Radial sealing fin surface microstructure of cycloid rotor engine

Abstract

The invention discloses a surface micro-texture of a radial sealing fin of a cycloid rotor engine. The surface micro-texture comprises a double-layer herringbone groove, a sealing weir area and a sealing dam area. The double-layer herringbone groove is formed in the contact surface of the rotor, gas enters the groove from the upper-layer gas inlet and the lower-layer gas inlet in the vertex angle of the herringbone groove, the maximum pressure value is achieved in the groove, and the gas is exhausted from the upper-layer gas outlet and the lower-layer gas outlet after the pressure difference effect is completed. A plurality of pairs of herringbone grooves are evenly distributed in the radial sealing piece, a sealing weir area is arranged between every two adjacent pairs of herringbone grooves in the axial direction, and a sealing dam area is arranged on the outer side. The herringbone grooves are of an axial symmetry structure, the groove depth is 1-5 micrometers, the number of the herringbone grooves is 2-10 pairs, and the edges can be straight lines, arc lines, spiral lines or sawtooth lines. Gas enables the radial sealing fins and the rotor to be tightly adsorbed through pressure difference, and the sealing weir area and the sealing dam area provide multi-layer sealing protection. The air tightness problem of the radial sealing piece is solved, the stable radial sealing performance of the cycloid rotor engine is achieved, and gas leakage is remarkably reduced.

Description

Technical Field

[0001] The present invention belongs to the field of engine radial seal, and specifically relates to a cycloid rotor engine radial seal surface micro-texture Background Art

[0002] Both the cycloid rotor engine and the reciprocating piston engine rely on the expansion pressure generated by fuel combustion to obtain power. Unlike the reciprocating piston engine, the rotor of the cycloid rotor engine rotates in one direction, that is, the rotor rotates continuously along a fixed path in the casing. The rotor rotates around the eccentric shaft, and the rotational motion of the eccentric shaft is directly transmitted to the external output torque through the rotor. Since the rotor is directly connected to the eccentric shaft, the structure of the connecting rod and the crankshaft is omitted. On the one hand, the power of the rotor can be transmitted to the eccentric shaft more directly and efficiently, thereby outputting mechanical power; on the other hand, the radial sealing plate becomes the core component to ensure the efficient operation of the cycloid rotor engine. The design of the radial sealing plate and the quality of the materials used directly affect the durability, reliability, power output and environmental performance of the cycloid rotor engine.

[0003] The current cycloid rotor engine mainly relies on direct sealing, that is, the contact between the radial sealing sheet and the rotor to achieve the purpose of sealing. Through the rotation of the rotor and the fixed position of the radial sealing sheet, the radial sealing sheet always keeps in contact with the rotor. The principle of direct sealing is to seal the gas through direct contact of the radial sealing sheet during the operation of the engine to prevent the gas between different cylinders from flowing, thereby ensuring the combustion performance of the cycloid rotor engine. The radial sealing sheet at the top of the rotor directly contacts the inner wall of the casing to form a seal without an additional isolation layer or structure.

[0004] Direct sealing faces some challenges and defects. First, the direct contact between the radial seal and the inner wall of the casing will generate friction, resulting in wear of the radial seal and the casing. Over time, wear causes the performance of the sealing system to decline, increasing the risk of air leakage, thereby affecting the combustion efficiency and performance of the engine. Second, during the operation of the cycloidal rotor engine, temperature changes will cause thermal expansion and deformation of the material. The gap between the radial seal and the inner wall of the casing will change with temperature. When the gap is too large, it will cause air leakage, and when the gap is too small, it will increase friction and wear. Third, uneven thermal expansion will also lead to stress concentration and increase the risk of damage to the radial seal. The uneven expansion of the radial seal will cause structural deformation of the entire sealing system, affecting the overall performance and life of the engine. Fourth, long-term high-temperature operation and temperature cycling will cause thermal fatigue of the radial seal material. The radial seal is prone to failure in high temperature and thermal cycling, resulting in reduced sealing performance and affecting the efficiency and emissions of the engine. Fourth, since the high-temperature and high-pressure gas generated during fuel combustion will expand and explode rapidly, this pressure fluctuation and impact force phenomenon will cause the radial seal to be subjected to periodic high-pressure shocks, causing deformation, displacement or wear of the radial seal, thereby affecting the sealing effect.

[0005] In actual applications, the operation of the cycloid rotor engine will lead to unstable sealing. When the speed is too high, the sealing may fail. In addition, the sealing of this sealing method is related to the surface morphology of the seal. Different surface morphologies of the seal may lead to huge differences in the sealing effect. At the same time, the unstable rotation of the rotor will make its contact with the seal unstable, increase the wear of the seal, and lead to poor sealing effect or failure. The root cause of the above problems is the vibration, leakage, wear and vibration of the radial sealing plate of the cycloid rotor engine.

[0006] Specifically, the vibration of the radial seal is the pulsating beating of the radial seal on the cylinder profile, which is called the vibration of the seal. The vibration phenomenon will cause leakage at the seal and cylinder vibration, and at the same time aggravate the wear of the seal, which will reduce the power and life of the engine. Specifically, the cylinder vibration phenomenon is the wavy wear phenomenon on the cylinder profile. Due to the poor durability of the radial seal and the cylinder profile, vibration often occurs in the combustion area of ​​the cylinder profile, as shown in the following figure. Figure 4 As shown. Cylinder vibration marks are extremely harmful. They will damage the seal of the engine, aggravate the wear and even break of the sealing plate, and have a bad impact on the performance and service life of the rotor machine. Specifically, air leakage at the seal of the radial sealing plate of the rotor machine is the main reason for the performance difference between the rotor machine and the reciprocating machine. When the engine speed decreases, the air leakage will be more obvious. The air leakage will reduce the maximum torque and increase the specific fuel consumption. The gas leakage path in the rotor machine cylinder, such as Figure 5As shown in the figure, one is leakage to the adjacent working room through the radial sealing piece, and the other is leakage from the end face through the end face gas seal strip. The former accounts for about 2 / 3-3 / 4 of the total leakage, while the leakage to the end face is less. Specifically, the wear of the radial sealing piece means that after the rotor machine has been running for a period of time, the top arc of the radial sealing piece will wear. Wear will affect the cylinder geometry accuracy of the rotor machine, the sealing performance and the service life of the engine.

[0007] A Chinese patent (CN106401786A) discloses a sealing device for a micro-rotor engine. By improving the design of the sealing sheet and the spring sheet, the sealing performance is improved and the leakage is reduced. However, there are still challenges in terms of complex manufacturing and assembly, durability of the spring sheet, wear, thermal expansion and dynamic response performance. Specifically, the sealing sheet and the spring sheet are in contact with the rotor and the cylinder during operation, and there are problems of friction and wear. Although the design reduces the leakage area, friction and wear may shorten the life of the sealing sheet and the spring sheet, affecting the sealing effect. Especially in high temperature and high pressure working environments, the wear resistance and fatigue resistance of the material are a challenge. Specifically, although the sealing sheet design reduces the leakage area, there is still a certain risk of leakage. In the actual working process, the sealing effect of the bottom of the sealing sheet and the spring sheet may be affected by many factors, such as manufacturing tolerances, assembly errors and changes in working conditions. Specifically, high temperatures are generated when the rotary engine is working, and the sealing sheet and the spring sheet may generate thermal stress due to thermal expansion, which may cause sealing failure or component damage. In particular, the different thermal expansion coefficients of different materials may cause relative movement and stress concentration between mating components. Specifically, the sealing sheet 2 and the spring sheet generate high-frequency vibration and impact when the rotary engine runs at high speed. The sealing effect under dynamic conditions is different from that of the static design, and the dynamic characteristics of the spring sheet 5 need to be optimized.

[0008] The Chinese utility model patent (CN220416239U) proposes a dry gas sealing structure that imitates an F-shaped dynamic pressure groove, attempting to improve the sealing performance, but there are still certain challenges and potential defects in thermal management and dynamic pressure opening effect. Specifically, although the distribution and micro-texture of the dynamic pressure groove are taken into account in the design to reduce the temperature, in actual operation, the friction and gas compression between the dynamic ring and the static ring still cause the end surface temperature to be too high. When the engine runs for a long time, it is easy to affect the performance and life of the sealing material. Specifically, although the dynamic pressure opening effect is improved by imitating the F-shaped dynamic pressure groove in the design, the dynamic pressure effect may still not be sufficient to completely prevent leakage during the initial startup stage, especially at low speed or stopped state. The dynamic pressure effect is highly dependent on the rotation speed, and the sealing effect is not ideal when the speed is low.

[0009] It can be seen that the existing technology currently uses the contact between the rotor and the radial sealing sheet to prevent the curved surface leakage of the radial sealing sheet. The sealing efficiency is average, the friction loss is large, and it is difficult to achieve a better anti-leakage effect. Summary of the invention

[0010] The actual working conditions of the cycloid rotor engine and the shortcomings of the existing technology show that the main obstacle in the development of the cycloid rotor engine is the radial seal. This requires improving the sealing effect and durability by improving the sealing structure design and material selection, thereby extending the service life of the cycloid rotor engine and improving its working performance.

[0011] In order to solve the above technical problems, the present invention aims to provide a surface micro-texture of a radial sealing sheet of a cycloidal rotor engine. The following is a specific technical solution adopted:

[0012] The present invention discloses a radial sealing plate with a surface micro-texture for a cycloidal rotor engine, i.e., a brand-new radial sealing plate with a slotted structure for use on a cycloidal rotor engine. The contact surface of the radial sealing plate with the rotor is provided with a double-layer herringbone groove 101. The double-layer herringbone groove 101 includes a plurality of pairs, each pair of herringbone grooves 101 has an equal groove depth, a grooveless sealing weir area 102 is provided between each pair of herringbone grooves 101, and a sealing dam area 103 is provided along the rotation direction of the rotor.

[0013] The present invention opens a double-layer herringbone groove 101 on the surface in contact with the rotor, and the herringbone groove 101 of the radial sealing plate enters the upper air inlet 201 and the lower air inlet 202 on the high-pressure air inlet side, and the maximum pressure is reached in the groove of the herringbone groove 101. Correspondingly, the gas is discharged from the upper air outlet 203 and the lower air outlet 204, thereby achieving exhaust from the high-pressure area on the right to the low-pressure area on the left.

[0014] After the gas flows into the groove, the pressure difference is generated due to the different pressures at different positions, which produces a negative pressure, thereby generating an adsorption force to adsorb the radial sealing sheet and the rotor together, thereby achieving the sealing purpose.

[0015] The herringbone grooves 101 are opened in the middle area of ​​the radial sealing sheet 1 and are evenly arranged in the circumferential direction and the length direction. Each herringbone groove 101 has an upper air inlet 201 and a lower air inlet 202 as a gas inlet, and then flows into the groove to reach the maximum pressure in the groove of the herringbone groove 101. Correspondingly, the gas is discharged from the upper air outlet 203 and the lower air outlet 204 to achieve exhaust from the high-pressure area on the right to the low-pressure area on the left, so as to achieve effective sealing when the radial sealing sheet 1 contacts the rotor 4 and optimize the gas flow path;

[0016] The sealing weir area 102 is provided in the middle part between two adjacent herringbone grooves 101 and is evenly distributed along the axial direction of the radial sealing sheet 1, forming a complementary structure with the double-layer herringbone grooves 101 to achieve primary blocking and airflow control;

[0017] The sealing dam area 103 is provided at the outer edge of the radial sealing sheet and arranged along the rotation direction of the rotor. There is no physical separation between the sealing dam area 103 and the double-layer herringbone groove 101, so that a continuous seamless connection is formed to achieve a smooth transition of the airflow.

[0018] The double-layer herringbone grooves 101 are distributed on the surface of the radial sealing sheet 1, and are divided into two layers of herringbone grooves 101, with the upper herringbone grooves 101 on the outside and the lower herringbone grooves 101 on the inside; the upper herringbone grooves 101 and the lower herringbone grooves 101 of the double-layer herringbone grooves 101 can be arranged alternately to maintain the continuity of the gas flow path; the upper herringbone grooves 101 and the lower herringbone grooves 101 of the double-layer herringbone grooves 101 maintain an equal vertical distance between them, ensuring that each layer of herringbone grooves 101 is relatively independent, so that the gas can flow freely between the layers; the double-layer herringbone grooves 101 structure is symmetrically distributed along the symmetry center line 104 of the radial sealing sheet 1, forming an axisymmetric structure, so that the radial sealing When the sheet 1 contacts the surface of the rotor 4, the airflow flows evenly in all directions, forming a uniform negative pressure and adsorption force; the airflow in the double-layer herringbone groove 101 enters the groove from the upper air inlet 201 and the lower air inlet 202 at the same time, and the gas flow pattern in the groove changes dramatically, and then the gas is discharged from the upper air outlet 203 and the lower air outlet 204; the double-layer herringbone groove 101 forms a high-pressure area and a low-pressure area in the groove due to the negative pressure effect; the high-pressure area is mainly located at the upper air inlet 201 and the lower air inlet 202, and the middle position of part of the groove; the low-pressure area is mainly located in the middle of the groove and the upper air outlet 203 and the lower air outlet 204 in the outlet area.

[0019] The herringbone grooves 101 in each layer are arranged parallel to each other, maintaining a fixed interval and parallel relationship, extending from the edge of the radial sealing sheet 1 to the center, forming a plurality of independent flow channels; the high-pressure gas first enters the upper herringbone grooves 101, and the gas enters the lower herringbone grooves 10 after passing through the upper grooves, thereby increasing the airflow resistance and the pressure difference effect.

[0020] Each of the herringbone grooves 101 is evenly arranged on the surface of the radial sealing plate 1, maintaining an equal interval and an equidistant parallel relationship relative to other grooves, and extending from the edge to the center of the radial sealing plate 1; each of the herringbone grooves 101 is composed of two symmetrical herringbone structures, which are divided into an upper herringbone groove 101 and a lower herringbone groove 101, ensuring that the flow path of the gas in the groove is balanced, and the symmetrical structure can be consistent in the upper herringbone groove 101 and the lower herringbone groove 101, forming a uniform pressure gradient; the opening direction of each herringbone groove 101 is consistent with the rotation direction of the rotor 4, ensuring that the high-pressure gas can smoothly enter the upper air inlet 201 and the lower air inlet 202.

[0021] The herringbone groove 101 spacing area is located in the spacing part between the herringbone grooves 101, forming a plurality of parallel or staggered herringbone grooves 101, each groove divides the contact surface into several parts; the herringbone groove 101 spacing area divides the contact area between the radial sealing plate 1 and the rotor 4 into a plurality of smaller areas, so that the friction is reduced and the sealing effect is increased by the pressure change of the gas in the groove; the herringbone groove 101 spacing area is an uncut solid part, located between the grooves of the five parallel herringbone grooves 101 on the radial sealing plate 1, and can actually contact the contact area part of the rotor 4; the herringbone groove 101 spacing area is also a tiny contact area formed near the edge of the groove, and the contact area part is at the high pressure area near the edge of the slot; the contact area of ​​the spacing area is located at the radial sealing plate 1 where there are five parallel herringbone grooves 101, and the spacing area between the grooves is the part that actually contacts the rotor 4; the specific position of the contact area is as follows:

[0022] Contact area 1: a spacing area between the first herringbone groove 101 and the second herringbone groove 101;

[0023] Contact area 2: a spacing area between the second herringbone groove 101 and the third herringbone groove 101;

[0024] Contact area 3: an interval area between the third herringbone groove 101 and the fourth herringbone groove 101;

[0025] Contact area 4: a spacing area between the fourth herringbone groove 101 and the fifth herringbone groove 101;

[0026] Contact area 5: the spacing area between the fifth herringbone groove 101 and the edge of the radial sealing sheet 1 .

[0027] The surface micro-texture of the radial sealing plate of the cycloid rotor engine is characterized in that the airflow path of the upper herringbone groove 101 is as follows:

[0028] S1. Airflow inlet: airflow enters the upper air inlet 201 and the lower air inlet 202 of the upper herringbone groove 101;

[0029] S2. Airflow path 1: The airflow flows along the upper herringbone groove 101 and the two arms of the lower herringbone groove 101;

[0030] S3. Air flow path 2: The gas flows into the channel, and the flow pattern changes dramatically in the channel, forming negative pressure adsorption until the end of the channel;

[0031] S4. Airflow confluence point: airflow is discharged from the upper air outlet 203 at the end of the herringbone groove 101;

[0032] The specific airflow path of the lower herringbone groove 101 is as follows:

[0033] S1. Airflow inlet: airflow enters from the lower air inlet 202 of the lower herringbone groove 101;

[0034] S2. Airflow path 3: The airflow flows along the lower air inlet 202 of the lower opening of the herringbone groove 101 and along the two arms of the new herringbone groove 101;

[0035] S3. Airflow path 4: The airflow flows in the channel until it is discharged from the lower air outlet 204 at the end of the herringbone groove 101 .

[0036] Specifically, the sealing weir area 102 forms a plurality of continuous groove-free areas, which are located in the middle part between two adjacent herringbone grooves 101, are evenly distributed along the axial direction of the radial sealing plate 1, and are directly connected to the adjacent herringbone grooves 101 to form a smooth and continuous surface; the sealing weir area 102 divides the herringbone grooves 101 into several pairs to form a plurality of independent sealing units, each of which can generate an effective pressure difference and negative pressure effect, thereby being able to transfer the pressure difference and negative pressure effect generated by the herringbone grooves 101 to the adjacent herringbone grooves 101 and the sealing dam area 103; the sealing dam area 103 forms a plurality of continuous groove-free areas, which are located at the outer edge of the herringbone grooves 101, and are distributed along the rotation direction of the rotor 4 to form a continuous, complete and smooth sealing interface; the sealing dam area 103 is formed through its The groove-free area forms a continuous and complementary structure with the herringbone groove 101, without any physical partition, and directly forms a continuous seamless connection, so that the airflow can smoothly transition from the herringbone groove 101 to the sealing dam area 103, preventing the gas from escaping from the outside of the radial sealing piece 1; the sealing dam area 103 transfers the pressure difference and negative pressure effect generated by the herringbone groove 101 and the sealing weir area 102 to the outer edge area of ​​the radial sealing piece 1; the sealing weir area 102 and the sealing dam area 103 cooperate with each other during the airflow movement, so that the various parts of the radial sealing piece 1 form a multi-layer protection, and the gas cannot easily find a leakage path; the sealing weir area 102 provides primary blocking, and the sealing dam area 103 provides secondary protection. The sealing weir area 102 and the sealing dam area 103 together form a combined sealing mechanism on the radial sealing piece 1.

[0037] Specifically, the double-layer herringbone groove 101, the sealing weir area 102 and the sealing dam area 103 cooperate to form a multi-layer sealing system, with a total of four sealing layers, as follows:

[0038] (1) The first sealing layer (preliminary sealing): the upper herringbone groove 101;

[0039] (2) Second sealing layer (middle sealing): sealing weir area 102;

[0040] (3) The third sealing layer (deep sealing): the lower herringbone groove 101;

[0041] (4) The fourth sealing layer (edge ​​sealing): sealing the dam area 103.

[0042] The preliminary sealing is achieved by separating the sealing weir area 102 between each upper herringbone groove 101, so that the gas flow cannot leak between the grooves; wherein the opening of the upper herringbone groove 101 faces the high-pressure gas side and can directly receive the high-pressure gas;

[0043] The middle seal is formed by the sealing weir area 102, which is located between the upper herringbone grooves 101 and is a continuous surface without grooves. The groove-free area formed by the sealing weir area 102 prevents gas from passing between grooves, so that even if a small amount of gas leaks in the upper groove, it cannot enter the adjacent groove through the sealing weir area 102, thereby achieving airtightness between the grooves.

[0044] The deep seal is achieved by the lower herringbone groove 101 being located below or at an interlaced position of the upper groove, and the high-pressure gas passes through the upper groove and the lower groove at the same time, thereby increasing the air flow resistance and the pressure difference effect, and forming a stronger negative pressure adsorption force;

[0045] The edge seal is that the sealing dam area 103 is located at the outer edge of the double-layer herringbone groove 101 to form a continuous surface without a groove; the grooveless area formed by the sealing dam area 103 serves as the last line of defense, providing an additional barrier layer to prevent gas from escaping from the outer edge of the radial sealing sheet 1; even if gas leaks out in the first three layers of sealing, the sealing dam area 103 can prevent the final leakage of the gas.

[0046] Specifically, the symmetry centerline 104 is the central axis that runs through the radial sealing plate 1, and is located in the middle position of the radial sealing plate 1, forming a symmetrical layout; the symmetry centerline 104 serves as the alignment point of the herringbone groove 101, ensuring that the opening direction of all grooves is consistent with the rotation direction of the rotor 4; the opening 201 is the entrance of the high-pressure gas into the herringbone groove 101, the upper air inlet 201 and the lower air inlet 202, which can guide the airflow into the herringbone groove 101 and flow along the airflow path to generate a pressure difference and a negative pressure adsorption effect.

[0047] The depth of the herringbone grooves 101 is 1-5; and there are 2-10 pairs of the herringbone grooves 101.

[0048] Furthermore, the edge line type of the herringbone groove 101 structure is one or more of a straight line, an arc line, a spiral line, and a sawtooth line.

[0049] Preferably, the material of the radial sealing sheet is silicon carbide material or cemented carbide (Ni-Cr-Co alloy, Co-Cr-W alloy, Ti-Al-V alloy and Al-Cu-Mg-Si alloy).

[0050] Preferably, the radial sealing sheet structure can be processed by laser.

[0051] The purpose of the present invention and the solution to its technical problems can be further achieved by adopting the following technical measures.

[0052] See also Figure 1-3As shown, in a sealing structure in which a herringbone groove 101 is opened on the curved surface of a radial sealing plate of an engine, gas enters through the groove of the herringbone groove and an opening 201 on one side of the radial sealing plate, and reaches a maximum pressure value at a corner 202 of the herringbone groove; a plurality of herringbone grooves 101 are evenly distributed along the axial direction on the curved surface of the radial sealing plate, the non-grooved area between two axially adjacent pairs of herringbone grooves 101 is a sealing weir area 102, and the non-grooved area outside the herringbone groove 101 is a sealing dam area 103.

[0053] In the present invention, the herringbone groove 101 is an axisymmetric pattern, and the herringbone groove 101 on the radial sealing sheet is symmetrical along the symmetry center line 104 of the radial sealing sheet.

[0054] In the present invention, the gas enters the groove from the notch 201, and a negative pressure is generated due to the difference in pressure at each point in the radial sealing plate curved surface herringbone groove 101, so that the radial sealing plate 1 and the rotor 4 are adsorbed together.

[0055] The working principle of the micro-texture on the surface of the radial sealing sheet of the cycloid rotor engine described in the present invention is as follows:

[0056] The working principle of the present invention is based on the double-layer herringbone groove 101 design and micro-textured surface, and the sealing effect is optimized by controlling the groove depth, number and edge line type, and selecting high-hardness materials. The pressure difference and negative pressure generated when the gas flows in the groove form an adsorption force, so that the radial sealing plate and the rotor fit tightly, thereby achieving effective sealing. The application of laser processing technology ensures the precise manufacturing of the micro-textured structure and improves the performance and service life of the radial sealing plate. Furthermore, the present invention provides an efficient, stable, vibration-resistant, and low-wear radial sealing solution by designing a double-layer herringbone groove 101 structure on the surface of the radial sealing plate, utilizing the gas lubrication principle and the pressure change of the groove structure.

[0057] The herringbone groove 101 structural design on the surface of the radial sealing plate is the core of the present invention. The present invention designs a double-layer herringbone groove 101 on the surface of the radial sealing plate in contact with the rotor. The double-layer herringbone groove 101 refers to a groove type of a specific shape opened on the radial sealing plate, and its main function is to generate pressure difference and negative pressure through the flow of gas in the groove, thereby achieving a sealing effect. Specifically, the groove depth of each pair of herringbone grooves 101 is between 1-5, and the number is 2-10 pairs. This design can accurately control the gas flow in the groove and optimize the generation of pressure difference.

[0058] Specifically, the edge line type of the herringbone groove 101 can be a combination of one or more of a straight line, an arc line, a spiral line or a sawtooth line; these edge line types of different shapes can further optimize the gas flow and pressure distribution and improve the sealing effect. Specifically, the design of the herringbone groove 101 reduces the direct contact area between the radial sealing sheet and the rotor; thereby reducing the contact area can reduce friction and wear, thereby extending the service life of the radial sealing sheet; at the same time, this design can also reduce the volume of the radial sealing sheet, which is a lightweight design.

[0059] Furthermore, the herringbone groove 101-type structure helps to enhance the anti-vibration performance of the radial sealing plate. The groove structure can absorb and offset part of the vibration energy during operation, thereby reducing the wear and damage of the radial sealing plate in a high vibration environment.

[0060] Furthermore, a groove-free sealing weir area 102 is provided between each pair of herringbone grooves 101, which can help stabilize the airflow and prevent gas leakage. At the same time, a sealing dam area 103 is also provided along the rotation direction of the rotor to further enhance the sealing effect.

[0061] The present invention utilizes the principle of gas lubrication. Gas lubrication is to form a gas film between the radial sealing plate and the rotor contact surface, and the lubrication and sealing effects are achieved through the pressure of the gas film. Due to the use of the gas lubrication and sealing principles, the sealing oil system required in the traditional sealing system is omitted. This not only simplifies the system design, reduces maintenance and operating costs, but also avoids the possibility of the sealing fluid being contaminated by oil.

[0062] When the slotted gas seal is working, a stable adsorption force will be generated on the two sealing end faces. The strength of this adsorption force is sufficient to make the two sealing end faces completely adsorbed together to ensure the sealing effect. This adsorption force can significantly reduce leakage and improve the stability and reliability of the seal. Specifically, when the rotor rotates, the gas will produce pressure changes when passing through the herringbone groove 101. Specifically, the geometric structure of the herringbone groove 101 will cause the gas to form local high-pressure areas and low-pressure areas in the groove, and these pressure changes will generate adsorption force between the radial sealing plate and the rotor. On the high-pressure inlet side, the opening design of the herringbone groove 101 allows the gas to enter the groove. Due to the pressure difference at different positions in the groove, a pressure difference and negative pressure will be generated, thereby forming an adsorption force between the radial sealing plate and the rotor. This adsorption force makes the radial sealing plate and the rotor fit tightly to achieve the purpose of sealing.

[0063] Furthermore, the preferred radial sealing sheet material of the present invention is silicon carbide or cemented carbide. These materials have high hardness and wear resistance, and can maintain structural stability and sealing effect in high pressure and high temperature environments. The micro-texture structure of the radial sealing sheet can be achieved by laser processing. Laser processing has the advantages of high precision and controllability, and can accurately carve the required micro-texture on the radial sealing sheet.

[0064] The beneficial effects of the surface micro-texture of the radial sealing sheet of the cycloid rotor engine described in the present invention are as follows:

[0065] First, the surface micro-texture of the radial sealing plate of a cycloidal rotor engine described in the present invention, compared with the existing ungrooved radial sealing plate sealing technology, the present invention grooves the radial sealing plate to reduce the volume of the radial sealing plate, reduce the contact area between the radial sealing plate and the rotor, reduce the friction loss between the radial sealing plate and the rotor, and extend the service life from the original 200 hours to 300-500 hours, thereby extending the replacement cycle of the radial sealing plate, thereby achieving the purpose of reducing use costs, reducing leakage, and making the seal more stable. In addition, grooves on the radial sealing plate can utilize the dynamic pressure effect generated when the gas flows in the groove to obtain an adsorption force between the radial sealing plate and the rotor, so that the radial sealing plate and the rotor can fit tightly together, achieve stable sealing performance, and reduce gas leakage.

[0066] Second, the surface micro-texture of the radial sealing piece of the cycloid rotor engine described in the present invention provides a double-layer herringbone groove 101-type radial sealing piece to solve the problems of unstable sealing, easy leakage, severe wear and tear of existing radial sealing pieces, such as Figure 1 As shown, the groove is formed on the arc surface where the radial seal contacts the rotor, and the radial seal is fixed in the radial seal fixing groove of the engine housing. The present invention is based on the gas lubrication theory, utilizes the superimposed combined structural features, and designs the radial seal contact surface groove structure according to the influence of the groove shape, groove geometry parameters and working condition parameters on the sealing performance, which can produce a stronger change in fluid pressure, significantly improve the sealing effect, thereby improving the operating stability of the seal and extending the service life.

[0067] Third, the micro-texture on the surface of the radial sealing plate of a cycloidal rotor engine described in the present invention can obtain an adsorption force between a rotor and the radial sealing plate through the pressure change generated by the rotation of the herringbone groove 101, which greatly improves the sealing effect, reduces the volume of the radial sealing plate, and reduces the production cost. In addition, the herringbone groove 101 (micro-texture) on the surface of the radial sealing plate has better anti-rotor vibration performance, and the grooving on the surface of the radial sealing plate reduces the contact area between the radial sealing plate and the rotor, which has a longer service life and extends the replacement cycle of the radial seal, thereby achieving the purpose of reducing use costs, reducing leakage, and making the seal more stable.

[0068] Fourth, the radial sealing plate of a cycloidal rotor engine described in the present invention has a micro-texture on its surface, and the herringbone groove 101 type gas seal on the surface of the radial sealing plate can generate pressure changes by shearing the fluid between the radial sealing plate and the rotor during rotation through two relatively rotating sealing components, so that the radial sealing plate and the rotor are adsorbed to each other under the influence of pressure, and finally the sealing end face is in a contact sealing state for a long time. The slotted gas seal can save the sealing oil system and eliminate some related common problems. It has low leakage, low energy consumption, low maintenance, and the sealed fluid is not contaminated by oil. The slotted gas seal is different from other seals in that the slotted gas seal will generate a stable adsorption force on the two sealing end faces when working. The adsorption force has a strong strength that allows the two sealing end faces to be completely adsorbed together to ensure the sealing effect.

[0069] Fifth, the present invention can achieve considerable technical advancement and practicality, and has a wide range of utilization value in the engine sealing element industry, and has at least the following advantages: First, the present invention forms a pressure difference and negative pressure on the high-pressure intake side by opening a double-layer herringbone groove 101 on the surface of the radial sealing plate, thereby enhancing the adsorption force between the radial sealing plate and the rotor. In this way, the radial sealing plate can pulsate and jump on the cylinder surface (vibration phenomenon) to maintain the stability of the cycloid rotor engine. Second, the double-layer herringbone groove 101 structure described in the present invention can form a negative pressure on the high-pressure intake side, adsorbing the radial sealing plate and the rotor more tightly together, thereby improving the sealing performance and reducing air leakage. Third, the sealing weir area 102 and the sealing dam area 103 structure on the radial sealing plate described in the present invention also act as a sealing barrier, further reducing gas leakage. BRIEF DESCRIPTION OF THE DRAWINGS

[0070] Figure 1 is a top view of the grooved curved surface of the herringbone groove 101 type seal of the present invention;

[0071] Figure 2 It is a wireframe diagram of the radial sealing sheet of the herringbone groove 101 of the present invention;

[0072] Figure 3It is a model diagram of the radial sealing sheet of the herringbone groove 101 of the present invention;

[0073] Figure 4 This is a layered view of the surface micro-texture of a radial sealing plate of a cycloidal rotor engine according to the present invention;

[0074] Figure 5 It is a detailed model diagram of the layered view of the surface micro-texture of the radial sealing plate of a cycloidal rotor engine described in the present invention;

[0075] Figure 6 It is a detailed wireframe diagram of a layered view of the surface micro-texture of a radial seal plate of a cycloidal rotor engine according to the present invention;

[0076] Figure 7 It is a schematic diagram of the airflow path of the micro-textured surface of the radial sealing plate of a cycloidal rotor engine described in the present invention.

[0077]

Numbers in the figure

[0078] Radial sealing sheet 1; rotor 4;

[0079] Herringbone groove 101; sealing weir area 102; sealing dam area 103; symmetry center line 104;

[0080] Upper air inlet 201; lower air inlet 202; upper air outlet 203; lower air outlet 204;

[0081] The mounting surface 301 of the rotor engine stator; the bottom spring mounting point 302. DETAILED DESCRIPTION

[0082] In order to further explain the technical means and effects adopted by the present invention to achieve the predetermined purpose of the invention, the specific implementation method, structure, characteristics and actual problems that can be solved of the radial sealing surface micro-texture of a cycloidal rotor engine according to the present invention are described in detail below in combination with the accompanying drawings and preferred embodiments.

[0083] See also Figure 1-3 As shown, the present invention describes a radial sealing plate surface micro-texture of a cycloidal rotor engine, and the purpose is to open a sealing structure of a herringbone groove 101 on the radial sealing plate curved surface. Gas enters from the groove of the herringbone groove 101 and the upper air inlet 201 and the lower air inlet 202 of the radial sealing plate, and reaches the maximum pressure in the groove of the herringbone groove 101. Correspondingly, the gas is discharged from the upper air outlet 203 and the lower air outlet 204, so as to achieve exhaust from the high-pressure area on the right to the low-pressure area on the left; a plurality of herringbone grooves 101 are evenly distributed along the axial direction on the radial sealing plate curved surface, the non-grooved area between two axially adjacent pairs of herringbone grooves 101 is the sealing weir area 102, and the ungrooved area outside the herringbone groove 101 is the sealing dam area 103.

[0084] In the present invention, the herringbone groove 101 is an axisymmetric pattern, and the herringbone groove 101 on the radial sealing sheet is symmetrical along the symmetry center line 104 of the radial sealing sheet.

[0085] In the present invention, the gas enters the groove from the upper gas inlet 201 and the lower gas inlet 202, and a negative pressure is generated by the difference in pressure at each point in the radial sealing plate curved surface herringbone groove 101, so that the radial sealing plate 1 and the rotor are adsorbed together.

[0086] like Figure 1 As shown, the top view of the grooved curved surface of the herringbone groove 101 type seal of the present invention shows the structure of the radial sealing plate 1 in the cycloidal rotor engine, including the herringbone groove 101, the sealing weir area 102, the sealing dam area 103 and the symmetry center line 104.

[0087] The herringbone groove 101 is Figure 1 The micro-texture on the surface of the radial sealing piece 1 is shown, which is mainly composed of a plurality of V-shaped herringbone grooves; these herringbone grooves are used to control the flow and distribution of gas, thereby achieving effective sealing; the sealing weir area 102 is the area between the herringbone grooves 101, which are not grooved and are used to increase the sealing effect and prevent gas leakage; the sealing dam area 103 is arranged in the ungrooved area outside the herringbone groove 101, and its function is to further enhance the sealing of the radial sealing piece; the symmetry center line 104 represents the symmetry center of the radial sealing piece 1 or the geometric center of the structure, which is used for reference or alignment.

[0088] The herringbone groove 101 refers to a V-shaped groove formed on the surface of the radial sealing plate 1; these grooves are arranged along the axial direction of the radial sealing plate, and are shaped like a herringbone (V-shaped); the main function of the herringbone groove 101 is to control the pressure and flow direction of the gas by changing the gas flow path. When the cycloidal rotor engine is running, the gas enters from the air inlet and flows through these herringbone grooves 101; and the V-shape of the groove causes the gas to be divided and converged during the flow process, forming a local pressure gradient. This pressure difference enhances the sealing effect to a certain extent, preventing the gas from leaking directly from the upper air inlet 201 and the lower air inlet 202 to the upper air outlet 203 and the lower air outlet 204, thereby improving the overall sealing performance of the radial sealing plate.

[0089] The sealing weir area 102 is a non-grooved area between the herringbone grooves 101; these areas do not have any grooves, but remain smooth and flat. The sealing weir area 102 serves as a blocking area for gas flow to prevent gas from flowing between different grooves; and these non-grooved areas block the flow path of gas between two adjacent grooves by increasing the effective contact area of ​​the radial sealing sheet, further enhancing the sealing performance; and thus effectively preventing gas from flowing along the radial sealing sheet surface in an unintended path, thereby reducing leakage.

[0090] The sealing dam area 103 is an ungrooved area outside the herringbone groove 101. The sealing dam area 103 is similar to the sealing weir area 102, and its function is to serve as an additional barrier to prevent gas from leaking from the edge of the radial sealing piece. In actual operation, the sealing dam area 103 can form a close contact with the cycloid rotor engine housing or stator, thereby preventing gas from escaping through the outer edge of the radial sealing piece, ensuring the integrity of the seal;

[0091] The symmetry centerline 104 represents the symmetry center or geometric center of the radial seal. The symmetry centerline 104 may be used as a reference line during the design and manufacturing process to ensure the symmetry and uniform distribution of the components such as the herringbone groove 101, the sealing weir area 102, and the sealing dam area 103, thereby ensuring that the radial seal is uniformly stressed and wears uniformly during operation, thereby ensuring the stable operation of the cycloidal rotor engine. Figure 1 As shown, in the top view of the grooved curved surface of the herringbone groove seal, the angle of the groove points to the rotation direction of the rotor, and the gas enters the groove through the upper gas inlet 201 and the lower gas inlet 202, so that the pressure at each position in the groove is different, generating a negative pressure, thereby generating an adsorption force between the radial sealing sheet and the rotor, making the radial sealing sheet and the rotor in close contact, reducing gas leakage. Due to the surface grooves, the contact area between the radial sealing sheet and the rotor is reduced, and the friction loss between the radial sealing sheet and the rotor is reduced.

[0092] From the perspective of gas flow, when the rotor rotates, the gas enters the slot through the upper gas inlet 201 and the lower gas inlet 202, and then flows along the V-shaped path of the herringbone slot 101. This complex flow path increases the flow resistance and forms different pressure areas.

[0093] In terms of pressure change, due to the different geometric shapes of the herringbone groove 101 and the groove, the gas forms different pressure areas during the flow process, forming a pressure gradient; the pressure gradient formed by the gas in the groove produces a negative pressure effect (located in the sealing dam area 103), which generates an adsorption force between the radial sealing sheet and the rotor.

[0094] From the perspective of negative pressure effect, the negative pressure effect makes the radial sealing plate 1 (located in the sealing dam area 103) in close contact with the rotor, reducing gas leakage; thus, the negative pressure effect not only improves the tightness between the radial sealing plate 1 and the rotor 4, but also reduces the contact area and friction loss, thereby extending the service life of the radial sealing plate 1.

[0095] In terms of friction and wear, due to the surface groove design, the contact area between the radial sealing plate 1 and the rotor 4 is reduced, thereby reducing friction loss; the reduced friction and wear extend the service life of the radial sealing plate 1 and improve the operating efficiency.

[0096] like Figure 2-3 As shown, the wireframe diagram of the radial sealing plate 1 with a herringbone groove 101, wherein the groove depth is 1-5. In order to see the groove depth more intuitively, the groove depth is magnified. Specifically, the herringbone groove 101 is presented as a plurality of herringbone structures arranged in parallel with each other. The upper air inlet 201 and the lower air inlet 202 enter in the direction of rotation toward the rotor 4 to ensure that the gas can smoothly enter the groove; specifically, a plurality of parallel herringbone grooves 101 are evenly distributed on the surface of the radial sealing plate 1 to form a continuous flow path and pressure change area. Specifically, although the actual groove depth is 1-5 microns, the shape and arrangement of the herringbone groove 101 can be more clearly seen by enlarging the display in the model. Specifically, through the design of the upper air inlet 201 and the lower air inlet 202 and the channel, the gas flows along the complex path of the herringbone groove 101, forming different pressure gradients and negative pressure effects.

[0097] like Figure 2 As shown, in the cycloid rotor engine, the upper air inlet 201, the lower air inlet 202, the upper air outlet 203 and the lower air outlet 204 are the key nodes for air inlet and air outlet, respectively. The gas flows inside the sealing plate through the herringbone groove 101 structure, and effective sealing is achieved by using the pressure difference and friction effect. The upper air inlet 201, the lower air inlet 202, the upper air outlet 203 and the lower air outlet 204 work independently to ensure the efficient operation of the cycloid rotor engine. The entire sealing system realizes the control and sealing of the gas through complex fluid dynamics design, minimizes the risk of leakage, and improves the efficiency and stability of the cycloid rotor engine.

[0098] Specifically, the upper gas inlet 201 and the upper gas outlet 203 constitute the gas pressure and flow path, which involves gas pressure control, flow path management, and optimized design of the sealing structure.

[0099] From the control of gas pressure and flow path, the gas flow process goes through the following:

[0100] S1. Introduction of high-pressure gas (upper air inlet 201): When the cycloidal rotor engine is running, the gas enters the upper part of the radial sealing plate through the upper air inlet 201. At this time, the pressure of the gas is relatively high. Due to the herringbone groove 101 on the radial sealing plate, the gas will first undergo an adjustment of the pressure distribution after entering. The structure of the herringbone groove 101 allows the gas to be guided into multiple branch paths, which not only extend the distance of gas flow, but also increase its contact surface area. Inside the groove, due to the shape and arrangement of the herringbone groove 101, the gas will be subject to a certain friction force, and as the gas flows in the groove, part of the pressure will be released and consumed. At the same time, the flow path of the gas will become more tortuous, which can effectively reduce the flow velocity of the gas, and then reduce its kinetic energy, thereby inhibiting gas leakage.

[0101] S2. Formation of low-pressure zone (upper gas outlet 203): When the gas is guided by the herringbone groove 101, it gradually reaches the other end of the radial sealing plate, that is, near the upper gas outlet 203. Due to the design of the groove, the pressure of the gas in this area is significantly reduced compared to when it enters. The formation of a low-pressure zone helps to guide the gas to flow naturally to the upper gas outlet 203 and avoid the backflow of gas in the system. In addition, the gradually contracting structure of the herringbone groove 101 allows the pressure of the gas to gradually decrease from the upper gas inlet 201 to the upper gas outlet 203. This pressure gradient ensures that the gas can flow along the designed path and be discharged from the system smoothly. In terms of enhancing the sealing effect, in the process of the gas flowing through the herringbone groove 101, the friction generated between the gas and the groove wall not only slows down the speed of the gas, but also further increases the sealing effect of the radial sealing plate; this friction converts part of the kinetic energy of the gas into heat energy, thereby reducing its fluidity and reducing possible leakage.

[0102] In terms of enhancing the sealing effect, when the gas flows through the herringbone groove 101, the friction generated between the gas and the groove wall not only slows down the speed of the gas, but also further increases the sealing effect of the radial sealing plate; this friction converts part of the kinetic energy of the gas into heat energy, thereby reducing its fluidity and reducing possible leakage. In terms of the pressure difference in the groove, inside the herringbone groove 101, due to the curve shape and the narrowing of the groove, the gas will form local high-pressure and low-pressure areas during the flow process; the high-pressure area is located near the upper air inlet 201, and as the gas flows along the groove, the pressure gradually decreases to form a low-pressure area. This pressure difference prevents the reverse flow and leakage of the gas to a large extent.

[0103] During the operation of the cycloid rotor engine, the gas can flow along a predetermined path in the sealing plate, and achieve a good sealing effect through effective pressure management and friction, thereby preventing gas leakage and improving the working efficiency of the cycloid rotor engine. The gas at the upper air inlet 201 enters the radial sealing plate under high pressure and flows along the herringbone groove 101; the structural design of the groove effectively controls the flow path of the gas through friction and pressure gradient, so that the gas gradually slows down and flows smoothly to the low-pressure area. After being guided by the groove, the gas at the upper air outlet 203 is discharged from the system at a lower pressure and speed, thereby completing the flow path of the gas.

[0104] Specifically, the lower gas inlet 202 and the lower gas outlet 204 constitute a gas pressure and flow path, which involves gas pressure control, flow path management, and optimized design of a sealing structure.

[0105] From the perspective of gas path control and pressure management, the gas flow process goes through the following:

[0106] S1. Introduction of high-pressure gas (lower air inlet 202): When the gas enters the lower portion of the sealing plate from the lower air inlet 202, it is in a higher pressure state; similar to the upper layer, the herringbone groove 101 allows the incoming gas to be guided through multiple tortuous paths, which increase the length and surface area of ​​the gas flow, thereby helping to control the flow rate and pressure of the gas. The design of the lower herringbone groove 101 is similar to that of the upper layer. The structure of the groove causes friction when the gas flows through the radial sealing plate, and part of the pressure is consumed. This friction not only controls the speed of the gas flow, but also reduces the kinetic energy of the gas to a certain extent, preventing it from leaking from the side edges of the groove.

[0107] S2. Formation of low-pressure zone (lower gas outlet 204): When the gas flows through the herringbone groove 101 and gradually reaches the lower gas outlet 204, the pressure of the gas gradually decreases, forming a low-pressure zone; this low-pressure zone helps the gas to be discharged from the system smoothly from the lower layer and prevents the gas from flowing back to the gas inlet. The tapered design of the herringbone groove 101 from the lower gas inlet 202 to the lower gas outlet 204 forms a pressure gradient. This pressure gradient forces the gas to flow along a predetermined path and gradually loses kinetic energy when flowing through each groove, ensuring that the gas can be discharged smoothly without backflow.

[0108] In terms of enhancing the sealing effect, when the gas flows through the lower herringbone groove 101, the friction between the gas and the groove wall will further slow down the speed of the gas and increase the sealing effect. The friction not only helps to reduce the flow speed of the gas, but also increases the radial sealing plate's ability to control the gas, reducing the potential risk of leakage. In terms of utilizing the pressure difference, the gas path design of the lower layer also utilizes the pressure difference inside the herringbone groove 101. The gas is in the high-pressure area when it enters, and as the gas flows along the herringbone groove 101, it gradually enters the low-pressure area. This pressure difference not only drives the gas to flow along the designed path, but also effectively prevents the gas from leaking from the inside of the groove.

[0109] Similarly, the design of the lower layer is similar to that of the upper layer, and the flow of gas is controlled by using the friction and pressure difference generated by the herringbone groove 101 structure. The high-pressure gas near the lower layer air inlet 202 is gradually decompressed through the groove and finally discharged from the lower layer air outlet 204, ensuring that the flow path of the gas inside the radial sealing sheet is controlled, and through effective sealing and flow management, the risk of leakage is minimized to maintain the efficient operation of the engine.

[0110] The gas at the lower air inlet 202 enters the radial sealing sheet under high pressure and flows along the path of the herringbone groove 101. The structure of the herringbone groove 101 slows down the flow speed of the gas and controls its flow path through friction and pressure gradient. The gas at the lower air outlet 204 is discharged from the system at a lower pressure and speed under the guidance of the groove, completing the flow path of the gas in the lower layer.

[0111] like Figure 3 , showing the key structure of the cycloid rotor engine stator, especially its mounting surface and spring mounting position. The mounting surface 301 of the rotor engine stator is used to support and fix the stator to ensure that it fits tightly with the rotor, while the bottom spring mounting position 302 is the fixing position of the spring, which is used to provide continuous elastic force during operation to maintain the sealing effect between the radial sealing sheet and the stator.

[0112] The mounting surface 301 of the rotor engine stator refers to a specially designed plane or multiple planes on the rotor engine stator, which is used to contact and fix with other key components of the cycloidal rotor engine (such as radial sealing plates, housings, and supporting structures). The mounting surface 301 of the rotor engine stator is precisely machined to ensure that the mounting surface 301 of the rotor engine stator can provide a flat and stable contact surface and seamlessly cooperate with other components.

[0113] The mounting surface 301 of the rotor engine stator is the main support point of the stator. Through the mounting surface 301 of the cycloidal rotor engine stator, the stator can be firmly mounted on the housing or other fixed parts of the cycloidal rotor engine, ensuring that the stator will not move or loosen at any position during the operation of the cycloidal rotor engine. The contact between the mounting surface 301 of the rotor engine stator and other parts is that the stator contacts with radial sealing sheets or housings and other parts through the mounting surface 301 of the rotor engine stator, keeping the stator from deviating from its working position. Since the matching accuracy between the rotor and the stator in the cycloidal rotor engine is crucial, the mounting surface 301 of the rotor engine stator must ensure that the stator maintains its ideal position during the entire operation.

[0114] From the perspective of sealing effect, in a cycloidal rotor engine, the sealing effect directly affects the working efficiency and performance of the cycloidal rotor engine. The accuracy of the mounting surface 301 of the rotor engine stator ensures strict clearance control between the stator and the radial sealing sheet, thereby achieving good air tightness. From the perspective of cooperation with the radial sealing sheet, the radial sealing sheet needs to fit tightly on the surface of the stator, and the mounting surface 301 of the rotor engine stator serves as a positioning reference to ensure this sealing effect; any slight error will cause gas leakage, thereby reducing the efficiency of the cycloidal rotor engine. From the perspective of affecting the operating efficiency of the system, the accuracy of the mounting surface 301 of the rotor engine stator directly affects the overall operating efficiency of the cycloidal rotor engine. If the mounting surface 301 of the rotor engine stator is not flat or does not meet the design requirements, the position of the stator will be offset, resulting in poor sealing, increased friction between the rotor and the stator, and even cycloidal rotor engine failure. In terms of vibration and wear control, the mounting surface 301 of the rotor engine stator can also reduce vibration and wear caused by misalignment or looseness, thereby extending the service life of the cycloid rotor engine; furthermore, the stability of the mounting surface 301 of the rotor engine stator helps to maintain a constant gap between the rotor and the stator, thereby reducing excessive wear or mechanical stress concentration.

[0115] In a specific installation scenario, the functions of the installation surface 301 of the rotor engine stator are as follows:

[0116] During the assembly process of the cycloid rotor engine, the mounting surface 301 of the rotor engine stator serves as a key positioning reference to ensure that the stator can be accurately installed in the designed position. This process requires extremely high precision, because any slight deviation will affect the final sealing effect and the balance of the rotor operation.

[0117] When the cycloid rotor engine is running, the mounting surface 301 of the rotor engine stator must maintain its structural integrity and accuracy. The stator is rigidly connected to other components through the mounting surface 301 of the rotor engine stator to withstand various forces generated by the rotor during high-speed rotation, such as centrifugal force and vibration.

[0118] During maintenance or repair of a cycloidal rotor engine, the mounting surface 301 of the rotor engine stator is also a key area for inspection and calibration; the flatness and wear of the mounting surface 301 of the rotor engine stator can be checked to ensure that the mounting surface 301 of the rotor engine stator can still provide the necessary accuracy and support.

[0119] The bottom spring mounting position 302 is a position on the radial sealing sheet or stator structure specifically used for fixing the spring. The bottom spring mounting position 302 usually has a certain groove or fixing structure so that the spring can be accurately and stably placed at the designed position.

[0120] In order to provide continuous elastic force, a spring is installed at the bottom spring installation 302. The radial sealing sheet is pressed against the surface of the stator by the elastic force of the spring. Since the elastic force is continuous, it is ensured that the radial sealing sheet can always maintain close contact with the stator under different working conditions (such as temperature changes and pressure fluctuations). Since the radial sealing sheet needs to maintain close contact between the high-speed rotating rotor and the stationary stator, the elastic force of the spring can compensate for the gap changes caused by factors such as thermal expansion and contraction of the material and wear, thereby preventing gas leakage. In order to compensate for wear and temperature changes, the radial sealing sheet will wear during the long-term operation of the cycloidal rotor engine, resulting in an increase in the gap between it and the stator.

[0121] The spring is installed at the bottom spring installation part 302, and the radial sealing sheet is pressed against the surface of the stator by the elastic force of the spring. This elastic force is continuous, ensuring that the radial sealing sheet can always maintain close contact with the stator under different working conditions (such as temperature changes, pressure fluctuations). Since the radial sealing sheet needs to maintain close contact between the high-speed rotating rotor and the stationary stator, the elastic force of the spring can compensate for the gap changes caused by factors such as thermal expansion and contraction of the material and wear, thereby preventing gas leakage.

[0122] The spring is mounted at the bottom spring mounting point 302. The spring is firmly positioned in place through the fixing structure of the mounting point. This fixation prevents the spring from shifting or falling off during operation, ensuring the stable function of the spring. The bottom spring mounting point 302 is not only used to fix the spring, but also takes into account the needs of maintenance and replacement. When the spring needs to be repaired or replaced, this mounting point enables engineers to easily remove the old spring and install a new spring to maintain the efficient operation of the engine.

[0123] like Figure 4 , Figure 5 , Figure 6 The figure shows the relative position and structure of the radial sealing sheet 1 and the rotor 4 in the cycloid rotor engine. The radial sealing sheet tightly surrounds the rotor, and its shape is precisely matched with the rotor surface to prevent gas leakage and ensure the efficient operation of the cycloid rotor engine.

[0124] The radial sealing sheet 1 is a key component for forming a seal between the rotor and the stator; the radial sealing sheet 1 surrounds the rotor and is located in the contact area between the rotor 4 and the stator to prevent gas leakage through close contact. Figure 4 As can be seen in the figure, the radial sealing sheet presents a complex closed curve shape, which is designed to match the shape of the rotor 4 and ensure a good sealing effect during the entire operation process. The radial sealing sheet 1 forms an airtight barrier by fitting to the outer surface of the rotor 4 to prevent the high-pressure gas inside the engine from leaking to the outside. Since the radial sealing sheet 1 will continuously contact and rub against the surface of the rotor 4 during operation, it has good wear resistance to extend the service life and maintain the sealing effect. The rotor 4 is the core component of the cycloid rotor engine. Figure 4 The area surrounded by the radial sealing sheet is the rotor 4; the rotor 4 rotates during the operation of the cycloid rotor engine, pushing the gas flow and generating power. The shape of the rotor 4 matches the radial sealing sheet, and is a complex curved shape to ensure that the radial sealing sheet 1 can fit tightly to the rotor surface during the rotation process; the rotation of the rotor 4 causes the gas to compress or expand, thereby completing the working cycle of the cycloid rotor engine.

[0125] The outer surface of the rotor 4 is in direct contact with the radial sealing sheet; the radial sealing sheet 1 is in close contact with the outer surface of the rotor 4, and maintains airtightness as the rotor 4 rotates to prevent gas leakage. The rotation of the rotor 4 not only drives the cycloid rotor engine to work, but also ensures that the gas flows along the airflow path inside the cycloid rotor engine through the cooperation between its shape and the radial sealing sheet 1, thereby maintaining the normal operation of the cycloid rotor engine.

[0126] like Figure 7 The figure shows a schematic diagram of the airflow path of the micro-texture on the surface of the radial sealing plate of a cycloidal rotor engine. Through the pressure difference and the flow path, the system can effectively control the flow speed and direction of the gas to ensure a good sealing effect in the application and prevent gas leakage. This structure may be used in mechanical systems such as cycloidal rotor engines that require high-precision sealing and flow control. The arrows in the figure indicate the path of the airflow, showing the inlet and outlet of the gas, which are represented by solid and dotted lines respectively. From the gas flow path, the solid arrow in the figure indicates the inlet path of the gas, that is, where the gas enters the micro-texture on the surface of the radial sealing plate; the dotted arrow indicates the outlet path of the gas, that is, where the gas is discharged after flowing through the micro-texture on the surface of the radial sealing plate.

[0127] The gas enters the radial sealing plate from the upper air inlet 201 and the upper air outlet 203 on the left side of the figure, passes through a series of herringbone groove structures, and is discharged from the lower air inlet 202 and the lower air outlet 204 on the right side of the figure.

[0128] From the perspective of gas flow, the gas enters the radial sealing sheet 1 through the upper inlet 201 and the upper outlet 203 on the left side, flows through multiple curved surfaces and grooves inside the radial sealing sheet 1, and is discharged from the lower inlet 202 and the lower outlet 204 on the right side. The herringbone groove 101 structure inside the radial sealing sheet 1 guides the gas to flow along the designed path. These herringbone grooves 101 are curved in shape, and the purpose is to control the flow rate and pressure of the gas by extending the flow path of the gas and increasing the contact area between the gas and the groove wall; the herringbone grooves 101 change the flow direction of the gas to generate a local pressure difference, further enhancing the sealing effect and reducing the leakage of gas from the side edge.

[0129] From the perspective of gas flow control, when the gas enters from the upper gas inlet 201 and the upper gas outlet 203, the gas pressure gradually decreases in the curved channel; this pressure difference pushes the gas to flow along the set path, and finally discharges through the lower gas inlet 202 and the lower gas outlet 204. When the gas flows through these herringbone grooves 101, due to the changes in pressure and speed, a high-pressure area is formed at the gas inlet and a low-pressure area is formed at the gas outlet, which helps prevent the gas from leaking out of the radial sealing sheet and maintain the stability of the internal pressure.

[0130] Double layer herringbone groove 101

[0131] The surface micro-texture of the radial sealing sheet of the cycloid rotor engine of the present invention is as follows: Figure 1-3 As shown, a plurality of herringbone grooves 101 (with an upper layer and a lower layer) are formed on the surface of the radial seal, and the herringbone grooves 101 form a double-layer combination structure; the opening direction of the herringbone grooves 101 is consistent with the rotation direction of the rotor. Through these notches, gas can enter the notch opening 201.

[0132] Furthermore, the herringbone grooves 101 are distributed on the surface of the radial sealing sheet and are divided into two layers of grooves. The herringbone grooves 101 of each layer are arranged in parallel, the upper herringbone grooves 101 are on the outside, and the lower herringbone grooves 101 are on the inside; the herringbone grooves 101 in each layer are arranged in parallel with each other; each herringbone groove 101 maintains a certain interval and parallel relationship with respect to other grooves, and extends from the edge to the center of the radial sealing sheet;

[0133] The two layers of the double-layer herringbone groove 101 structure are connected by the arrangement of the layers; the herringbone groove 101 is divided into two layers, the upper layer and the lower layer; the herringbone grooves 101 of the upper layer and the lower layer maintain the same parallel arrangement mode, and the opening directions of the upper layer herringbone groove 101 and the lower layer herringbone groove 101 are consistent, ensuring the consistency and continuity of the gas flow;

[0134] Specifically, the grooves of the herringbone grooves 101 may be connected in parallel or staggered arrangement; further, the grooves of the herringbone grooves 101 are connected, and the herringbone grooves 101 in each layer are arranged in parallel to each other to form a plurality of independent flow channels; each of the herringbone grooves 101 has the same interval and maintains a fixed spacing, so that each groove can work independently, and the gas flow in the groove will not directly affect the gas flow of the adjacent grooves, thereby maintaining their respective pressure gradients and flow characteristics;

[0135] Specifically, the herringbone groove 101 is divided into two layers, an upper groove and a lower groove. The opening directions of the upper groove and the lower groove are consistent, and the high-pressure gas enters the upper herringbone groove and the lower herringbone groove from the groove opening 101 at the same time; a certain vertical distance is maintained between the upper and lower herringbone grooves 101, and the vertical distance ensures the independence of each layer of grooves while allowing the gas to flow freely between layers; the groove openings of the upper and lower layers are aligned in the vertical direction, so that the gas can pass through the upper and lower herringbone grooves at the same time, which can generate greater adsorption force and enhance the sealing effect.

[0136] Furthermore, the opening direction of the herringbone groove 101 is consistent with the rotation direction of the rotor (i.e., symmetrical about the symmetry centerline 104), that is, the opening direction of the herringbone groove 101 always points to the direction in which the opening of the herringbone groove faces the rotation direction of the rotor, so that the gas follows the flow path and can smoothly enter the upper gas inlet 201 and the upper gas outlet 203 in the groove, and form the required flow and pressure changes in the groove;

[0137] Specifically, the rotation direction of the rotor is relative to a fixed reference system (such as the housing or mounting base of the cycloid rotor engine), and does not change with changes in the viewing angle; the rotation direction of the rotor can be clockwise or counterclockwise, both are observed from a fixed viewing angle (usually from above or from the front), and does not change with changes in the viewing angle;

[0138] Specifically, each of the herringbone grooves 101 is composed of two symmetrical herringbone structures, and each groove expands from the center to both sides to form a herringbone; the apex of the herringbone structure faces the rotation direction of the rotor, while the sides extend outward, so that the gas is introduced into the groove during the rotation process and flows along the designed path, forming an effective pressure change and gradient.

[0139] Specifically, the two sides of each herringbone groove 101 are symmetrical, that is, the angle and length of the two herringbone structures are the same, so that the flow path of the gas in the groove is balanced, avoiding flow instability; the symmetry of the herringbone groove 101 allows the gas to form a uniform pressure gradient in the groove;

[0140] Alternatively, in the double-layer structure design, the herringbone grooves 101 may be arranged in a staggered manner, that is, the upper herringbone grooves 101 and the lower herringbone grooves 101 appear alternately in the longitudinal direction, and the gas enters the upper herringbone grooves and the lower herringbone grooves at the same time, thereby increasing the adsorption force between the radial seal and the rotor, making the sealing effect more stable;

[0141] The upper herringbone grooves 101 and the lower herringbone grooves 101 are arranged in a staggered manner in the vertical direction, and the opening of the upper herringbone groove 101 is located in the middle of the lower herringbone groove 101, so as to ensure the complexity and continuity of the gas flow path;

[0142] The opening directions of the upper and lower herringbone grooves 101 and 101 are consistent with the rotation direction of the rotor, so that the gas can smoothly enter the grooves and flow along the gas flow path;

[0143] The herringbone structures of each herringbone groove 101 maintain the same angle to ensure the balance of the gas flow path and the stability of the pressure gradient;

[0144] The two sides of the herringbone groove 101 are symmetrical, ensuring the balance of the gas flow path in the groove. This symmetry is maintained in both the upper and lower layers, ensuring the stability of the radial sealing plate; the staggered arrangement of the upper herringbone grooves 101 and the lower herringbone grooves 101 forms alternating flow paths in the vertical direction, further enhancing the complexity of the gas flow.

[0145] In summary, in order to more intuitively understand the arrangement of the double-layer herringbone grooves 101, it can be visually described as follows: the surface of the radial sealing plate, from the edge to the center, has a plurality of parallel or staggered herringbone grooves 101; the opening direction of each herringbone groove 101 is consistent with the rotation direction of the rotor, ensuring that the gas can smoothly enter the groove.

[0146] The herringbone groove 101 has a specific depth and width to optimize gas flow and pressure change, and is precisely designed through geometric parameters to achieve the best sealing effect; each layer of the herringbone groove 101 in the double-layer structure exists independently, but forms a complex combined structure as a whole, making the flow path of the gas in the groove more complicated;

[0147] The number of the herringbone grooves 101 is determined by the size of the radial sealing sheet and the required sealing performance. The larger the radial sealing sheet, the more grooves are required to ensure the sealing effect.

[0148] Specifically, the density of the herringbone grooves 101 is the number of grooves per unit area, which depends on the requirements of the radial sealing sheet and the operating parameters;

[0149] Furthermore, the density of the herringbone groove 101 can be divided into a high-density design and a low-density design; the high-density design can increase the number of herringbone grooves per unit area in applications requiring high sealing performance, so that the radial sealing plate increases the frequency of pressure changes, thereby improving the sealing effect; the low-density design can reduce the number of herringbone grooves per unit area in applications with high requirements for friction loss, so that the radial sealing plate can reduce the contact area and friction loss.

[0150] Specific parameter examples, for example, the fixed spacing between each herringbone groove 101 is 5 mm; the number of grooves and the groove density are as follows: from the perspective of the number of grooves, if the width of the radial sealing plate is 100 mm, there may be 20 grooves (spacing 5 mm) under high-density design, and there may be 10 grooves (spacing 10 mm) under low-density design; from the perspective of groove density, the high-density design has a larger number of grooves per unit area, for example, 4 grooves per square centimeter; the low-density design has a smaller number of grooves per unit area, for example, 2 grooves per square centimeter.

[0151] Specifically, the double-layer herringbone groove 101 divides the contact area between the radial sealing sheet and the rotor into multiple smaller areas, thereby reducing friction and increasing the sealing effect through the pressure change of the gas in the groove.

[0152] Further, the contact area between the radial sealing sheet and the rotor is the area where the radial sealing sheet actually contacts the rotor surface;

[0153] Further, the contact area of ​​the rotor is mainly located in the interval between the herringbone grooves 101, and the specific number and position of the contact area depend on the number and arrangement of the grooves, that is, a plurality of parallel or staggered herringbone grooves 101 are formed on the surface of the rotor, and each groove divides the contact surface into several parts;

[0154] Further, the spacing portion of the groove is the uncut solid portion between the herringbone grooves 101; the edge of the groove is the high-pressure area near the edge of the groove, and although the groove itself is not a contact surface, a tiny contact area is formed near the edge of the groove;

[0155] For example, there are five parallel herringbone grooves 101 on the radial sealing sheet, and the interval area between the grooves is the part that actually contacts the rotor; the specific position of the contact area is as follows:

[0156] Contact area 1: the spacing area between the first herringbone groove 101 and the second groove;

[0157] Contact area 2: the interval area between the second groove and the third groove;

[0158] Contact area 3: the interval area between the third groove and the fourth groove;

[0159] Contact area 4: the interval area between the fourth groove and the fifth groove;

[0160] Contact area 5: The spaced area between the fifth groove and the edge of the radial sealing sheet.

[0161] The double-layer herringbone groove 101 is divided into gas flow transmission, pressure transmission and force transmission by optimizing the gas flow path and pressure distribution;

[0162] Specifically, the gas flow is transmitted, when the rotor rotates, the gas enters the upper air inlet 201 and the upper air outlet 203 through the symmetry center line 104 of the herringbone groove 101, the opening direction of the herringbone groove 101 is consistent with the rotation direction of the rotor, so that the gas can be smoothly introduced into the groove; the double-layer herringbone groove 101 is a double-layer herringbone structure, the upper herringbone groove 101 and the lower herringbone groove 101 are staggered, and the gas enters the upper herringbone groove 101 and the lower herringbone groove 101 at the same time, so that the seal between the rotor and the radial sealing plate is more stable; the gas flow path continuously changes direction and speed during the flow process according to the geometric shape and arrangement of each groove, so that the gas forms different and relatively stable pressure gradients in the groove; finally, the gas is discharged from the upper air outlet 203 and the lower air outlet 204, so as to achieve exhaust from the high-pressure area on the right to the low-pressure area on the left.

[0163] Specifically, the pressure transmission, due to the complex flow path of the herringbone groove 101, the flow speed and direction of the gas in the groove are constantly changing, forming different pressure areas; the pressure change of the gas in the groove forms a negative pressure effect between the radial sealing sheet and the rotor through the principle of fluid dynamics, and the negative pressure makes the radial sealing sheet fit closely to the rotor, thereby enhancing the sealing effect; the double-layer structure of the double-layer herringbone groove 101 makes the pressure transmission of the gas between the upper herringbone groove 101 and the lower herringbone groove 101 more continuous and stable, ensuring that a uniform negative pressure area is formed on the entire surface of the radial sealing sheet;

[0164] Specifically, the force transmission, that is, the adsorption force generated by the negative pressure effect in the groove makes the radial sealing plate in close contact with the rotor surface, generating a force transmission of negative pressure effect; the negative pressure makes the radial sealing plate fit the rotor more closely, reducing the sliding friction on the contact surface, and the negative pressure effect formed reduces the friction between the radial sealing plate and the rotor; as the friction force is reduced, the wear and energy loss of the radial sealing plate and the rotor are also reduced accordingly, thereby extending the service life of the radial sealing plate and improving the overall efficiency of the cycloid rotor engine.

[0165] Sealed weir area 102

[0166] The surface micro-texture of the radial sealing sheet of the cycloid rotor engine of the present invention is as follows: Figure 1-3 As shown, the sealing weir area 102 is located in the middle part between two adjacent herringbone grooves 101, and is a groove-free area, thereby avoiding disturbance of the airflow during transition;

[0167] Specifically, the sealing weir area 102 is evenly distributed along the axial direction and directly connected to the adjacent herringbone groove 101 to form a smooth and continuous surface. The seamless connection ensures a smooth transition of the airflow from the herringbone groove 101 to the sealing weir area 102.

[0168] Specifically, the sealing weir area 102 and the adjacent herringbone grooves 101 form a continuous surface without physical partitions, effectively dividing the herringbone grooves 101 into several pairs and providing necessary blocking in the airflow path.

[0169] Specifically, the sealing weir area 102 forms a complementary structure with the herringbone groove 101 through its groove-free design, thereby blocking and controlling the airflow;

[0170] Furthermore, a continuous, complementary and complete sealing structure is formed between the sealing weir area 102 and the herringbone groove 101, so that the pressure difference and negative pressure effect generated by the herringbone groove 101 are strengthened in the sealing weir area 102, thereby enhancing the sealing effect; the sealing weir area 102 separates the herringbone groove 101 into several pairs, forming a plurality of independent sealing units; the sealing weir area 102 and the herringbone groove 101 enhance the pressure difference and negative pressure effect by blocking and controlling the airflow;

[0171] Furthermore, the sealing weir area 102 and the sealing dam area 103 work together, the sealing weir area 102 provides primary blocking, and the sealing dam area 103 provides secondary protection. The sealing weir area 102 blocks the airflow, and the sealing dam area 103 further prevents the airflow from escaping, forming double protection, so that the high-pressure area and the rotor rotation direction can achieve a sealing effect;

[0172] Furthermore, the sealing weir area 102 transfers the pressure difference and negative pressure effect generated by the herringbone groove 101 to the adjacent herringbone groove 101 and the sealing dam area 103 through its groove-free surface; when the airflow enters the herringbone groove 101 from the high-pressure area, the sealing weir area 102 acts as a blocking area to ensure that the airflow forms a stable pressure difference in the groove, further transferring and enhancing the negative pressure adsorption effect; the sealing weir area 102 plays a key control and transmission role in the airflow path, ensuring the overall sealing stability of the radial sealing plate.

[0173] Sealed Dam Area 103

[0174] The surface micro-texture of the radial sealing sheet of the cycloid rotor engine of the present invention is as follows: Figure 1-3 As shown, the sealing dam area 103 is located at the outer edge of the herringbone groove 101 and is a groove-free area, thereby avoiding disturbance of the airflow during transition; the sealing dam area 103 is a continuous and smooth surface without any grooves, which can block the escape of the airflow and reduce wear.

[0175] Specifically, the sealing dam area 103 is located at the outer edge of the herringbone groove 101 and arranged along the rotation direction of the rotor. In Figures 1-3, the sealing dam area 103 is generally shown as the outer edge of the radial sealing sheet, forming an additional sealing protection area;

[0176] Specifically, there is no physical separation between the sealing dam area 103 and the adjacent herringbone groove 101, and a continuous seamless connection is directly formed, so that the airflow transitions smoothly from the herringbone groove 101 to the sealing dam area 103; the sealing dam area 103 effectively blocks the airflow from the herringbone groove 101 area, preventing the gas from escaping from the outer side of the radial sealing sheet;

[0177] Furthermore, the sealing dam area 103 forms a continuous and complementary structure with the herringbone groove 101 through its own groove-free area, further blocking and controlling the airflow; the smooth surface of the sealing dam area 103 reduces the direct impact of the airflow and reduces the risk of wear;

[0178] Furthermore, the sealing dam area 103 is located outside the herringbone groove 101 to provide secondary blocking; the sealing weir area 102 and the sealing dam area 103 work together to ensure the sealing effect in the high pressure area and the rotation direction of the rotor;

[0179] Furthermore, the sealing dam area 103 transmits the pressure difference and negative pressure effect generated by the herringbone groove 101 and the sealing weir area 102 to the outer edge area of ​​the radial sealing plate through its groove-free surface; the sealing dam area 103 plays a final blocking and protective role in the airflow path, ensuring that the airflow forms a stable sealing effect on the surface of the radial sealing plate.

[0180] Example 1: Surface micro-texture of radial sealing sheet of a cycloidal rotor engine according to the present invention

[0181] This embodiment realizes an efficient and stable radial sealing sheet through detailed structural design and operation steps. Through the ingenious design of the herringbone groove 101 and reasonable installation steps, the sealing effect and service life of the cycloid rotor engine are significantly improved. This sealing structure is suitable for various high-pressure and high-speed cycloid rotor engines and can effectively improve their operating efficiency and reliability.

[0182] The present embodiment provides a sealing structure in which a herringbone groove 101 is opened on the curved surface of the radial sealing plate of the cycloid rotor engine. The specific structure is described as follows: the gas enters through the groove of the herringbone groove 101 and the upper air inlet 201 and the upper air outlet 203 of the radial sealing plate, and reaches the maximum pressure value in the groove of the herringbone groove 101; a plurality of herringbone grooves 101 are evenly distributed along the axial direction on the curved surface of the radial sealing plate, and the non-grooved area between two adjacent pairs of herringbone grooves 101 in the axial direction is a sealing weir area 102, and the non-grooved area outside the herringbone groove 101 is a sealing dam area 103. The herringbone groove 101 is an axisymmetric figure, and the herringbone groove 101 on the radial sealing plate is symmetrical along the symmetry center line 104 of the radial sealing plate. The gas enters the groove from the slot opening 201, and a negative pressure is generated by the difference in pressure at each point in the radial sealing plate curved surface herringbone groove 101, so that the radial sealing plate and the rotor are adsorbed together; finally, the gas is discharged from the upper gas outlet 203 and the lower gas outlet 204, realizing exhaust from the high-pressure area on the right to the low-pressure area on the left.

[0183] Furthermore, the herringbone groove 101 structure of the present invention needs to confirm the position structure of the component during operation during implementation. Specifically, the herringbone groove 101 confirms that a plurality of pairs of herringbone grooves 101 with straight edges are opened on the curved surface of the radial sealing plate; the groove depth of each pair of herringbone grooves 101 is equal, and is designed as an axially symmetrical figure, and is symmetrically distributed along the symmetry center line 104 of the radial sealing plate. Specifically, the upper air inlet 201 and the upper air outlet 203 are the positions where the gas enters the herringbone groove 101, ensuring that the airflow starts to flow. Specifically, the sealing sealing weir area 102 is a non-grooved area located between two axially adjacent pairs of herringbone grooves 101. Specifically, the sealing dam area 103 is an ungrooved area located outside the herringbone groove 101, and is arranged along the direction of rotation of the rotor.

[0184] Furthermore, the present embodiment provides a sealing structure in which a herringbone groove 101 is opened on the curved surface of the radial sealing plate of the engine. The specific assembly instructions are as follows: Before installing each component, prepare the components and tools. During component preparation, confirm that the radial sealing plate (with a double-layer herringbone groove 101 structure), the rotor, the fixing bolts and the installation fixture are ready. Specifically, the radial sealing plate has a double-layer herringbone groove 101 structure; the rotor is an engine rotor component that cooperates with the radial sealing plate; the fixing bolts and the installation fixture are used to fix the radial sealing plate. During tool preparation, confirm that the torque wrench, laser alignment tool, cleaning tool (such as alcohol and brush), and installation fixture are ready.

[0185] Assembly Step 1: Initial Inspection and Cleaning

[0186] (1) Check the components: First, check the radial sealing sheet to confirm that the double-layer herringbone grooves 101 on the radial sealing sheet have been processed according to the design requirements; then check that the groove depth of the herringbone grooves 101 is 1-5 μm, and there is a sealing weir area 102 without a groove between each pair of grooves, and a sealing dam area 103 is provided on the outside.

[0187] (2) Cleaning components: Use alcohol and a brush to clean the radial seal and rotor surface to ensure that there are no impurities and dirt.

[0188] Assembly step 2: Positioning and installing the radial seal double-layer herringbone groove 101

[0189] (3) Align the radial seal: Accurately position the radial seal in the radial seal fixing groove of the engine housing; use a laser alignment tool to ensure that the radial seal is fully aligned with the rotor surface.

[0190] (4) Preliminary fixation: Use a mounting fixture to preliminarily fix the radial sealing plate in position to ensure that it fits tightly against the rotor surface; confirm that the upper air inlet 201 and the upper air outlet 203 of the herringbone groove 101 face the high-pressure air inlet side so that the gas can enter the groove smoothly; confirm that the herringbone groove 101 is symmetrically distributed along the symmetry centerline 104 of the radial sealing plate.

[0191] Assembly Step 3: Install the seal seal weir area 102

[0192] (1) Aligning the sealing weir area 102: Positioning the sealing weir area 102 on the radial sealing sheet to ensure that the sealing weir area 102 is located between two pairs of axially adjacent herringbone grooves 101; and ensuring that the sealing weir area 102 and the herringbone grooves 101 are seamlessly connected to form a smooth transition.

[0193] (2) Fixing the sealing weir area 102: Use appropriate clamps and tools to fix the sealing weir area 102 to ensure that it is stable and has no gaps.

[0194] Assembly step 4: Install sealing dam area 103

[0195] (1) Aligning the sealing dam area: Position the sealing dam area 103 at the outer edge of the herringbone groove 101 and arrange it along the rotation direction of the rotor; ensure that the sealing dam area 103 is seamlessly connected with the herringbone groove 101 and the sealing dam area 102 to form a continuous sealing interface.

[0196] (2) Fixing the sealing dam area 103: Use appropriate clamps and tools to fix the sealing dam area 103 to ensure that it is stable and has no gaps.

[0197] Step 5: Adjust and tighten

[0198] (5) Adjust the position: Adjust the position of the radial sealing sheet so that it is completely aligned with the rotor surface; ensure that the herringbone grooves 101 are symmetrically distributed along the symmetry center line 104 of the radial sealing sheet; then check the alignment of the radial sealing sheet, the sealing weir area 102 and the sealing dam area 103 to ensure that all components are correctly positioned.

[0199] (6) Tighten the radial seal: Use a torque wrench to tighten the fixing bolts to ensure that the radial seal is firmly fixed to avoid any looseness.

[0200] Specifically, the sealing structure provided in this embodiment has a herringbone groove 101 on the curved surface of the radial sealing piece of the cycloid rotor engine. In order to be successfully installed on the cycloid rotor engine, preliminary preparation and processing of the radial sealing piece are required.

[0201] Preliminary preparation requires material preparation, tool preparation, and environmental preparation. Specifically, in the material preparation, it is necessary to select high-quality silicon carbide or cemented carbide materials to make radial seals; in the tool preparation, laser processing equipment, installation fixtures, torque wrenches, cleaning tools (such as alcohol, brushes, etc.); in the environmental preparation, ensure that the installation environment is clean, dust-free and dry to prevent impurities from entering and affecting the installation quality.

[0202] According to the design described in the present invention, the surface of the radial sealing plate is laser processed with double-layer herringbone grooves 101. Specifically, in the laser processing, a laser processing device is used to open a double-layer herringbone groove 101 on the surface of the radial sealing plate, and the groove depth is 1-5μm; ensure that the groove depth of each pair of herringbone grooves 101 is consistent, and a grooveless sealing weir area 102 is provided between each pair of herringbone grooves 101, and a sealing dam area 103 is provided along the rotation direction of the rotor; ensure the edge line shape of the herringbone groove 101, and select a straight line, arc, spiral line or sawtooth line according to the needs during processing. Further, attention should be paid to the processing accuracy during laser processing to ensure that the groove depth and groove shape required by the design can be achieved. Further, quality inspection is required after the laser processing is completed. Clean the finished product (radial sealing plate with double-layer herringbone groove 101 microtexture) after processing to ensure that there is no processing residue; use a microscope or other detection tools to check the groove depth and groove shape to ensure that the finished product after laser processing meets the installation requirements.

[0203] Furthermore, in order to be applied to a cycloid rotor engine, the sealing structure provided in this embodiment, which has a herringbone groove 101 on the curved surface of the radial sealing plate of the engine, must be subjected to installation verification (or operation test) after assembly. The installation verification (or operation test) includes air tightness test, operation observation, wear test and high speed test.

[0204] Specifically, in the air tightness test, start the engine, perform the air tightness test, and check the sealing effect between the radial sealing plate and the rotor surface; ensure that the sealing effect meets the design requirements by monitoring leakage and pressure changes; specifically, in the operation observation, especially during the initial operation and high-speed test, it is necessary to closely observe the working status of the radial sealing plate, and promptly discover and deal with any abnormalities; specifically, in the wear test, when the cycloid rotor engine runs at low speed for a period of time, it is necessary to check the working status of the radial sealing plate to ensure that there is no abnormal vibration or wear; specifically, in the high-speed test, it is necessary to gradually increase the engine speed to ensure that the radial sealing plate can still maintain a good sealing effect at high speed.

[0205] Furthermore, the sealing structure provided in this embodiment, in which a herringbone groove 101 is formed on the curved surface of the radial sealing sheet of the engine, requires regular inspection of the radial sealing sheet in actual working conditions. Specifically, the state of the micro-texture on the radial sealing sheet needs to be regularly inspected, especially the upper air inlet 201 and the upper air outlet 203 on the high-pressure air inlet side; at the same time, the integrity of the sealing weir area 102 and the sealing dam area 103 needs to be observed to ensure that there is no wear and damage.

[0206] Embodiment 2 The edge line type of the herringbone groove 101 of the present invention is a straight line

[0207] The advantage of a straight edge is that it provides a basic sealing effect and structural strength. Following all the contents of the general embodiment (Example 1), as mentioned above, except that the edge line type of the herringbone groove 101 is a straight line, other design components and parameters remain unchanged. The double-layer herringbone groove 101 scheme with a straight edge line type provided in this embodiment is relatively simple to design and process, and is suitable for sealing scenarios that require uniform distribution of pressure and negative pressure, such as the sealing of ordinary cycloid rotor engines and low and medium speed conditions in industrial application scenarios.

[0208] Furthermore, the straight edge double-layer herringbone groove 101 has a sealing effect in that the straight edge can provide a stable pressure distribution, which helps to evenly distribute the negative pressure; the flow path formed by the straight edge is relatively simple, and the turbulence effect is low, which is suitable for sealing scenarios that require smooth flow.

[0209] Specifically, in terms of pressure distribution and negative pressure effect, the straight edge line shape can achieve uniform pressure distribution, ensuring consistent pressure on the entire radial sealing plate surface; after the gas enters the groove, it flows along a straight path, and negative pressure is generated through the pressure difference at different positions, ensuring that the radial sealing plate is tightly adsorbed to the rotor surface.

[0210] Specifically, in terms of flow path and turbulence effect, the flow path formed by the straight edge is relatively simple, which reduces the complexity of the airflow and makes the flow smoother; due to the straight edge design, the turbulence effect of the airflow is lower when flowing in the groove, which is suitable for sealing scenarios that require smooth flow and reduces the impact of airflow disturbance on the sealing effect.

[0211] Furthermore, in terms of applicable scenarios, the straight edge profile is suitable for sealing ordinary cycloid rotor engines that require uniformly distributed pressure and negative pressure, ensuring stable operation of the engine under different operating conditions; on the other hand, under low and medium speed conditions, the straight edge profile can provide a stable sealing effect and a longer service life, which is suitable for most industrial application scenarios.

[0212] Furthermore, from the perspective of processing radial sealing sheets, the design of the straight edge profile is relatively simple, does not require complex curves or multi-level structures, and is suitable for standardized production; the straight edge profile facilitates high-precision manufacturing through laser processing technology, ensuring that the depth and shape of each pair of grooves are consistent, thereby ensuring the sealing effect.

[0213] Example 3 The edge line shape of the herringbone groove 101 of the present invention is an arc shape

[0214] The advantage of the arc edge is that it helps to generate turbulence when the fluid passes through and increase energy dissipation. Following all the contents of the general embodiment (Example 1), as mentioned above, except that the edge line of the herringbone groove 101 is arc-shaped, other design components and parameters remain unchanged. The arc-shaped double-layer herringbone groove 101 scheme provided in this embodiment has a smooth curve and is suitable for high-precision sealing scenarios that require smooth airflow and reduced wear, such as high-precision cycloidal rotor engines and high-speed cycloidal rotor engines.

[0215] The arc-shaped double-layer herringbone groove 101 has a sealing effect in that the arc-shaped edge can smoothly guide the airflow, reduce airflow turbulence, and maintain flow stability; the arc shape can alleviate stress concentration when the airflow turns, reduce local stress, and thus reduce wear.

[0216] In terms of airflow guidance and stability, the arc edge line shape can smoothly guide the airflow, reduce the turbulence of the airflow when turning, and make the flow more stable. The smooth curve allows the airflow to flow smoothly along the arc edge, avoiding the flow instability that may be caused by the straight edge; due to the shape of the arc, the airflow is not easy to form turbulence and eddy currents when flowing in the groove, thereby reducing airflow turbulence, maintaining flow stability, and helping to improve the sealing effect.

[0217] In terms of stress distribution and wear control, the arc shape can effectively alleviate the stress concentration of the airflow when it turns, and avoid the local high stress caused by the sharp turn of the airflow. This smooth transition reduces stress concentration and reduces the local stress of the radial sealing piece; by reducing stress concentration and airflow turbulence, the arc edge line shape can significantly reduce wear and extend the service life of the radial sealing piece, which is particularly suitable for high-precision and high-speed sealing scenarios.

[0218] In terms of applicable scenarios, the arc edge line design is suitable for cycloidal rotor engine applications that require smooth airflow and high-precision sealing, ensuring the sealing effect in a high-precision environment; under high-speed conditions, the arc edge line design can effectively reduce airflow turbulence and wear, provide a stable sealing effect, and is suitable for high-speed cycloidal rotor engines.

[0219] From the processing of radial sealing sheets, the design of the arc edge line can be optimized according to the specific application scenario, and the curvature and distribution of the arc can be adjusted to achieve the best airflow guidance and stress distribution effects; laser processing technology can accurately realize the design of the arc edge, ensuring that the depth and shape of each pair of grooves are consistent, ensuring high-quality sealing effects.

[0220] Example 4 The edge line shape of the herringbone groove 101 of the present invention is a spiral line shape

[0221] The advantage of the helical edge is that it further enhances the turbulence effect and increases the residence time of the fluid on the sealing surface. Following all the contents of the general embodiment (Example 1), as mentioned above, except that the edge line of the herringbone groove 101 is a spiral line, other design components remain unchanged. The spiral double-layer herringbone groove 101 scheme provided in this embodiment is a rotating curve. The spiral edge increases the complexity of the flow path by guiding the airflow to flow along a spiral path, significantly enhancing the pressure difference effect and the viscosity effect, and providing a stronger negative pressure effect. It is suitable for high-efficiency sealing scenarios (or scenarios with complex flow paths) that require enhanced pressure difference effect and viscosity effect, such as high-pressure cycloidal rotor engines.

[0222] The spiral double-layer herringbone groove 101 has a sealing effect in that the spiral edge can guide the airflow to flow along the spiral path, increase the complexity of the flow path, and enhance the pressure difference effect and viscosity effect; due to the complex flow of the airflow in the spiral path, the negative pressure effect is stronger and the sealing effect is better.

[0223] In terms of airflow guidance and pressure difference effect, the spiral edge line shape can guide the airflow to flow along the spiral path, increasing the complexity of the flow path. The design of the spiral path requires the airflow to go through more bends and turns when flowing in the groove, increasing the flow resistance of the airflow; due to the complex flow of the airflow in the spiral path, the pressure difference at different positions is more obvious, forming a stronger pressure difference effect. This can generate a greater negative pressure when the airflow passes, thereby enhancing the adsorption force between the radial sealing sheet and the rotor surface.

[0224] From the perspective of viscosity effect, the spiral edge line shape increases the complexity of the flow path, which increases the contact area between the airflow and the groove wall during the flow process, thereby enhancing the viscosity effect. The enhancement of the viscosity effect slows down the flow speed of the airflow in the groove;

[0225] In terms of negative pressure effect, due to the complex flow of airflow in the spiral path, the negative pressure effect is stronger, which makes the adsorption force between the radial sealing sheet and the rotor greater, ensuring the stability and reliability of the seal.

[0226] In terms of applicable scenarios, the spiral edge line design is suitable for high-pressure cycloid rotor engine seals that require enhanced pressure difference effect and viscosity effect, ensuring the sealing effect under high-pressure environment; in applications with complex flow paths and high-efficiency sealing requirements, the spiral edge line design can provide better sealing effect and stability.

[0227] From the processing of radial sealing sheets, the design of the spiral edge line can be optimized according to the specific application scenario, and the angle and curvature of the spiral can be adjusted to achieve the best airflow guidance and pressure difference effect; laser processing technology can accurately realize the design of the spiral edge, ensuring that the groove depth and shape of each pair of grooves are consistent, ensuring high-quality sealing effect.

[0228] Example 5 The edge line shape of the herringbone groove 101 of the present invention is a zigzag shape

[0229] The advantage of the serrated edge is that the pressure difference of the sealing surface is increased through a local pressure drop, thereby improving the sealing performance. Following all the contents of the general embodiment (Example 1), as mentioned above, except that the edge line shape of the herringbone groove 101 is serrated, other design components and parameters remain unchanged. The serrated double-layer herringbone groove 101 scheme provided in this embodiment has multiple peaks and valleys, and is suitable for high-strength sealing scenarios that require stronger sealing force and adsorption force, such as cycloidal rotor engines under extreme working conditions.

[0230] The serrated double-layer herringbone groove 101 has a sealing effect in that the serrated edge can produce a stronger turbulence effect, thereby enhancing the mixing and pressure difference effect of the gas; the serrated edge can increase the shear force of the airflow, thereby further enhancing the adsorption force between the radial sealing sheet and the rotor surface.

[0231] In terms of turbulence effect and gas mixing, the sawtooth edge can produce a strong turbulence effect when the airflow passes through it through its multiple peaks and valleys. This turbulence effect can form a complex flow path for the airflow in the slot, increasing the degree of gas mixing; due to the enhanced turbulence effect, the speed of the airflow in the slot changes more dramatically, thereby enhancing the pressure difference at different positions and forming a stronger pressure difference effect. This pressure difference effect can further improve the adsorption force between the radial sealing sheet and the rotor surface.

[0232] In terms of shear force and adsorption force, the multiple peaks and valleys of the sawtooth edge can increase the shear force of the airflow, making the flow of airflow in the slot more complex. This shear force can effectively enhance the adsorption force between the radial sealing sheet and the rotor surface; by enhancing the shear force and pressure difference effect of the airflow, the sawtooth edge line shape can significantly improve the sealing effect, allowing the radial sealing sheet to maintain stable sealing performance under high-intensity working conditions.

[0233] In terms of applicable scenarios, the serrated edge line design is suitable for high-strength sealing scenarios that require stronger sealing and adsorption forces, ensuring the cycloidal rotor engine under extreme working conditions; moreover, under high pressure and high temperature conditions, the serrated edge line can provide stronger sealing force and stability, which is suitable for high-demand industrial applications.

[0234] From the processing of radial sealing sheets, the design of the serrated edge line can be optimized according to the specific application scenario, and the size and spacing of the serrations can be adjusted to achieve the best turbulence effect and shear force; laser processing technology can accurately realize the design of the serrated edge, ensuring that the depth and shape of each pair of grooves are consistent, ensuring high-quality sealing effects.

[0235] Example 6 Mixed edge line type of the herringbone groove 101 of the present invention

[0236] The mixed edge line type, as mentioned above, is formed by combining the technical features of the different edge line types in Examples 2-5, and further enhances the sealing performance of the radial sealing plate. Following all the contents of the general embodiment (Example 1), as mentioned above, except that the edge line type of the herringbone groove 101 is a mixed edge line type (that is, the edge line type of a straight line, an arc line, a spiral line and a serrated line is combined on the same radial sealing plate), other design components and parameters remain unchanged. The double-layer herringbone groove 101 solution with a mixed edge line type provided in this embodiment is suitable for complex sealing scenarios that require multiple effects, such as comprehensive sealing requirements under various working conditions.

[0237] The sealing principle of the mixed edge line type is mainly to form a liquid film, increase the sealing pressure difference, generate turbulence and uniform pressure distribution. Specifically, the formation of the liquid film is that during the sealing process, the fluid will form a liquid film on the edge of the herringbone groove 101; the existence of the liquid film can fill the sealing gap, reduce the leakage channel, and thus improve the sealing performance; the liquid film can provide uniform pressure distribution to ensure the integrity and stability of the sealing surface. Specifically, the increase in the sealing pressure difference is that the sawtooth line part can produce a local pressure drop when the fluid passes through its special shape, thereby increasing the pressure difference on both sides of the sealing surface; this pressure difference helps to improve the sealing effect, because the larger pressure difference can effectively prevent fluid leakage. Specifically, the generation of turbulence is that the design of the arc and spiral parts causes the fluid to generate turbulence near the sealing surface; turbulence increases the energy dissipation of the fluid and reduces the possibility of leakage; and turbulence can also destroy the laminar state of the fluid, further improving the sealing effect.

[0238] The uniform pressure distribution is a reasonably designed mixed edge line type that can make the pressure distribution of the liquid film more uniform, avoiding the situation where the local pressure is too high or too low; the uniform pressure distribution helps to improve the stability and reliability of the seal and reduce the risk of seal failure. Specifically, in the mixed edge line type design of the herringbone groove 101, the straight line edge line type, the arc line edge line type, the spiral line edge line type and the sawtooth line edge line type can be combined to enhance the effect. Specifically, the straight line is combined with the arc line, and the alternation of straight lines and arc lines can be formed on the edge of the herringbone groove 101. The straight line part provides a stable seal, and the arc line part can increase the elasticity and adaptability of the seal. Specifically, the straight line is combined with the spiral line, and the combination of the straight line and the spiral line can produce a spiral sealing line on the sealing surface to enhance the sealing effect; the presence of the spiral line can increase the turbulence of the fluid and improve the reliability of the seal. Specifically, the arc line is combined with the sawtooth line, and the combination of the arc line and the sawtooth line can form a complex line type on the edge of the herringbone groove 101; the arc line part provides better sealing performance, and the sawtooth line part can increase the pressure difference of the seal and improve the stability of the seal.

[0239] By combining different edge profiles, uniform pressure distribution and negative pressure effect can be achieved on the entire radial sealing sheet, ensuring stable sealing performance. Specifically, the combination of arc and straight edge profiles can smoothly guide the airflow, reduce airflow turbulence and stress concentration, and thus reduce the wear of the radial sealing sheet. Specifically, the combination of spiral and serrated edge profiles can significantly enhance the pressure difference effect and turbulence effect of the airflow, and improve the sealing effect and adsorption force. Specifically, the design of mixed edge profiles enables the radial sealing sheet to adapt to a variety of operating conditions, improving the versatility and adaptability of the radial sealing sheet.

[0240] From the perspective of radial sealing sheet processing, the design of mixed edge lines can be optimized according to specific application scenarios, and the proportions and layouts of various edge lines can be adjusted to achieve the best sealing effect. Laser processing technology can accurately realize the design of mixed edge lines, ensuring that the depth and shape of each pair of grooves are consistent, thereby ensuring high-quality sealing effects.

[0241] In terms of applicable scenarios, the design of mixed edge lines is suitable for complex sealing scenarios that require multiple effects. The mixed edge lines can provide stronger sealing force and stability, and are suitable for high-demand industrial applications. Specifically, under high-pressure conditions, the serrated lines and straight sections can provide sufficient structural strength and sealing pressure difference. Specifically, under high-speed conditions, the arcs and spirals can enhance the turbulence effect and reduce leakage. Specifically, under high-temperature conditions, the combination of different line types can adapt to the expansion and contraction of the material caused by temperature changes and maintain the sealing effect.

[0242] The working principle of the radial sealing surface micro-texture of the cycloid rotor engine described in the present invention is as follows:

[0243] First, the design and working principle of the double-layer herringbone groove 101

[0244] From the perspective of the double-layer structure, the double-layer herringbone groove 101 is designed on the surface of the radial sealing plate, and two layers of herringbone grooves 101 are opened, which are located at different heights or depths. The hierarchical distribution of different heights or depths ensures that the gas forms multiple flow paths and pressure gradients at different levels; the upper and lower grooves of the double-layer herringbone grooves 101 are staggered, and the opening of the upper herringbone groove 101 is aligned with the middle of the lower herringbone groove 101. The staggered arrangement of the upper and lower layers increases the complexity of gas flow and the diversity of paths. Therefore, the double-layer herringbone grooves 101 provide multiple sealing barriers, so that the gas needs to pass through multiple complex paths to leak out; the double-layer structure can make the negative pressure adsorption force more evenly distributed on the surface of the radial sealing plate, reduce the problem of excessive or insufficient local pressure, and thus effectively reduce the vibration (vibration) phenomenon of the radial sealing plate.

[0245] From the perspective of the herringbone shape, the shape of each layer of the double-layer herringbone groove 101 is a herringbone, that is, a V-shaped structure; the opening direction matches the rotation direction of the rotor, which can ensure that the gas can smoothly enter the groove; the two sides of the herringbone groove 101 are symmetrical, ensuring the balance of the gas flow path, and the symmetrical structure can be consistent in the upper and lower layers to form a stable pressure gradient. Therefore, the geometric shape of the herringbone groove 101 (such as a straight line, arc, spiral line, serrated line, etc.) can be optimized according to specific application requirements to achieve the best pressure distribution and fluid viscosity effect. Different shapes will have different effects on the flow path and pressure difference of the fluid, and can be adjusted and optimized according to actual conditions.

[0246] When the rotor rotates, the gas enters the slot through the opening of the herringbone slot 101, and the gas starts to flow. The upper herringbone slot 101 receives the gas first, and the gas flows along the V-shaped path, and then alternately enters the lower herringbone slot 101; due to the staggered arrangement of the upper and lower herringbone slots 101, the flow path of the gas in the slot becomes complicated; the complicated path helps to increase the resistance of the gas flow, thereby forming different pressure gradients in the slot.

[0247] Based on the gas lubrication theory, the design reduces friction and enhances the sealing effect by forming a gas film between the radial seal and the rotor. The double-layer herringbone groove 101 design optimizes gas flow and pressure distribution through a complex groove structure according to the gas lubrication theory. The complexity of the gas flow path and the formation of the pressure gradient create a negative pressure effect in the groove, thereby enhancing the adsorption force between the radial seal and the rotor.

[0248] From the perspective of the gas flow process, the gas enters the groove through the opening symmetric center line 104 of the herringbone groove 101; the opening direction of the double-layer herringbone groove 101 is consistent with the rotation direction of the rotor, ensuring that the gas can be smoothly introduced; the upper groove and the lower groove of the double-layer herringbone groove 101 are staggered, and the gas first enters the upper herringbone groove 101, and then enters the lower herringbone groove 101 along the staggered flow path, forming a complex flow path;

[0249] In terms of pressure changes, due to the different geometric shapes and flow resistances at different positions in the groove, different pressure areas will be formed when the gas flows in the groove; the herringbone design and double-layer structure of the groove make the gas constantly change direction and speed during the flow process, generating different pressure gradients; each layer of grooves in the double-layer structure can generate an independent pressure gradient, and the staggered arrangement of the upper and lower herringbone grooves 101 allows these gradients to be superimposed on each other, forming a more complex and stable pressure change.

[0250] From the perspective of the negative pressure effect, due to the pressure gradient in the groove, the gas forms a negative pressure area at certain positions; the negative pressure effect generates an adsorption force between the radial sealing sheet and the rotor; the negative pressure effect enables the radial sealing sheet to fit the rotor surface more closely, reducing gas leakage; further, in the double-layer structure, the negative pressure effects of the upper and lower herringbone grooves 101 are superimposed on each other, and the negative pressure forms a double-layer superposition effect, which makes the overall negative pressure effect more significant and enhances the tightness of the radial sealing sheet.

[0251] From the perspective of the pressure difference effect, the design of the double-layer herringbone groove 101 forms a complex flow channel structure on the radial sealing plate. When high-pressure gas enters these herringbone grooves 101 from the rotor, due to the flow channel structure in the groove, the gas will form different flow paths and speeds in the groove. Due to the different flow paths and speeds in various parts of the groove, different pressure distributions will be formed in various parts of the groove. The pressure difference effect is the pressure difference formed due to the different pressures at different positions in the groove; and the pressure difference causes the gas to flow from the high-pressure area to the low-pressure area. Normally, the pressure is higher at the corners of the groove, while the pressure is lower in other areas. This pressure difference will cause negative pressure areas to form in the groove. These negative pressure areas will generate adsorption force, which will tightly adsorb the radial sealing plate to the rotor surface, thereby enhancing the sealing effect and reducing the vibration and movement of the radial sealing plate.

[0252] From the perspective of fluid viscosity effect, the double-layer herringbone groove 101 design has two layers of herringbone groove 101 structure on the surface of the radial sealing plate. The fluid viscosity effect is that when the gas flows through the herringbone groove 101, the groove wall will hinder the flowing gas; specifically, in the boundary layer formed near the groove wall, the gas flow velocity is low; while the flow velocity in the central area is high, forming a velocity gradient. Through this viscosity effect, the pressure difference effect in the groove can be further enhanced. Such a design can increase the complexity of the fluid path in the groove, further enhance the pressure difference effect and viscosity effect, thereby improving the adsorption force and sealing effect.

[0253] Second, the design and working principle of the sealing weir area 102

[0254] The sealing weir area 102 is a non-grooved area between two adjacent pairs of herringbone grooves 101. The sealing weir area 102 is designed to have a smooth surface without any thinning or grooving. The smooth surface of the sealing weir area 102 forms a continuous sealing barrier to prevent gas from leaking through the gaps between the herringbone grooves 101 inside the radial sealing sheet.

[0255] The sealing weir area 102 has no notches, so gas cannot flow in the sealing weir area 102, thereby preventing gas leakage. The sealing weir area 102 forms multiple continuous non-grooved areas on the radial sealing sheet, and these non-grooved areas work together to further improve the overall sealing performance of the radial sealing sheet.

[0256] The sealing weir area 102 can balance the pressure distribution on the radial sealing piece, reduce the local pressure concentration phenomenon, thereby reducing the vibration phenomenon of the radial sealing piece and improving the stability of the radial sealing piece.

[0257] The sealing weir area 102 is designed as a smooth surface, which can reduce friction when in contact with the rotor surface, thereby reducing wear. Since the sealing weir area 102 reduces friction and wear, the radial sealing piece can be used for a long time under high pressure and high temperature environment, reducing the need for frequent replacement and increasing the service life of the radial sealing piece.

[0258] Third, the design and working principle of the sealing dam area 103

[0259] The sealing dam area 103 is an ungrooved area outside the herringbone groove 101, and the sealing dam area 103 is an ungrooved area. The sealing dam area 103 is not thinned, and relative to the grooved area, the original thickness, strength and material integrity of the radial sealing sheet are retained, so that the radial sealing sheet has higher compressive strength and structural stability in the sealing dam area 103. When the high-pressure gas exerts an impact on the radial sealing sheet, the sealing dam area 103 can effectively resist deformation due to its greater thickness and strength, thereby preventing the sealing dam area 103 from being damaged in its entirety or in part.

[0260] The sealing dam area 103 is arranged at a key position of the gas flow path, evenly distributed along the edge of the radial sealing sheet, and covers the key area of ​​the radial sealing sheet, especially the part of the gas flow path that is easily impacted.

[0261] The sealing dam area 103 disperses the impact force of the high-pressure gas to a larger area, reducing the local stress concentration phenomenon. The stress dispersion formed by the sealing dam area 103 can prevent the radial sealing sheet from being deformed and damaged due to excessive local stress. When the cycloidal rotor engine is running, the sealing dam area 103, as the first line of defense, can absorb and alleviate part of the impact energy during the flow of high-pressure gas and protect the subsequent sealing structure.

[0262] Fourth, the layout (coordination) and working principle of the sealing weir area 102 and the sealing dam area 103

[0263] (1) Cooperation of the sealing weir area 102 and the sealing dam area 103 for the sealing function

[0264] The sealing weir area 102 prevents gas leakage inside the radial sealing sheet by its grooveless design, while the sealing dam area 103 provides an additional sealing layer by its position and thickness to prevent gas leakage from outside the radial sealing sheet. Therefore, the sealing weir area 102 and the sealing dam area 103 together form a multiple sealing barrier.

[0265] The smooth surface of the sealing weir area 102 is evenly distributed on the radial sealing sheet, which helps to distribute the pressure on the radial sealing sheet and reduce local stress concentration. The sealing dam area 103 provides pressure buffering through its thickness, further improving the sealing effect of the radial sealing sheet.

[0266] (2) Coordination of the support function between the sealing weir area 102 and the sealing dam area 103

[0267] The combination of the sealing weir area 102 and the sealing dam area 103 makes the radial sealing sheet more stable when subjected to the impact of high-pressure gas. The sealing weir area 102 provides basic support, while the sealing dam area 103 further enhances the overall stability of the radial sealing sheet by increasing thickness and strength.

[0268] The grooveless design of the sealing weir area 102 reduces wear, and the strength and thickness of the sealing dam area 103 improve the wear resistance and impact resistance, which together can significantly extend the service life of the radial sealing sheet.

[0269] (3) From the perspective of gas flow path control, the cooperation between the sealing weir area 102 and the sealing dam area 103

[0270] When the gas flows into the herringbone groove 101, the sealing weir area 102, as a groove-free area, blocks the channel for the gas to flow directly inside the radial sealing piece. Therefore, the sealing weir area 102 effectively prevents the gas from leaking out from the inside of the radial sealing piece, ensuring the integrity of the seal.

[0271] The sealing dam area 103 is located outside the herringbone groove 101, forming an additional sealing barrier. This barrier effectively cuts off the gas that penetrates from the outside, further enhancing the sealing effect. Even if there is some small leakage in the herringbone groove 101 area, the sealing dam area 103 can block the gas and prevent it from eventually leaking out of the sealing device.

[0272] (4) From the perspective of pressure management, the cooperation between the sealing weir area 102 and the sealing dam area 103

[0273] The sealing weir area 102 is a smooth contact surface without grooves, which can help distribute the pressure more evenly on the radial sealing piece. The sealing weir area 102 can avoid local stress concentration and reduce the deformation or damage of the seal under high pressure environment. The smooth contact interface forms a buffer for the sealing weir area 102, which is conducive to the smooth transition of pressure and reduces the stress peak.

[0274] The sealing dam area 103 increases the thickness and strength of the radial sealing sheet, and provides an additional pressure buffer. Even under high pressure, the strength of the sealing dam area 103 can withstand the pressure and prevent the radial sealing sheet from being deformed or damaged as a whole. This further improves the compressive performance of the radial sealing micro-texture of the present invention under high temperature and high pressure conditions.

[0275] Furthermore, the present invention can comprehensively solve the vibration, air leakage, wear problems of the radial seal of the cycloid rotor engine, as well as the cylinder vibration problem and the seal failure problem through the double-layer herringbone groove 101 radial seal of the present invention. The specific solution is as follows:

[0276] First, the vibration phenomenon of the cycloid rotor engine

[0277] Double layer herringbone groove 101

[0278] From the structure of the double-layer herringbone groove 101, the present invention opens a double-layer herringbone groove 101 on the surface of the radial sealing plate. The geometric shape of the double-layer herringbone groove 101 is "V" shaped, and the opening of the double-layer herringbone groove 101 faces the high-pressure air intake side, and the shape can be a straight line, an arc, a spiral line or a sawtooth line. The double-layer herringbone groove 101 has two levels of V"-shaped grooves, and the double-layer herringbone groove 101 allows the airflow to pass through a more complex path.

[0279] From the perspective of the airflow path, the double-layer herringbone groove 101 opens on the high-pressure air inlet side, allowing the gas to enter the groove. When the high-pressure gas flows from the high-pressure side of the rotor into the double-layer herringbone groove 101, due to the geometric shape and complex flow path of the double-layer herringbone groove 101, the gas will produce changes in speed and flow path when flowing through the groove. The herringbone grooves 101 on the radial sealing sheet are symmetrically distributed to ensure that the airflow is evenly distributed when entering and flowing through the groove, and the sealing weir area 102 and the sealing weir area between the grooves enhance the sealing effect.

[0280] The upper herringbone groove 101 is open on the high-pressure air inlet side so that the gas can enter the groove. The high-pressure gas enters the opening area of ​​the herringbone groove 101 from the high-pressure side of the rotor. Due to the sudden encounter with the groove wall, the air flow speed slows down, the pressure increases, and a high-pressure area is formed. When the air flow flows in the groove, the gas continues to flow to the middle of the herringbone groove 101 in the middle of the upper herringbone groove 101, the flow path gradually becomes smooth, the flow rate increases, and the pressure decreases to form a pressure difference in the groove, forming a low-pressure area. At the corners in the upper herringbone groove 101, the gas flow direction changes, the flow rate decreases, the pressure increases, and a local high-pressure area is formed. At the outlet of the upper herringbone groove 101, the gas approaches the outlet area of ​​the groove, the flow rate further increases, and the pressure decreases to form a pressure difference in the groove, forming a low-pressure area. In the lower groove, as in the case of the upper herringbone groove 101, the air flow will also experience changes in speed and pressure, forming more high-pressure and low-pressure areas. The double-layer herringbone groove 101 structure forms a cumulative pressure difference effect, increases the length and complexity of the airflow path, and makes the negative pressure effect in the low-pressure area more significant.

[0281] Due to the double-layer herringbone groove 101 structure, a significant pressure difference is generated between the high-pressure area and the low-pressure area, which causes a negative pressure area to form in the groove. The high-pressure area is mainly located at the inlet and the corners in the groove, and the low-pressure area is mainly located in the middle and outlet areas of the groove.

[0282] High-pressure areas usually appear in areas where gas flow is obstructed or flow rate is low, such as the inlet area and the corners of the double-layer herringbone groove 101. In the inlet area of ​​the double-layer herringbone groove 101, when the gas just enters the slot, the flow is obstructed by the slot wall, the flow rate decreases, and the pressure increases. At the corners in the slot (or the corners or curvature of the slot change greatly), the gas flow direction changes, the flow rate decreases, and the pressure increases. These corners will form local high-pressure areas. Low-pressure areas usually appear in areas where gas flow is smoother and the flow rate is higher, such as the middle and outlet areas of the double-layer herringbone groove 101 and the characteristic positions in the slot. In the middle and outlet areas of the double-layer herringbone groove 101, the gas flows through the slot into the middle of the slot. As the flow path is extended, the flow rate increases and the pressure decreases. Especially in the area where the slot narrows or a nozzle effect is formed, the flow rate is further increased and the pressure is further reduced. At certain locations in the channel, due to the geometry of the channel, the gas flow path is complex and the flow velocity in some areas is significantly higher than in other areas, thus forming a low-pressure area.

[0283] When the pressure in the low-pressure area is significantly lower than that in the high-pressure area, a negative pressure area is formed. The negative pressure in the low-pressure area will generate an adsorption force, which will tightly adsorb the radial sealing sheet to the rotor surface. The adsorption force is an inward suction force that acts on the surface of the entire radial sealing sheet, so that the radial sealing sheet is in close contact with the rotor surface. The double-layer herringbone groove 101 structure forms a continuous adsorption effect, ensuring that the negative pressure adsorption force is evenly distributed and continuously acts on the surface of the entire radial sealing sheet.

[0284] Due to the fixing effect of the negative pressure adsorption force, the radial sealing sheet is fixed to the rotor surface during operation, reducing the free vibration and movement of the radial sealing sheet. The negative pressure adsorption force effectively suppresses the vibration and impact of the radial sealing sheet, thereby suppressing the vibration phenomenon. The negative pressure adsorption force makes the radial sealing sheet fit tightly with the rotor surface, reducing gas leakage. The double-layer herringbone groove 101 optimizes the contact surface between the radial sealing sheet and the rotor while guiding the airflow and forming negative pressure, further improving the radial sealing performance.

[0285] Second, the cylinder vibration phenomenon of the cycloid rotor engine

[0286] Double layer herringbone groove 101

[0287] like Figure 4 As shown, the double-layer herringbone groove 101 has an axisymmetric design and a uniformly distributed groove structure, which effectively solves the cylinder vibration problem by optimizing the airflow path and pressure distribution. The axisymmetric design ensures the uniform distribution of airflow and adsorption force, reducing the vibration problem caused by the asymmetric design; the uniformly distributed groove structure makes the radial sealing sheet evenly stressed, avoiding local stress concentration, thereby reducing the vibration phenomenon of the cylinder.

[0288] The double-layer herringbone groove 101 structure is symmetrically distributed along the center line of the radial sealing plate to form an axisymmetric structure; the axisymmetric design ensures that when the radial sealing plate contacts the rotor surface, the airflow flows evenly in all directions to form a uniform negative pressure and adsorption force.

[0289] Double-layer herringbone groove 101 forms an axisymmetric design

[0290] From the perspective of balancing the airflow pressure, the axisymmetric design of the double-layer herringbone groove 101 enables the airflow to form a symmetrical pressure distribution when flowing on the surface of the radial sealing plate. This symmetrical pressure distribution can avoid the local high pressure area caused by the asymmetrical design. Furthermore, the symmetrical pressure distribution reduces the local high pressure and stress concentration, thereby preventing the formation of vibration marks. The uniform distribution of stress can significantly reduce the wavy wear phenomenon on the cylinder body surface.

[0291] From the perspective of uniform adsorption force, the axisymmetric structure makes the airflow evenly distributed on the surface of the radial seal, and the negative pressure adsorption force is also evenly distributed. The uniform adsorption force ensures that the radial seal and the rotor surface are stably fitted, reducing the wear caused by vibration and uneven friction. Furthermore, the uniform adsorption force reduces the irregular movement and relative sliding between the radial seal and the rotor surface, preventing local excessive wear caused by vibration, thereby reducing the chattering phenomenon.

[0292] From the perspective of the airflow path, when the airflow enters the herringbone groove 101 from the high-pressure area, due to the axisymmetric design of the herringbone groove 101, the airflow is evenly distributed to the left and right directions when entering the groove; the airflow flows along a symmetrical path in the groove, and the symmetrical flow will not form excessive pressure accumulation on one side. When the airflow flows in the groove, under the axisymmetric design, the airflow flows along the symmetrical path of the herringbone groove 101. The two arms of the herringbone groove 101 are symmetrically distributed, and the airflow is divided into two streams in the groove, flowing along the two arms of the "V" shape respectively; due to the symmetrical design, the airflow forms a uniform pressure distribution in the groove, avoiding the generation of local high-pressure areas.

[0293] Furthermore, the airflow path goes through three stages: the high-pressure area enters the double-layer herringbone groove 101, the airflow flows in the groove, and the airflow transfers between the grooves. When the airflow enters the herringbone groove 101 from the high-pressure area, due to the axisymmetric design of the herringbone groove 101, the airflow is evenly distributed to the left and right directions when entering the groove; the airflow flows along a symmetrical path in the groove, and the symmetrical flow will not form excessive pressure accumulation on one side; when the airflow flows in the groove, under the axisymmetric design, the airflow flows along the symmetrical path of the herringbone groove 101. The two arms of the herringbone groove 101 are symmetrically distributed, and the airflow is divided into two streams in the groove, flowing along the two arms of the "V" shape respectively; due to the symmetrical design, the airflow forms a uniform pressure distribution in the groove, avoiding the generation of local high-pressure areas; when the airflow transfers between the grooves, the airflow encounters a symmetrical outlet at the end of the upper herringbone groove 101, and enters the opening of the lower herringbone groove 101 along a symmetrical path, maintaining uniform flow; when entering the lower groove, the airflow still flows along the symmetrical path, and the airflow will not deviate laterally, so excessive pressure accumulation will not form on one side.

[0294] Furthermore, the reduction of the cylinder vibration mark phenomenon is due to the axisymmetric design of the double-layer herringbone groove 101, which mainly balances the airflow pressure and uniform adsorption force. In terms of balancing the airflow pressure, the axisymmetric design of the double-layer herringbone groove 101 allows the airflow to form a uniform symmetrical pressure distribution when flowing on the surface of the radial sealing plate, avoiding the local high-pressure area caused by the asymmetric design; the uniform pressure distribution reduces stress concentration, thereby preventing the formation of vibration marks. In terms of uniform adsorption force, the axisymmetric design of the double-layer herringbone groove 101 allows the airflow to form a uniform negative pressure adsorption force on the surface of the radial sealing plate, ensuring that the radial sealing plate is stably fitted on the rotor surface; the uniform negative pressure adsorption force reduces the relative movement and friction caused by vibration, further preventing the formation of vibration marks. In summary, the axisymmetric design of the double-layer herringbone groove 101 allows the symmetrical airflow path to avoid local high-pressure areas and stress concentration, reducing the formation of cylinder vibration marks; through scientific and reasonable airflow management of the cylinder, the cylinder vibration mark problem is effectively solved and the service life of the engine is extended.

[0295] The double-layer herringbone grooves 101 are evenly distributed along the axial direction.

[0296] The double-layer herringbone grooves 101 are evenly distributed along the axial direction, so that each groove is evenly arranged on the surface of the radial sealing plate, ensuring that the airflow and pressure are evenly distributed on the entire radial sealing plate surface. The evenly distributed groove design enables the radial sealing plate to be evenly stressed during operation, avoiding local stress concentration, thereby reducing the formation of cylinder vibration marks.

[0297] Uniform stress: The evenly distributed groove design enables the radial seal to be evenly stressed during operation, avoiding local stress concentration and thus reducing the formation of cylinder vibration marks.

[0298] In terms of uniform stress distribution, the evenly distributed double-layer herringbone groove 101 structure ensures that the radial sealing plate is evenly stressed during operation, preventing the generation of local high stress areas. This uniform stress reduces stress concentration and reduces the probability of cylinder vibration lines. Due to the uniform stress, the radial sealing plate is balanced during the entire operation process, reducing the possibility of local excessive wear, thereby reducing the vibration line phenomenon on the cylinder surface. Under the design of evenly distributed double-layer herringbone grooves 101, each groove is subjected to similar pressure and stress, and the radial sealing plate is evenly stressed as a whole. The uniform stress distribution reduces the possibility of wavy wear on the cylinder surface, thereby reducing the formation of cylinder vibration lines.

[0299] From the perspective of optimizing airflow path management, the evenly distributed grooves make the airflow path more complex and uniform, so that the airflow will not be concentrated in a specific area to form an impact force. The turning and dispersion of the airflow in the grooves reduces the concentrated impact of the airflow on a specific area, thereby reducing the impact of the airflow on the radial sealing plate; uniform airflow management makes the airflow flow more smoothly in the grooves, reduces the vibration and wear caused by the airflow, and further prevents the formation of cylinder vibration marks.

[0300] Third, the air leakage phenomenon of the cycloid rotor engine

[0301] Double layer herringbone groove 101

[0302] As mentioned above, Figure 5 As shown, due to the geometric design of the double-layer herringbone groove 101, the flow path of the gas in the groove is complex, resulting in different flow velocities and pressure distributions. The airflow is obstructed at the entrance of the groove, forming a high-pressure area; in the middle and outlet of the groove, the airflow velocity increases, forming a low-pressure area. The gas enters the opening area of ​​the double-layer herringbone groove 101 from the high-pressure side, the flow velocity decreases, the pressure increases, and a high-pressure area is formed. As the gas flows along the groove, the airflow in the groove accelerates, the pressure decreases, and a low-pressure area is formed. The pressure difference between the high-pressure area and the low-pressure area generates negative pressure in the low-pressure area. The negative pressure adsorption force of the low-pressure area adsorbs the radial sealing plate on the rotor surface, so that the radial sealing plate is in close contact with the rotor surface, and the double-layer herringbone groove 101 forms an effective pressure differential seal, reducing gas leakage.

[0303] The upper grooves and the lower grooves in the double-layer herringbone grooves 101 are arranged in a staggered manner on the surface of the radial sealing plate. The airflow flows in from the inlet of the upper herringbone groove 101 and the inlet of the lower herringbone groove at the same time, and flows along the two arms of the herringbone groove 101. Each path adjustment and turn will increase the resistance of the airflow, making the overall path of the airflow tortuous and complicated.

[0304] The complex airflow path mainly goes through three links: initial path, flow in upper and lower slots, and path adjustment of slot transfer.

[0305] When the gas flow is in the initial path, the high-pressure gas first enters the opening of the upper herringbone groove 101 .

[0306] When the airflow flows in the upper groove, it experiences channel flow and branch flow. Channel flow is the airflow flowing along a "V"-shaped path in the upper groove; due to the structure of the herringbone groove 101, the airflow needs to constantly turn in the groove, making the flow path tortuous. Branch flow is in the two arms of the herringbone groove 101, the airflow will be divided into two flows, and diffuse outward along the two arms of the herringbone groove 101 respectively.

[0307] When the airflow flows in the lower slot, it experiences a new flow path and staggered arrangement. The new flow path is that the airflow flows along a new "V"-shaped path again, and continues to experience the turning and branching flow similar to that in the upper slot. The staggered arrangement is due to the staggered arrangement of the lower slot and the upper slot. When the airflow enters the lower slot, it needs to undergo complex turning and adjustment, which further complicates the flow path.

[0308] Furthermore, the flow paths of the airflow in the upper herringbone groove 101 and the lower herringbone groove 101 are:

[0309] (1) Air flow inlet: air flow enters from the openings of the upper and lower slots (upper air inlet 201 and upper air outlet 203);

[0310] (2) Airflow path 1: the airflow flows along the two arms of the herringbone groove 101;

[0311] (3) Airflow path 2: In the channel, the airflow flows along the two arms until the end of the channel;

[0312] (4) Airflow converging point: The airflows converge at the ends of the slots (lower air inlet 202 and lower air outlet 204).

[0313] In summary, the design of the double-layer herringbone groove 101 makes the airflow path more complicated by increasing the turning and path adjustment of the airflow in the groove. The airflow undergoes multiple turns and branch flows in the upper herringbone groove 101 and the lower herringbone groove 101, and flows from the entrance of the upper herringbone groove 101 and the lower herringbone groove 101 along the two arms of the herringbone groove 101, and again experiences similar turns and branch flows. Each path adjustment and turn increases the resistance of the airflow, making the overall path of the airflow tortuous and complicated. The staggered double-layer groove design requires the airflow to pass through multiple staggered areas during the path adjustment process, further increasing the complexity of the flow path.

[0314] The sealing weir area 102 prevents leakage between grooves on the radial seal.

[0315] From the gas flow path, the gas will always try to flow from the high-pressure area to the low-pressure area through different paths. Especially on the radial sealing plate, the place with the notch is the path where the gas may escape. The sealing weir area 102 is located between the double-layer herringbone grooves 101 (between the grooves), which is a continuous surface without grooves, forming a groove-free area, ensuring that the sealing weir area 102 does not have any notches or gaps, and the gas cannot escape through the sealing weir area 102. Since the sealing weir area 102 has no notches, when the gas tries to leak through these areas, it will encounter a continuous surface and there is no path to follow. The sealing weir area 102 forms an uninterrupted, continuous plane, and the gas cannot flow through these areas. The sealing weir area 102 utilizes the control of the gas flow path to ensure that the gas can only flow in a specific groove and cannot leak through the groove-free area of ​​the radial sealing plate. Thereby enhancing the overall sealing of the radial sealing plate.

[0316] The sealing dam area 103 prevents leakage at the outer edge of the radial sealing piece

[0317] The sealing dam area 103 is located at the outer edge of the herringbone groove 101 and is a groove-free area on the outer side of the radial sealing piece. Since the sealing dam area 103 is not grooved, it means that there is no notch or interruption on the outer edge of the radial sealing piece, so that the outer edge of the radial sealing piece forms a continuous, complete, and smooth sealing interface, and the gas cannot leak through here. The sealing dam area 103 becomes an additional barrier layer of the radial sealing piece, which is equivalent to adding an additional barrier to the radial sealing piece, so that the gas cannot easily leak or escape through the outer edge of the radial sealing piece. This has an effect on the sealing of the outer edge of the radial sealing piece.

[0318] From the gas flow path, the gas enters the herringbone groove 101 under high pressure, flows along the groove, and may find a path to escape from the outer edge of the radial sealing sheet. Since the sealing dam area 103 is located at the outer edge of the radial sealing sheet and has no grooves, these areas form a natural barrier to effectively block the leakage path of the gas. The grooveless design of the sealing dam area 103 utilizes the control of the gas flow path to ensure that the gas can only flow in a specific groove and cannot leak through the outer edge of the radial sealing sheet. Therefore, the sealing dam area 103 maintains the airtightness of the edge of the radial sealing sheet, prevents the gas from escaping from the outer edge, and thus enhances the edge sealing effect.

[0319] In the design of the double-layer herringbone groove 101, the sealing weir area 102 and the sealing dam area 103 form a combined sealing

[0320] The sealing weir area 102 is located in the groove-free area between the herringbone grooves 101 to prevent gas leakage between the grooves. The sealing dam area 103 is located in the groove-free area at the outer edge of the herringbone groove 101 to prevent gas leakage from the outer edge of the radial sealing sheet.

[0321] Specifically, the sealing weir area 102 and the sealing dam area 103 are not grooved, forming a continuous non-grooved area, which makes the various parts of the radial sealing sheet form a multi-layer protection, and the gas cannot easily find a leakage path. The combined sealing mechanism formed by the sealing weir area 102 and the sealing dam area 103 on the radial sealing sheet can utilize the combination of the non-grooved area and the additional barrier layer to ensure that the gas will encounter the obstruction of the non-grooved area on any possible leakage path, so that it cannot easily leak, and achieve an efficient radial sealing effect.

[0322] In the design of the double-layer herringbone groove 101, the groove-free design of the sealing weir area 102 and the sealing dam area 103 cooperate with each other to form four sealing layers. The details are as follows:

[0323] (1) The first sealing layer: the upper herringbone groove 101;

[0324] (2) Second sealing layer: sealing weir area 102;

[0325] (3) The third sealing layer: the lower herringbone groove 101;

[0326] (4) The fourth sealing layer: sealing dam area 103.

[0327] The openings of the upper herringbone grooves 101 face the high-pressure side, and the high-pressure gas first enters these grooves; the complex flow paths in the grooves increase the resistance of the airflow, forming a preliminary pressure difference effect and negative pressure adsorption force, and starting to seal the gas (preliminary sealing);

[0328] The sealing weir area 102 is located between the upper herringbone grooves 101 and is a continuous surface without grooves. The groove-free area formed by the sealing weir area 102 prevents gas from passing between the grooves, further preventing gas leakage. The sealing weir area 102 forms an intermediate seal, ensuring that even if a small amount of gas leaks in the upper groove, it cannot enter the adjacent groove through the sealing weir area 102, thereby ensuring the airtightness between the grooves.

[0329] The lower herringbone groove 101 is located below or at an interlaced position of the upper groove. After passing through the upper groove, the high-pressure gas enters the lower groove. The lower groove branches out another complex flow path, further increasing the air flow resistance and pressure difference effect, forming a stronger negative pressure adsorption force, further sealing the gas, and forming a deep seal.

[0330] The sealing dam area 103 is located at the outer edge of the double-layer herringbone groove 101 and is a continuous surface without grooves. The groove-free area formed by the sealing dam area 103 serves as the last line of defense and provides an additional barrier layer to prevent gas from escaping from the outer edge of the radial sealing sheet. Even if gas leaks out in the first few layers of sealing, the sealing dam area 103 can prevent the final leakage of the gas, thus achieving edge sealing.

[0331] Multiple sealing layers form a comprehensive sealing system through the cleverly designed double-layer herringbone groove 101, sealing weir area 102 and sealing dam area 103. Each layer increases the resistance of the airflow and the complexity of the flow path, blocking and adsorbing the gas layer by layer, ensuring a high sealing effect.

[0332] Fourth, the wear phenomenon of the cycloid rotor engine

[0333] The present invention uses the selection of preferred materials (silicon carbide or cemented carbide), precise herringbone groove 101 design (including double-layer groove structure, groove depth and groove geometry parameters), and laser processing technology (high precision and smooth surface), so that the double-layer herringbone groove 101 radial sealing piece can significantly reduce wear problems, enhance the sealing effect, and improve the operating stability and service life of the radial sealing piece. The combination of these technical means enables the radial sealing piece to maintain good performance in a high-load, high-friction environment, reduces wear, and extends the service life of the engine.

[0334] The micron-level groove depth and the micro-texture formed by multiple grooves fully utilize the superior characteristics of the micro-texture, effectively optimize the airflow path and pressure distribution, reduce wear, and increase the service life of the radial seal and the overall performance of the cycloid rotor engine.

[0335] Double layer herringbone groove 101

[0336] The geometric parameters of the double-layer herringbone grooves 101 are a groove depth of 1-5 and a number of 2-10 pairs of double-layer herringbone grooves 101 .

[0337] From the groove depth range of the double-layer herringbone groove 101, the groove depth range of 1-5 is a groove depth of micron level, which is sufficient to form a significant pressure difference effect and negative pressure adsorption force, thereby enhancing the sealing effect. The groove depth of micron level makes the pressure distribution more refined and uniform when the airflow flows in the groove, reduces the formation of local high-pressure areas, and reduces the risk of wear caused by stress concentration. The groove depth of micron level can reduce excessive weakening of the material and ensure the structural integrity of the radial sealing sheet under high load conditions. This also enables the radial sealing sheet to maintain good mechanical properties and durability during long-term operation and reduce wear. From the perspective of fine flow channels, the double-layer herringbone groove 101 is a micro-texture, and the groove depth of 1-5μm forms fine flow channels on the surface of the radial sealing sheet. These flow channels can significantly change the flow characteristics of the airflow and enhance the fluid dynamics effect. From the perspective of negative pressure adsorption, the double-layer herringbone groove 101 is a micro-texture formed by a groove depth of 1-5μm, which can generate a stable negative pressure adsorption force when the airflow passes through, so that the radial sealing sheet fits closely with the rotor surface and reduces wear caused by vibration.

[0338] From the number of double-layer herringbone grooves 101, 2-10 pairs of double-layer herringbone grooves 101 allow the airflow to form multiple complex paths on the surface of the radial sealing plate. These micro-texture (2-10 pairs of double-layer herringbone grooves 101) paths optimize the distribution of the airflow, reduce the concentrated impact of the airflow on a single path, enhance the negative pressure adsorption force, ensure that the radial sealing plate stably fits the rotor surface, and reduce the relative movement and wear caused by vibration. Multiple micro-texture levels provide a multi-layer protection mechanism. Even if a certain groove is worn, other grooves can still work effectively, extending the overall service life of the radial sealing plate. At the same time, 2-10 pairs of double-layer herringbone grooves 101 can disturb the airflow, causing the airflow to continuously turn and adjust between different grooves, increasing the flow resistance and pressure changes, and further enhancing the sealing effect. Multiple grooves make the stress distribution on the surface of the radial sealing plate more uniform, avoiding the stress concentration problem that is prone to occur in a single groove design, and reducing local wear. Therefore, 2-10 pairs of double-layer herringbone grooves 101 form multiple fine flow channels on the surface of the radial sealing plate, and these flow channels work together to optimize the airflow path and improve the fluid dynamics performance.

[0339] From the perspective of pressure distribution, the double-layer herringbone groove 101 will cause the airflow in the groove to generate a pressure difference, and the low-pressure area will form a negative pressure, which will adsorb the radial sealing sheet and the rotor surface. The micro-texture of the double-layer herringbone groove 101 can guide the airflow, causing the airflow to form different pressure distributions in the groove, and the low-pressure area will generate negative pressure, which will adsorb the radial sealing sheet and the rotor surface. The generated negative pressure adsorption force makes the radial sealing sheet and the rotor surface fit stably, reducing the friction and wear caused by vibration.

[0340] From the perspective of negative pressure adsorption, the micro-texture of the double-layer herringbone groove 101 causes the airflow to encounter more resistance and deflection when flowing in the groove, forming local high-pressure and low-pressure areas, and enhancing the negative pressure effect. The negative pressure adsorption force makes the radial sealing sheet fit tightly with the rotor surface, reducing the relative movement caused by vibration. The tight fit reduces the relative movement between the radial sealing sheet and the rotor surface, reducing the wear rate.

[0341] Sealed weir area 102

[0342] As part of the micro-texture, the sealing weir area 102 significantly reduces the impact of the airflow on the radial sealing sheet through its grooveless and smooth design. The sealing weir area 102 remains smooth and continuous at the micron level without the interference of the groove. The sealing weir area 102 is located between the herringbone grooves 101 and is a grooveless and continuous surface, which provides an additional layer of barrier and reduces the impact of the airflow on the radial sealing sheet. The sealing weir area 102 is also a micro-texture, and its smooth surface reduces the impact of the airflow on the radial sealing sheet, avoids the high-pressure airflow from concentrating on certain points, and reduces local wear. The sealing weir area 102 acts as an additional layer of barrier to reduce the impact of the airflow on the radial sealing sheet. The grooveless sealing weir area 102 reduces the number of times the airflow directly impacts the surface of the radial sealing sheet, reducing the wear caused by the high-pressure airflow; at the same time, the grooveless sealing weir area 102 ensures the uniform distribution of the airflow, reducing stress concentration and local wear.

[0343] Sealed Dam Area 103

[0344] As a part of the micro-texture, the sealing dam area 103 significantly reduces the impact of the airflow on the outer edge of the radial sealing piece through its grooveless smooth design. The sealing dam area 103 is located at the outer edge of the herringbone groove 101 and is a grooveless area. It is optimized at the micron level to form a grooveless micro-textured outer area to ensure the airtightness of the outer edge. The grooveless design of the sealing dam area 103 forms a smooth surface, which reduces the direct impact of the airflow on the radial sealing piece. By reducing the direct impact of the airflow, the sealing dam area 103 effectively protects the outer edge of the radial sealing piece and reduces wear. The micro-texture design of the sealing dam area 103 ensures the airtightness of the outer edge and prevents the airflow from escaping from the outer side of the radial sealing piece. By preventing the airflow from escaping, the sealing dam area 103 enhances the overall sealing effect of the radial sealing piece and ensures the stability of the pressure in the cylinder. The sealing dam area 103 can reduce the concentration of high-pressure airflow, so that the airflow is dispersed when passing through the radial sealing piece, avoiding the concentration of high-pressure airflow at certain points, thereby reducing local wear. The airflow flows evenly on the smooth surface of the sealing dam area 103, reducing the number of times the airflow directly impacts the outer edge of the radial sealing piece, and reducing the wear caused by the high-pressure airflow. The grooveless sealing dam area 103 evenly distributes the airflow, reduces stress concentration, avoids excessive wear in local areas, ensures the uniformity of stress distribution on the outer edge of the radial sealing piece, and thus enhances the durability of the radial sealing piece.

[0345] The surface micro-texture of the radial seal is made of high hardness materials (silicon carbide and cemented carbide)

[0346] The micro-texture on the surface of the radial sealing plate of the cycloidal rotor engine described in the present invention selects high-hardness materials (silicon carbide and cemented carbide). Silicon carbide has extremely high hardness and wear resistance, is not easy to deform, and can effectively reduce wear when in contact with the rotor. Cemented carbide is composed of high-hardness metal carbides and metal binders, has high wear resistance and toughness, and is suitable for use in high-friction environments. Silicon carbide and cemented carbide can withstand greater loads during operation, reducing the friction and wear between the top arc of the radial sealing plate and the rotor surface, thereby extending the service life of the radial sealing plate and reducing the replacement frequency.

[0347] Laser processing technology is used in the processing technology of materials (silicon carbide and cemented carbide). Laser processing technology can accurately control the shape and size of the double-layer herringbone groove 101 to ensure the uniformity and accuracy of each groove. In turn, the surface of the radial sealing plate is more uniform, reducing local stress concentration and wear caused by surface unevenness. The smooth surface produced by laser processing technology can reduce the friction coefficient between the radial sealing plate and the rotor, which not only reduces the initial wear, but also improves the durability of the radial sealing plate in long-term operation.

[0348] The properties of high-hardness materials (silicon carbide and cemented carbide) can ensure the operation of the radial seal of the cycloid rotor engine. In the initial operation stage, the high-hardness and high-wear-resistant materials reduce the wear between the radial seal and the rotor surface. The design of the herringbone groove 101 allows the airflow to form a pressure difference in the groove, and the negative pressure adsorption force makes the radial seal fit tightly against the rotor surface, reducing friction and wear. In the long-term operation stage, the synergistic effect of the high-hardness material and the herringbone groove 101 design enables the radial seal to maintain stable performance in long-term operation and reduces wear caused by friction and vibration. The high precision and smooth surface of laser processing further reduce wear and increase the service life of the radial seal.

[0349] By applying micro-texture design, the double-layer herringbone groove 101 of the present invention shows significant advantages in controlling the airflow path of the radial sealing plate, optimizing pressure distribution and reducing friction and wear. The micro-texture not only effectively reduces the friction coefficient and wear rate, but also enhances the fit stability between the radial sealing plate and the rotor surface, prolongs the service life of the radial sealing plate, and improves the overall performance and reliability of the cycloid rotor engine. The technical solution described in the present invention fully utilizes the synergistic effect of materials and structures through fine design at the micron level, and can solve the problem of radial sealing plate wear in the long term.

[0350] In summary, the present invention can solve the problems of vibration, air leakage, wear and cylinder vibration by designing a reasonable sealing structure (such as a double-layer herringbone groove 101 structure, an axisymmetric design, a uniformly distributed groove structure, a groove-free sealing weir area 102 and a sealing dam area 103, etc.). Furthermore, the micro-texture on the radial sealing sheet of the present invention can effectively mitigate the occurrence of eccentric failure in the radial seal of the cycloid rotor engine, ensure uniform contact between the radial sealing sheet and the rotor surface, thereby improving the sealing effect and the durability of the radial sealing sheet.

Claims

1. A cycloid rotor engine radial sealing plate surface micro-texture, the rotor engine comprising a rotor (4) and a stator, the stator comprising three arc-shaped side walls, characterized in that: The surface of the radial sealing sheet (1) is provided with a plurality of herringbone grooves (101), a sealing weir area (102) and a sealing dam area (103), and a rotor (4) is provided on the opposite side of the radial sealing sheet (1); The herringbone grooves (101) are opened in the middle area of ​​the radial sealing sheet (1) and are evenly arranged in the circumferential direction and the longitudinal direction. Each herringbone groove (101) has an upper air inlet (201) and a lower air inlet (202) as a gas inlet, and then flows into the groove channel, reaching a maximum pressure in the groove channel of the herringbone groove (101). Correspondingly, the gas is discharged from the upper air outlet (203) and the lower air outlet (204), achieving exhaust from the high-pressure area on the right to the low-pressure area on the left, so as to achieve effective sealing when the radial sealing sheet (1) contacts the rotor and optimize the gas flow path; The sealing weir area (102) is arranged in the middle part between two adjacent herringbone grooves (101), and is evenly distributed along the axial direction of the radial sealing sheet (1), forming a complementary structure with the double-layer herringbone grooves (101) to achieve primary blocking and airflow control; The sealing dam area (103) is provided at the outer edge of the radial sealing sheet (1), arranged along the rotation direction of the rotor (4), and has no physical separation with the double-layer herringbone groove (101), thus forming a continuous seamless connection and achieving a smooth transition of the airflow.

2. The surface micro-texture of the radial sealing plate of a cycloidal rotor engine according to claim 1, characterized in that: The double-layer herringbone grooves (101) are distributed on the surface of the radial sealing sheet (1) and are divided into two layers of grooves, with the upper layer of herringbone grooves (101) being on the outside and the lower layer of herringbone grooves (101) being on the inside; The upper layer of the herringbone grooves (101) and the lower layer of the herringbone grooves (101) can be arranged in a staggered manner to maintain the continuity of the gas flow path; The upper layer of the herringbone groove (101) and the lower layer of the herringbone groove (101) of the double-layer herringbone groove (101) maintain an equal vertical distance to ensure that each layer of the herringbone groove (101) is relatively independent, so that gas can flow freely between the layers; The double-layer herringbone groove (101) structure is symmetrically distributed along the symmetry center line (104) of the radial sealing sheet (1) to form an axisymmetric structure, so that when the radial sealing sheet (1) contacts the surface of the rotor (4), the airflow flows evenly in all directions, forming a uniform negative pressure and adsorption force; The airflow in the double-layer herringbone groove (101) enters the groove from the upper air inlet (201) and the lower air inlet (202) at the same time, and the gas flow pattern in the groove changes dramatically, and then the gas is discharged from the upper air outlet (203) and the lower air outlet (204) and flows out; The double-layer herringbone groove (101) forms a high-pressure area and a low-pressure area in the groove due to the negative pressure effect; the high-pressure area is mainly located at the upper air inlet (201) and the lower air inlet (202), and the middle position of part of the groove; the low-pressure area is mainly located at the middle of the groove and the upper air outlet (203) and the lower air outlet (204) in the outlet area.

3. The surface micro-texture of the radial sealing plate of a cycloidal rotor engine according to claim 2, characterized in that: The herringbone grooves (101) of each layer are arranged in parallel with each other, maintaining a fixed interval and parallel relationship, and extending from the edge of the radial sealing sheet (1) to the center to form a plurality of independent flow channels; the high-pressure gas first enters the herringbone grooves (101) of the upper layer, and then enters the herringbone grooves (101) of the lower layer after passing through the upper layer channels, thereby increasing the airflow resistance and the pressure difference effect.

4. The surface micro-texture of the radial sealing plate of a cycloidal rotor engine according to claim 2 or 3, characterized in that: Each of the herringbone grooves (101) is evenly arranged on the surface of the radial sealing sheet (1), maintaining an equal spacing and an equidistant parallel relationship with respect to other herringbone grooves (101), and extending from the edge to the center of the radial sealing sheet (1); Each herringbone groove (101) is composed of two symmetrical herringbone structures, which are divided into an upper herringbone groove (101) and a lower herringbone groove (101), ensuring that the flow path of the gas in the groove is balanced. The symmetrical structure can be kept consistent in the upper herringbone groove (101) and the lower herringbone groove (101), forming a uniform pressure gradient; the opening direction of each herringbone groove (101) is consistent with the rotation direction of the rotor (4), ensuring that the high-pressure gas can smoothly enter the upper air inlet (201) and the lower air inlet (202).

5. The surface micro-texture of the radial sealing plate of a cycloidal rotor engine according to claim 2, characterized in that: The herringbone groove (101) spacing area is located in the spacing part between the herringbone grooves (101), forming a plurality of parallel or staggered herringbone grooves (101), each groove dividing the contact surface into a plurality of parts; the herringbone groove (101) spacing area divides the contact area between the radial sealing plate (1) and the rotor (4) into a plurality of smaller areas, thereby reducing friction and increasing the sealing effect through the pressure change of the gas in the groove; the herringbone groove (101) spacing area is an uncut solid part, located between the grooves of the five parallel herringbone grooves (101) on the radial sealing plate (1), and is a contact area part that can actually contact the rotor (4); the herringbone groove (101) spacing area is also a tiny contact area formed near the edge of the groove, and is a contact area part at a high pressure area near the edge of the groove.

6. The surface micro-texture of the radial sealing plate of a cycloidal rotor engine according to claim 1, characterized in that: The sealing weir area (102) forms a plurality of continuous non-groove areas, which are located in the middle part between two adjacent herringbone grooves (101), are evenly distributed along the axial direction of the radial sealing sheet (1), and are directly connected to the adjacent herringbone grooves (101) to form a smooth and continuous surface; the sealing weir area (102) divides the herringbone grooves (101) into a plurality of pairs to form a plurality of independent sealing units, each of which can generate an effective pressure difference and negative pressure effect, and can further transmit the pressure difference and negative pressure effect generated by the herringbone groove (101) to the adjacent herringbone groove (101) and the sealing weir area (103); The sealing dam area (103) forms a plurality of continuous non-grooved areas, which are located at the outer edge of the herringbone groove (101) and distributed along the rotation direction of the rotor (4), forming a continuous, complete and smooth sealing interface; the sealing dam area (103) forms a continuous and complementary structure with the herringbone groove (101) through its non-grooved area, without any physical separation, and directly forms a continuous seamless connection, so that the airflow can smoothly transition from the herringbone groove (101) to the sealing dam area (103), thereby preventing the gas from escaping from the outer side of the radial sealing sheet (1); the sealing dam area (103) transmits the pressure difference and negative pressure effect generated by the herringbone groove (101) and the sealing dam area (102) to the outer edge area of ​​the radial sealing sheet (1); The sealing weir area (102) and the sealing dam area (103) cooperate with each other during the movement of the airflow, so that various parts of the radial sealing sheet (1) form a multi-layer protection, and the gas cannot easily find a leakage path; the sealing weir area (102) provides primary blocking, and the sealing dam area (103) provides secondary protection. The sealing weir area (102) and the sealing dam area (103) together form a combined sealing mechanism on the radial sealing sheet (1).

7. The surface micro-texture of the radial sealing plate of a cycloidal rotor engine according to claim 1 or 7, characterized in that: The double-layer herringbone groove (101), the sealing weir area (102) and the sealing dam area (103) cooperate to form a multi-layer sealing system, with a total of four sealing layers, as follows: (1) First sealing layer (preliminary sealing): upper herringbone groove (101); (2) Second sealing layer (middle sealing): sealing weir area (102); (3) The third sealing layer (deep sealing): lower herringbone groove (101); (4) Fourth sealing layer (edge ​​sealing): sealing dam area (103); The preliminary sealing is achieved by separating the sealing weir area (102) between each upper herringbone groove (101), so that the gas flow cannot leak between the grooves; wherein the opening of the upper herringbone groove (101) faces the high-pressure gas side and can directly receive the high-pressure gas; The intermediate seal is formed by a sealing weir area (102), which is located between the upper herringbone grooves (101) and is a continuous surface without grooves. The groove-free area formed by the sealing weir area (102) prevents gas from passing between grooves, so that even if a small amount of gas leaks in the upper groove, it cannot enter the adjacent groove through the sealing weir area (102), thereby achieving airtightness between the grooves. The deep sealing is achieved by the lower herringbone groove (101) being located below or at an interlaced position of the upper groove, and the high-pressure gas passes through the upper groove and the lower groove at the same time, thereby increasing the airflow resistance and the pressure difference effect, and forming a stronger negative pressure adsorption force; The edge seal is that the sealing dam area (103) is located at the outer edge of the double-layer herringbone groove (101) to form a continuous surface without grooves; the groove-free area formed by the sealing dam area (103) serves as the last line of defense, providing an additional barrier layer to prevent gas from escaping from the outer edge of the radial sealing sheet (1); so that even if gas leaks out during the first three layers of sealing, the sealing dam area (103) can prevent the final leakage of the gas.

8. The surface micro-texture of the radial sealing plate of a cycloidal rotor engine according to claim 1, characterized in that: The symmetry center line (104) is the central axis that runs through the radial sealing sheet (1) and is located in the middle of the radial sealing sheet (1), forming a symmetrical layout; the symmetry center line (104) serves as an alignment point for the herringbone grooves (101), ensuring that the opening directions of all the grooves are consistent with the rotation direction of the rotor (4); The openings (201) are the upper air inlet (201) and the lower air inlet (202) for high-pressure gas to enter the herringbone groove (101), and can guide the airflow to enter the herringbone groove (101) and flow along the airflow path, thereby generating a pressure difference and negative pressure adsorption effect.

9. The surface micro-texture of the radial sealing plate of a cycloidal rotor engine according to claims 1 and 2, characterized in that: The double-layer herringbone grooves (101) have a groove depth of 1-5 μm, forming fine flow channels on the surface of the radial sealing sheet (1); the number of the double-layer herringbone grooves (101) is 2-10 pairs, so that the airflow is continuously turned between the multiple grooves; The geometric shape of the double-layer herringbone groove (101) is a herringbone shape, and the edge line type of the structure is one or more of a straight line, an arc line, a spiral line, and a sawtooth line; The spiral double-layer herringbone groove (101) is in a rotating curve, and the edge of the spiral line guides the airflow to flow along the spiral path, making the flow path more complex, thereby enhancing the pressure difference effect and the viscosity effect; The sawtooth linear double-layer herringbone groove (101) has multiple peaks and valleys, and can generate a stronger turbulence effect, enhance gas mixing and pressure difference effect, enhance the shear force of the airflow, and enhance the adsorption force between the radial sealing sheet and the rotor surface.

10. The surface micro-texture of the radial sealing plate of a cycloidal rotor engine according to claims 1-9, characterized in that: The material of the radial sealing sheet (1) is silicon carbide material or hard alloy (Ni-Cr-Co alloy, Co-Cr-W alloy, Ti-Al-V alloy and Al-Cu-Mg-Si alloy).

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