radial wave-like bouncing of piston ring 21 from the outer circular surface 16 of the ring body and the cylinder wall and the gap of the ring body joint. The remaining air, mixture, or combustion gas is introduced into ring land 2 from the metered exhaust port 32 at the 0 or 6 o'clock position on the lower side of piston ring groove 24. At the same time, the oil buffered in piston ring groove 24 and ring land 2 is blown downward and driven away.

[0067] When piston 1 enters the intake stroke, the oil moves upwards in the opposite direction along the downward 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 clearance of the piston ring 21, the metering outlet 32, and the metering intake 31. The high-density, viscous oil, however, is mostly blocked at the bottom of the small metering outlet 32. The oil, struggling to pass through the narrow lower clearance 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 escapes through the metering intake 31 and enters the combustion chamber. When this tiny amount of oil is introduced onto the surface of the piston ring 21, piston 1 switches to the compression stroke, and the oil is promptly blown downwards by the air or air-fuel mixture.

[0068] 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.

[0069] 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.

[0070] The size of the metered air inlet hole 31 and metered air outlet hole 32 can be customized according to the requirements of different vehicle engines, so as to achieve a customizable amount of gas entering the ring 2. The amount of gas leakage is not affected by the wear of the air ring 21, and a fixed amount of gas flow can be maintained stably for a long time.

[0071] 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.

[0072] 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.

[0073] 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.

[0074] If a combined oil ring is used, it includes an upper scraper 41, an inner liner, and a lower scraper 42. The upper scraper 41 and the lower scraper 42 clamp the inner liner in the middle to form an oil ring cavity 43.

[0075] If an integrated oil ring is used, it 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.

[0076] Example 2

[0077] This is a further refinement of the accompanying embodiment based on the structure of Embodiment 1.

[0078] The air ring 21 is a single-layer, double-step overlap ring with a lower incision structure and a fully sealed ring. The overlap is as follows: Figure 5 , Figure 6 As shown, a metered air inlet hole 31 needs to be provided on the upper side of the 0, 3 or 9 o'clock position of the air ring groove 24; and a metered air outlet hole 32 needs to be provided on the lower side of the 0 or 6 o'clock position.

[0079] Installation method and requirements of the gas ring 21:

[0080] ① If the quantitative air inlet 31 is set at the 0 o'clock position and the quantitative air outlet 32 ​​is set at the 0 o'clock position, then the opening of the air ring 21 must be aligned with the 3 o'clock or 9 o'clock position.

[0081] ② If the quantitative air inlet 31 is set at the 0 o'clock position and the quantitative air outlet 32 ​​is set at the 6 o'clock position, then the opening of the air ring 21 must be aligned with the 3 o'clock or 9 o'clock position.

[0082] ③ If the quantitative air inlet 31 is set at the 3 o'clock position and the quantitative air outlet 32 ​​is set at the 0 o'clock position, then the opening of the air ring 21 should be aligned with the 9 o'clock position.

[0083] ④ If the quantitative air inlet 31 is set at the 9 o'clock position and the quantitative air outlet 32 ​​is set at the 0 o'clock position, then the opening of the air ring 21 should be aligned with the 3 o'clock position.

[0084] The second gas ring groove 25 is a commonly used existing structure, and the second gas ring 22 is an existing flat-mouth gas ring 6 with a lower outer tangent structure.

[0085] Installation method and requirements for gas ring 22 (flat-mouth gas ring 6):

[0086] The flat-mouth air ring 6 is an existing mature technology, and its installation method is the same as the existing method.

[0087] 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.

[0088] 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 air ring must be aligned with the 0 o'clock position.

[0089] The installation method of the combined oil ring or the integrated oil ring is the same as that of the existing methods.

[0090] Detailed working principle of the combined use of gas ring groove 24 and gas ring 21:

[0091] First, when piston 1 enters the power and exhaust strokes, the high-temperature, high-pressure combustion gases in the combustion chamber impact piston 1, causing piston 1 to move downwards. The combustion gases descend from the gap between the piston 1's top (fire) bank 7 and the cylinder wall, putting pressure on the front 11 of the compression ring 21. The bottom 13 of the compression ring 21 is in close contact with the lower side of the compression ring groove 24. Simultaneously, the combustion gases enter the back of the ring from the upper side gap of the compression ring 21 and the metering intake port 31, making the back 12 of the compression ring 21 also a pressure surface. The outer circular surface 16 of the ring body is in close contact with the cylinder wall. The pressure of the descending combustion gases causes the compression ring 21 to compress downwards and expand radially, thereby preventing the combustion gases from leaking down from the outer circular surface 16 or the bottom surface 13 of the compression ring 21. In addition, the double-stepped interlocking joint of the ring body, with both the upper and lower layers being stepped joints, and the upper and lower steps being radially staggered, and the left and right ends being double-stepped and staggered, significantly increases the sealing of the compression ring 21. The sealing structure between the gas ring groove 24 and the gas ring 21 allows the gas ring 21 to rely on its own elasticity for the first seal and the gas force for the second seal, thereby blocking more than 90% of the gas above the gas ring groove 24.

[0092] Some of the combustion gas will leak downwards into the ring land 2 through the radial wave-like bouncing of the ring body as it moves up and down, from the gap between the outer circular surface 16 of the ring body and the cylinder wall, as well as the ring body overlap gap. The guided combustion gas enters the gap between the back of the ring body and the bottom of the ring groove 24 through the metered intake port 31 at the 0 o'clock, 3 o'clock or 9 o'clock position. Then, together with the combustion gas entering from the upper side gap, it is guided into the ring land 2 through the metered exhaust port 32 at the lower 0 o'clock or 6 o'clock position.

[0093] When the gas ring 21 expands, the bottom surface 13 is provided with a ring of inwardly tangent structure 71 on the side near the back surface 12, which increases the back clearance space of the gas ring 21. This is beneficial for the expansion, decompression, and cooling of the gas, and appropriately reduces the elasticity of the ring body. At the same time, it produces a slight torsional effect, which is beneficial for the piston 1 to distribute oil evenly when it moves upward and to scrape off excess oil from the cylinder wall when it moves downward.

[0094] As described above, the metered air inlet 31 is located at the 0 o'clock position on the upper side of the gas ring groove 24, while the metered air outlet 32 ​​is correspondingly located at the 0 o'clock position on the lower side. The high-temperature, high-pressure combustion gas in the combustion chamber is introduced through the metered air inlet 31 at the 0 o'clock position. Simultaneously, the gas creates lateral pressure on the back of the gas ring 21 at the narrow bottom of the gas ring groove 24, and leaks into the outer space of the annular land 2 from the corresponding metered air outlet 32 ​​at the 0 o'clock position. The new U-shaped path formed from the metered air inlet 31 to the metered air outlet 32 ​​achieves the effects of limiting, guiding, cooling, and depressurizing the combustion gas. Only a small amount of combustion gas can enter the annular land 2 through this U-shaped channel.

[0095] The staggered arrangement of the metered air inlet 31 and metered air outlet 32 ​​creates a new arc-shaped extended path between them, increasing the gas flow path and enhancing the effects of limiting, guiding, cooling, and reducing gas flow. Only a small amount of gas can enter the ring bank 2 through this multi-bend arc-shaped extended channel.

[0096] 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 metered intake port 31, and is extinguished due to heat loss and temperature reduction.

[0097] Because the sizes of the metered air inlet port 31 and the metered air outlet port 32 are customizable, the amount of gas entering the annular space 2 can be customized. A stable and 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.

[0098] The sealing structures of the first and second ring grooves 24 and 21 connect to the second and second ring grooves 25 and 22, and the oil ring grooves 26 and 23. The sealing structures of the first and second ring grooves 24 and 21 limit and guide the 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 and second ring grooves 25, the recessed ring land 3, and the oil ring cavity 43, thus meeting the lubrication requirements of the piston head 1.

[0099] The compression ring 21 is designed with increased thickness, meaning its thickness is 1.5 to 2 times greater than existing compression rings. This significantly improves heat conduction at the contact surface between the compression ring 21 and the cylinder wall, preventing high temperatures at the piston head. Simultaneously, combined with the structural design of the compression ring groove 24, the combustion gas undergoes flow restriction, guidance, pressure reduction, and cooling through a new U-shaped or arc-shaped extended path formed by the metered intake port 31, the ring back, and the metered outlet port 32. This results in a more gentle flow of combustion gas entering the ring land 2, avoiding the violent scavenging that occurs when the compression ring 21 is a traditional flat-mouth compression 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 to the compression ring groove 24. When the oil is blown downward, the buffered oil is released while turbulence is present. 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.

[0100] 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.

[0101] 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.

[0102] 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.

[0103] 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.

[0104] 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.

[0105] 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.

[0106] 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 U-shaped or arc-shaped extended 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.

[0107] In this embodiment, 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.

[0108] Under high cylinder pressure, a very small amount of engine oil is introduced into the combustion chamber, participating in near-complete combustion with the fuel. This completely avoids the formation of carbon black and gum, thus preventing carbon buildup on 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 excessive shearing of the oil buffered in the labyrinthine channels of the piston head due to high-temperature vaporization, significantly extending oil life, ensuring lubrication performance, and significantly increasing the service life of piston 1, compression ring 21, compression ring 22, and oil ring 23. Simultaneously, it achieves energy saving and emission reduction, significantly improving engine efficiency and extending engine life.

[0109] This invention achieves over 90% gas blockage within the first gas ring groove, allowing for better control of the gas flow along the labyrinthine channel, enabling effective flow preparation, and effectively controlling the upward flow of engine oil. This ensures good overall circulation and reciprocating motion of the piston 1, guaranteeing its service life.

[0110] The aforementioned gas ring sealing structure is applicable to piston air compressors, piston refrigeration machines, and piston-type lifting equipment. Specifically, a piston air compressor or air compressor piston, piston refrigeration machine or refrigeration machine piston, piston-type lifting equipment, or other equipment piston all adopt the aforementioned gas ring sealing structure.

[0111] 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.

[0112] 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 first gas ring groove sealing structure, comprising a piston (1) and a gas ring first (21) and a gas ring groove first (24) on the head of the piston (1), wherein the gas ring first (21) is sleeved in the gas ring groove first (24), characterized in that, The first air ring (21) is provided with an elastic opening and remains a fully sealed ring when it is opened in the cylinder. It is a single-layer double-step joint with a lower incision structure fully sealed ring. The corresponding two ends of the elastic opening are provided with double double-step insertion joints. The first air ring (21) includes a front (11), a back (12), a bottom (13), a double-step joint one (14), a double-step joint two (15), and an outer circular surface (16). When the first air ring (21) opens in the cylinder, its maximum elastic opening is the two double-step interlocking joints at the very end of the joint. The double-step interlocking joint one (14) and the double-step interlocking joint two (15) form an interlocking joint. The interlocking joint is divided into two layers. The upper and lower layers are both stepped interlocking joints. The upper and lower steps are radially staggered, and the left and right ends are double-step staggered and interlocked.

2. The piston first ring groove sealing structure according to claim 1, characterized in that, A concave arc hole (17) is provided at the right angle of the upper step of the double-step joint (14).

3. The piston first ring groove sealing structure according to claim 1, characterized in that, The bottom surface (13) of the air ring (21) is provided with a ring of inward tangent structure (71) on the side near the back (12).

4. The piston first ring groove sealing structure according to claim 1, characterized in that, 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 a 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 first ring groove (24) is provided with a second ring groove (25) and an oil ring groove (26). The second ring groove (25) and the oil ring groove (26) are respectively fitted with a second ring (22) and an oil ring (23). The first ring groove (24) and the second ring groove (25) are connected by a ring lander (2), and the second ring groove (25) and the oil ring groove (26) are connected by a recessed ring lander (3).

5. The piston first ring groove sealing structure according to claim 4, characterized in that, A metered air inlet hole (31) is provided on the upper side of the air ring groove (24), and a metered air outlet hole (32) is provided on the lower side of the air ring groove (24). The metered air inlet hole (31) and the metered air outlet hole (32) are connected to the bottom of the air ring groove (24).

6. The piston first ring groove sealing structure according to 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 piston first ring groove sealing structure according to claim 6, characterized in that, The quantitative air inlet (31) can be set at any position on the upper side of the air ring groove (24) corresponding to the 9 o'clock to 0 o'clock or 0 o'clock to 3 o'clock position. The quantitative air inlet (31) is preferably set at the 9 o'clock, 0 o'clock or 3 o'clock position on the upper side of the air ring groove (24). The quantitative air outlet (32) should be set at the 0 o'clock or 6 o'clock position on the lower side of the air ring groove (24) corresponding to the 0 o'clock or 6 o'clock position.

8. The piston first ring groove sealing structure according to claim 7, characterized in that, A row of oil storage holes (51) is arranged at the same radial spacing on 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 on 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.

Images