Micro-textured surface of radial sealing element for cycloid rotor engine

Abstract

Disclosed in the present invention is a micro-textured surface of a radial sealing element for a cycloid rotor engine, comprising double-layer herringbone grooves, a sealing weir zone, and a sealing dam zone. Providing double-layer herringbone grooves on a surface in contact with a rotor allows for gas to enter the herringbone grooves from an upper-layer inlet and a lower-layer inlet at a top corner thereof, reaching a maximum pressure value within the grooves, and after a pressure differential has acted on the gas, the gas is discharged from an upper-layer outlet and a lower-layer outlet. A plurality of pairs of herringbone grooves are evenly distributed on the radial sealing element, the sealing weir zone is provided between two adjacent pairs of herringbone grooves in an axial direction, and the sealing dam zone is provided on an outer side of the radial sealing element. The herringbone grooves are of an axisymmetric structure, having a depth of 1-5 microns, a count of the grooves being 2-10 pairs, and an edge thereof being a straight line, an arc, a spiral, or a serrated line. The gas, by means of the pressure differential, causes the radial sealing element to tightly adhere to the rotor, and the sealing weir zone and the sealing dam zone provide multi-layer sealing protection. The present invention addresses gas-tightness issues in radial sealing elements, achieves stable sealing performance in radial sealing elements for cycloid rotor engines, and significantly reduces gas leakage.

Description

Microtexture on the surface of a radial seal of a cycloidal rotor engine Technical Field

[0001] This invention belongs to the field of radial sealing for engines, specifically relating to a microtexture on the surface of a radial sealing sheet for a cycloidal rotor engine. Background Technology

[0002] Both cycloidal rotor engines and reciprocating piston engines rely on the expansion pressure generated by fuel combustion to obtain power. Unlike reciprocating piston engines, the rotor of a cycloidal rotor engine rotates in one direction, meaning it continuously rotates along a fixed path within the engine casing. The rotor rotates around an eccentric shaft, and the rotational motion of the eccentric shaft is directly transmitted to the external output torque through the rotor. Because the rotor is directly connected to the eccentric shaft, the connecting rod and crankshaft structures are eliminated. This allows the rotor's power to be transmitted to the eccentric shaft more directly and efficiently, thus outputting mechanical power. Furthermore, the radial seal becomes a core component ensuring the efficient operation of the cycloidal rotor engine. The design and quality of the materials used in the radial seal directly affect the durability, reliability, power output, and environmental performance of the cycloidal rotor engine.

[0003] Current cycloidal rotor engines primarily rely on direct sealing, i.e., the contact between the radial sealing plate and the rotor, to achieve a seal. Through the rotor's rotation and the fixed position of the radial sealing plate, the plate remains in constant contact with the rotor. The principle of direct sealing is to seal the gas through direct contact between the radial sealing plate and the rotor during engine operation, preventing gas flow between different cylinders and thus ensuring the combustion performance of the cycloidal rotor engine. The radial sealing plate at the rotor apex directly contacts the inner wall of the engine casing to form a seal, without any additional isolation layer or structure.

[0004] Direct sealing faces several challenges and drawbacks. First, the direct contact between the radial seal and the inner wall of the housing generates friction, leading to wear on both. Over time, this wear degrades the sealing system's performance, increases the risk of leakage, and consequently affects the engine's combustion efficiency and performance. Second, during the operation of a cycloidal rotor engine, temperature changes cause thermal expansion and deformation of the materials. The gap between the radial seal and the inner wall of the housing varies with temperature; an excessively large gap leads to leakage, while an insufficient gap increases friction and wear. Third, uneven thermal expansion can cause stress concentration, increasing the risk of damage to the radial seal. Uneven expansion of the radial seal can cause structural deformation of the entire sealing system, affecting the engine's overall performance and lifespan. Fourth, prolonged high-temperature operation and temperature cycling can lead to thermal fatigue of the radial seal material. Under high temperatures and thermal cycling, the radial seal is prone to failure, resulting in decreased sealing performance and impacting engine efficiency and emissions. Fifth, the rapid expansion and explosion of high-temperature, high-pressure gases generated during fuel combustion causes periodic high-pressure impacts on the radial seal, leading to deformation, displacement, or wear, thus affecting the sealing effect.

[0005] In practical applications, the operation of cycloidal rotor engines can lead to unstable sealing. Excessive rotational speed can cause seal failure. Furthermore, the sealing performance of this method is related to the surface morphology of the sealing element; different surface morphologies can result in significant differences in sealing effectiveness. Simultaneously, the unstable rotation of the rotor makes the contact between the rotor and the sealing element unstable, increasing wear and leading to poor sealing or even failure. The root cause of these problems lies in the radial seals of the cycloidal rotor engine exhibiting vibration, leakage, wear, and cylinder block grooves.

[0006] Specifically, the vibration of the radial sealing strip refers to the pulsating movement of the radial sealing strip on the cylinder profile, known as the sealing strip vibration phenomenon. This vibration phenomenon causes air leakage at the sealing strip and cylinder block vibration marks, while also accelerating the wear of the sealing strip, thus reducing the engine's power and lifespan. Specifically, cylinder block vibration marks are wavy wear phenomena appearing on the cylinder block profile. Due to the poor durability of the radial sealing strip and the cylinder profile, vibration marks often appear in the combustion area of ​​the cylinder profile, as shown in Figure 4. Cylinder block vibration marks are extremely harmful, damaging the engine's seals, accelerating the wear and even breakage of the sealing strip, and severely impacting the performance and lifespan of the rotary engine. Specifically, air leakage at the sealing point of the radial sealing strip of the rotary engine is the main reason for the performance difference between rotary and reciprocating engines. Air leakage becomes more pronounced when the engine speed decreases, reducing maximum torque and increasing specific fuel consumption. The gas leakage paths within the rotary engine cylinder are shown in Figure 5: one is leakage to the adjacent working chamber via the radial sealing strip, and the other is leakage from the end face via the end face gas seal. The former accounts for approximately 2 / 3 to 3 / 4 of the total leakage, while leakage towards the end face is relatively small. Specifically, radial seal wear occurs after the rotor has been running for a period of time, resulting in wear on the top arc of the radial seal. This wear affects the cylinder geometry accuracy, sealing performance, and engine lifespan of the rotor.

[0007] Chinese patent (CN106401786A) discloses a sealing device for a miniature rotary engine. By improving the design of the sealing sheet and spring plate, it enhances sealing performance and reduces leakage. However, challenges remain regarding manufacturing and assembly complexity, spring plate durability, wear, thermal expansion, and dynamic response performance. Specifically, the sealing sheet and spring plate come into contact with the rotor and cylinder during operation, leading to frictional wear. Although the design reduces the leakage area, frictional wear can shorten the lifespan of the sealing sheet and spring plate, affecting the sealing effect. Especially under high temperature and high pressure operating environments, the wear resistance and fatigue resistance of the materials pose a challenge. Specifically, although the sealing sheet design reduces the leakage area, a certain risk of leakage still exists. In actual operation, the sealing effect of the bottom of the sealing sheet and the spring plate can be affected by various factors, such as manufacturing tolerances, assembly errors, and changes in operating conditions. Specifically, the high temperatures generated during the operation of the rotary engine can cause thermal stress in the sealing sheet and spring plate due to thermal expansion, potentially leading to seal failure or component damage. In particular, the different coefficients of thermal expansion of different materials can lead to relative movement and stress concentration between mating components. Specifically, the sealing plate 2 and the spring plate generate high-frequency vibration and impact when the rotor engine is running at high speed. The sealing effect under dynamic conditions is different from that under static design, and the dynamic characteristics of the spring plate 5 need to be optimized.

[0008] Chinese utility model patent (CN220416239U) proposes a dry gas sealing structure with an imitation F-shaped dynamic pressure groove, attempting to improve sealing performance. However, it still faces certain challenges and potential defects in thermal management and dynamic pressure opening effect. Specifically, although the design considers the distribution of dynamic pressure grooves and microtexture to reduce temperature, friction between the rotating and stationary rings and gas compression still lead to excessively high end-face temperatures during actual operation. This can easily affect the performance and lifespan of the sealing material during prolonged engine operation. Furthermore, although the design improves the dynamic pressure opening effect through the imitation F-shaped dynamic pressure groove, the dynamic pressure effect may still be insufficient to completely prevent leakage during the initial start-up phase, especially at low speeds or when the engine is stationary. The dynamic pressure effect is highly dependent on rotational speed; at lower speeds, the sealing effect is not ideal.

[0009] It is evident that current technologies address curved surface leakage of radial seals by relying on the contact between the rotor and the radial seal. This approach generally results in low sealing efficiency, high frictional losses, and difficulty in achieving better leak prevention. Summary of the Invention

[0010] The actual operating conditions of cycloidal rotor engines and the shortcomings of existing technologies reveal that the main obstacle in their development currently lies in the radial sealing strip. This necessitates improvements in sealing structure design and material selection to enhance sealing effectiveness and durability, thereby extending the service life of the cycloidal rotor engine and improving its performance.

[0011] To address the aforementioned technical problems, this invention aims to provide a microtexture on the surface of the radial sealing sheet of a cycloidal rotor engine. The specific technical solution adopted is as follows:

[0012] The present invention discloses a radial sealing sheet surface microtexture for a cycloidal rotor engine, namely a novel slotted radial sealing sheet for a cycloidal rotor engine. The radial sealing sheet has a double-layer herringbone groove 101 on the contact surface with the rotor. The double-layer herringbone groove 101 includes several pairs, each pair of herringbone grooves 101 has the same groove depth, and each pair of herringbone grooves 101 is provided with a grooveless sealing weir area 102. A sealing dam area 103 is provided along the rotor rotation direction.

[0013] The present invention has a double-layer herringbone groove 101 on the surface in contact with the rotor. The herringbone groove 101 of the radial sealing sheet enters through the upper air inlet 201 and the lower air inlet 202 on the high-pressure air inlet side. The pressure reaches the maximum value 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, realizing the exhaust from the high-pressure area on the right to the low-pressure area on the left.

[0014] After the gas flows into the tank, the pressure difference at different locations creates a negative pressure, which in turn generates an adsorption force that causes the radial sealing plate and the rotor to adhere together, thus achieving the purpose of sealing.

[0015] The herringbone grooves 101 are evenly arranged in the circumferential and length directions in the middle area of ​​the radial sealing plate 1. Each herringbone groove 101 has an upper air inlet 201 and a lower air inlet 202 as the gas inlet, and then the gas flows into the groove. The pressure reaches the maximum value 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, realizing the 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 plate 1 contacts the rotor 4 and optimize the gas flow path.

[0016] The sealing weir area 102 is located 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 herringbone grooves 101 to achieve primary blocking and airflow control.

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

[0018] The double-layer herringbone grooves 101 are distributed on the surface of the radial sealing plate 1, consisting of two layers of herringbone grooves 101, with the upper herringbone groove 101 on the outer side and the lower herringbone groove 101 on the inner side. The upper and lower herringbone grooves 101 can be staggered to maintain the continuity of the gas flow path. The upper and lower herringbone grooves 101 maintain equal vertical distances to ensure that each layer of herringbone grooves 101 is relatively independent, allowing gas to flow freely between layers. The double-layer herringbone groove structure is symmetrically distributed along the symmetrical center line 104 of the radial sealing plate 1, forming an axisymmetric structure, which makes the radial sealing... When plate 1 contacts the surface of rotor 4, the airflow flows uniformly 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. The gas flow pattern changes drastically in the groove, and then the gas is discharged from the upper air outlet 203 and the lower air outlet 204. Due to the negative pressure effect, the double-layer herringbone groove 101 forms a high-pressure zone and a low-pressure zone in the groove. The high-pressure zone is mainly located in the upper air inlet 201 and the lower air inlet 202, as well as in the middle of part of the groove. The low-pressure zone is mainly located in the middle of the groove and the outlet area of ​​the upper air outlet 203 and the lower air outlet 204.

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

[0020] Each herringbone groove 101 is evenly arranged on the surface of the radial sealing plate 1, maintaining equal spacing and parallelism relative to other grooves, extending from the edge of the radial sealing plate 1 towards the center; each herringbone groove 101 consists of two symmetrical herringbone structures, divided into an upper herringbone groove 101 and a lower herringbone groove 101, ensuring a balanced gas flow path within the groove. The symmetrical structure maintains consistency in both the upper and lower herringbone grooves 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 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 interval between the herringbone grooves 101, forming multiple parallel or staggered herringbone grooves 101, each groove dividing 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 multiple smaller areas, reducing friction and increasing the sealing effect through pressure changes of the gas inside 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 the contact area that can actually contact the rotor 4; the herringbone groove 101 spacing area is also a small contact area formed near the edge of the groove, and is the contact area at the high-pressure area near the edge of the groove; the contact area of ​​the spacing area is located at the five parallel herringbone grooves 101 on the radial sealing plate 1, and the interval area between the grooves is the part that actually contacts the rotor 4; the specific location of the contact area is as follows:

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

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

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

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

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

[0027] The microtexture on the surface of the radial sealing sheet of the cycloidal rotor engine is characterized in that the airflow path of the upper herringbone groove 101 is as follows:

[0028] S1. Airflow inlet: The airflow enters through 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 two arms of the upper herringbone groove 101 and the lower herringbone groove 101;

[0030] S3. Airflow path 2: Gas flows into the channel, where the flow pattern changes drastically, creating negative pressure adsorption until the end of the channel;

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

[0032] The specific airflow path of the lower herringbone-shaped 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 opening of the lower herringbone groove 101, the lower air inlet 202, 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 channel 101.

[0036] Specifically, the sealing weir area 102 forms multiple continuous grooveless regions located in the middle portion between two adjacent herringbone grooves 101, uniformly distributed along the axial direction of the radial sealing sheet 1, and directly connected to the adjacent herringbone grooves 101, forming a smooth and continuous surface; the sealing weir area 102 divides the herringbone grooves 101 into several pairs, forming multiple independent sealing units, each of which can generate effective pressure difference and negative pressure effects, thereby transmitting the pressure difference and negative pressure effects generated by the herringbone grooves 101 to the adjacent herringbone grooves 101 and the sealing dam area 103; the sealing dam area 103 forms multiple continuous grooveless regions located at the outer edge of the herringbone grooves 101, distributed along the rotation direction of the rotor 4, forming a continuous, complete, and smooth sealing interface; the sealing dam area 103, through its The grooveless area forms a continuous and complementary structure with the herringbone groove 101, without any physical separation, directly forming a continuous and seamless connection. This allows the airflow to smoothly transition from the herringbone groove 101 to the sealing dam area 103, preventing gas from escaping from the outside of the radial sealing plate 1. 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 1. The sealing weir area 102 and the sealing dam area 103 cooperate with each other in the airflow movement, so that each part of the radial sealing plate 1 forms a multi-layer protection, making it difficult for gas to 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 plate 1.

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

[0038] (1) First sealing layer (preliminary sealing): upper herringbone groove 101;

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

[0040] (3) Third sealing layer (deep seal): lower herringbone groove 101;

[0041] (4) Fourth sealing layer (edge ​​seal): seal dam area 103.

[0042] The initial sealing is achieved by separating the sealing weir area 102 between each upper herringbone groove 101, so that the airflow 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 intermediate seal is formed by the sealing weir area 102, which is located between the upper herringbone grooves 101 and is a grooveless continuous surface. The grooveless area formed by the sealing weir area 102 prevents gas from passing between the grooves, so that even if a small amount of gas leaks in the upper channel, it cannot enter the adjacent channel through the sealing weir area 102, thus achieving airtightness between the channels.

[0044] The deep sealing is achieved by the lower herringbone groove 101 being located below or staggered with the upper groove, and high-pressure gas passing through both the upper and lower grooves simultaneously, which increases airflow resistance and pressure difference effect, forming a stronger negative pressure adsorption force.

[0045] The edge seal is a sealing dam 103 located at the outer edge of the double herringbone groove 101, forming a groove-free continuous surface; the groove-free area formed by the sealing dam 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 piece 1; so that even if gas leaks out in the first three layers of seal, the sealing dam 103 can prevent the final leakage of gas.

[0046] Specifically, the symmetrical center line 104 is the central axis passing through the radial sealing plate 1, located in the middle of the radial sealing plate 1, forming a symmetrical layout; the symmetrical center line 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 upper air inlet 201 and the lower air inlet 202 for high-pressure gas to enter the herringbone groove 101, which can guide the airflow into the herringbone groove 101, flow along the airflow path, and generate pressure difference and negative pressure adsorption effect.

[0047] The groove depth of the herringbone groove 101 is 1-5 cm; the herringbone groove 101 has 2-10 pairs.

[0048] Furthermore, the edge profile of the herringbone groove 101 structure can be one or more of the following: straight line, arc, spiral, or sawtooth.

[0049] Preferably, the radial sealing sheet is made of silicon carbide or hard alloy (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 laser-processed.

[0051] The objectives of this invention and the technical problems it addresses can be further achieved by the following technical measures.

[0052] Please refer to Figures 1-3. In a sealing structure with herringbone grooves 101 on the curved surface of the radial sealing plate of the engine, gas enters through the grooves of the herringbone grooves and one side opening 201 of the radial sealing plate, and reaches the maximum pressure value at the corner 202 of the herringbone grooves. Several 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 pairs of axially adjacent herringbone grooves 101 is the sealing weir area 102, and the non-grooved area outside the herringbone grooves 101 is the sealing dam area 103.

[0053] In this invention, the herringbone groove 101 is an axisymmetric shape, 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 this invention, gas enters the groove through the slot 201, and a negative pressure is generated by the pressure difference at each point in the radial sealing plate's curved herringbone groove 101, thereby causing the radial sealing plate 1 and the rotor 4 to adhere together.

[0055] The working principle of the radial sealing plate surface microtexture of the cycloidal rotor engine described in this invention:

[0056] The working principle of this invention is based on the design of a double-layer herringbone groove 101 and a micro-textured surface. The sealing effect is optimized by controlling the groove depth, number, and edge profile, as well as selecting high-hardness materials. The pressure difference and negative pressure generated when gas flows within the grooves create an adsorption force, ensuring a tight fit between the radial sealing sheet and the rotor, thus achieving an effective seal. The application of laser processing technology ensures the precise manufacturing of the micro-textured structure, improving the performance and service life of the radial sealing sheet. Furthermore, this invention, by designing a double-layer herringbone groove 101 structure on the surface of the radial sealing sheet, utilizes the principle of gas lubrication and the pressure changes of the groove structure to provide a highly efficient, stable, vibration-resistant, and low-wear radial sealing solution.

[0057] The herringbone groove 101 structure design on the radial sealing plate surface is the core of this invention. This invention designs a double-layer herringbone groove 101 on the surface of the radial sealing plate that contacts the rotor. The double-layer herringbone groove 101 refers to a groove of a specific shape opened on the radial sealing plate. Its main function is to generate pressure difference and negative pressure through gas flow within the groove, thereby achieving a sealing effect. Specifically, the groove depth of each pair of herringbone grooves 101 is between 1 and 5 mm, and the number is 2 to 10 pairs. This design allows for precise control of gas flow within the groove and optimizes the generation of pressure difference.

[0058] Specifically, the edge profile of the herringbone groove 101 can be one or more combinations of straight lines, arcs, spirals, or serrated lines; these different edge profiles can further optimize gas flow and pressure distribution, improving the sealing effect. Specifically, the design of the herringbone groove 101 reduces the direct contact area between the radial sealing plate and the rotor; thus reducing the contact area can reduce friction and wear, thereby extending the service life of the radial sealing plate; at the same time, this design can also reduce the volume of the radial sealing plate, constituting a lightweight design.

[0059] Furthermore, the herringbone groove 101 structure helps enhance the vibration resistance of the radial seal. The groove structure can absorb and offset some of the vibration energy during operation, thereby reducing wear and damage to the radial seal in high-vibration environments.

[0060] Furthermore, grooveless sealing weir areas 102 are provided between each pair of herringbone grooves 101. These areas help stabilize airflow and prevent gas leakage. At the same time, sealing dam areas 103 are also provided along the rotor rotation direction to further enhance the sealing effect.

[0061] This invention utilizes the principle of gas lubrication. Gas lubrication involves forming a thin film of gas between the radial sealing plate and the rotor contact surface, and achieving lubrication and sealing effects through the pressure of this gas film. Because it employs gas lubrication and sealing principles, the sealing oil system required in traditional sealing systems is eliminated. This not only simplifies system design and reduces maintenance and operating costs, but also avoids the possibility of oil contamination of the sealing fluid.

[0062] During operation, the slotted gas seal generates a stable adsorption force on both sealing end faces. This adsorption force is strong enough to completely bind the two sealing end faces together, ensuring a tight seal. This adsorption force significantly reduces leakage and improves the stability and reliability of the seal. Specifically, as the rotor rotates, the gas passing through the herringbone groove 101 experiences pressure changes. The geometry of the herringbone groove 101 causes localized high-pressure and low-pressure zones within the groove, and these pressure changes generate an 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 gas to enter the groove. Due to pressure differences at different locations within the groove, differential pressure and negative pressure are generated, thus creating an adsorption force between the radial sealing plate and the rotor. This adsorption force ensures a tight fit between the radial sealing plate and the rotor, achieving a seal.

[0063] Furthermore, the preferred radial sealing material of this invention is silicon carbide or cemented carbide. These materials possess high hardness and wear resistance, enabling them to maintain structural stability and sealing performance under high pressure and high temperature environments. The microtexture structure of the radial sealing sheet can be achieved through laser processing. Laser processing offers advantages such as high precision and controllability, allowing for the precise engraving of the desired microtexture on the radial sealing sheet.

[0064] The beneficial effects of the microtexture on the surface of the radial sealing plate of the cycloidal rotor engine described in this invention are as follows:

[0065] First, the microtextured surface of the radial sealing sheet of the cycloidal rotor engine described in this invention, compared with the existing ungrooved radial sealing sheet sealing technology, reduces the volume of the radial sealing sheet by grooves, reduces the contact area between the radial sealing sheet and the rotor, reduces the frictional loss between the radial sealing sheet and the rotor, and extends the service life from the original 200 hours to 300-500 hours, thus extending the replacement cycle of the radial sealing sheet. This achieves the purpose of reducing operating costs, reducing leakage, and making the seal more stable. In addition, the grooves on the radial sealing sheet can utilize the dynamic pressure effect generated when the gas flows in the grooves to obtain an adsorption force between the radial sealing sheet and the rotor, so that the radial sealing sheet and the rotor can fit tightly together, achieving stable sealing performance and reducing gas leakage.

[0066] Secondly, the radial sealing sheet surface microtexture of the cycloidal rotor engine described in this invention addresses the problems of unstable sealing, easy leakage, and severe wear of existing radial sealing sheets. It provides a double-layer herringbone groove type 101 radial sealing sheet, as shown in Figure 1. The groove is opened on the arc surface where the radial seal contacts the rotor, and the radial sealing sheet is fixed within the radial sealing sheet fixing groove of the engine housing. Based on gas lubrication theory, this invention utilizes superimposed and combined structural features. According to the influence of the groove shape, groove geometry parameters, and operating parameters on the sealing performance, the groove structure of the radial sealing sheet contact surface is designed to generate stronger fluid pressure changes, significantly improving the sealing effect, thereby enhancing the operational stability of the seal and extending its service life.

[0067] Third, the microtexture on the surface of the radial sealing sheet of the cycloidal rotor engine described in this invention can obtain an adsorption force between the rotor and the radial sealing sheet 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 sheet, and lowers the production cost. Furthermore, the herringbone groove 101 (microtexture) on the surface of the radial sealing sheet has better resistance to rotor vibration. The groove on the surface of the radial sealing sheet reduces the contact area between the radial sealing sheet and the rotor, resulting in a longer service life and extending the replacement cycle of the radial seal. This achieves the purpose of reducing usage costs, reducing leakage, and making the seal more stable.

[0068] Fourth, the radial sealing plate surface microtexture of the cycloidal rotor engine described in this invention, with its herringbone groove type 101 gas seal, utilizes two relatively rotating sealing components. The pressure change generated by the shearing of the fluid between the radial sealing plate and the rotor during rotation causes the radial sealing plate and the rotor to adhere to each other under pressure, ultimately maintaining a prolonged contact seal at the sealing end faces. The slotted gas seal eliminates the need for a sealing oil system and avoids some related common problems. It features low leakage, low energy consumption, low maintenance, and the sealed fluid is not contaminated by oil. Unlike other seals, the slotted gas seal generates a stable adsorption force on the two sealing end faces during operation. This strong adsorption force ensures the two sealing end faces are completely adhered together, thus guaranteeing a sealing effect.

[0069] Fifth, this invention achieves considerable technological advancement and practicality, and has broad application value in the engine sealing element industry. It possesses at least the following advantages: First, by creating a double-layer herringbone groove 101 on the surface of the radial sealing sheet, this invention creates a pressure difference and negative pressure on the high-pressure intake side, enhancing the adsorption force between the radial sealing sheet and the rotor. This prevents the radial sealing sheet from pulsating (beating phenomenon) on the cylinder profile, maintaining the stability of the cycloidal rotor engine. Second, the double-layer herringbone groove 101 structure of this invention can create a negative pressure on the high-pressure intake side, more tightly adsorbing the radial sealing sheet and the rotor together, thereby improving sealing performance and reducing leakage. Third, the sealing weir area 102 and sealing dam area 103 structure on the radial sealing sheet of this invention also act as a sealing barrier, further reducing gas leakage. Attached Figure Description

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

[0071] Figure 2 is a wireframe diagram of the radial sealing sheet of the herringbone groove 101 described in this invention;

[0072] Figure 3 is a model diagram of the radial sealing sheet of the herringbone groove 101 described in this invention;

[0073] Figure 4 is a layered view of the microtexture on the surface of the radial sealing sheet of a cycloidal rotor engine according to the present invention;

[0074] Figure 5 is a detailed model diagram of the microtexture layering view of the radial sealing sheet surface of a cycloidal rotor engine according to the present invention.

[0075] Figure 6 is a detailed wireframe view of the microtexture layering on the surface of the radial sealing sheet of a cycloidal rotor engine according to the present invention.

[0076] Figure 7 is a schematic diagram of the airflow path of the microtexture on the surface of the radial seal of a cycloidal rotor engine according to the present invention.

[0077] [Labels in the diagram]: Radial sealing plate 1; Rotor 4; Herringbone groove 101; Sealing weir area 102; Sealing dam area 103; Symmetry center line 104; Upper air inlet 201; Lower air inlet 202; Upper air outlet 203; Lower air outlet 204; Rotor engine stator mounting surface 301; Bottom spring mounting location 302. Detailed Implementation

[0078] To further illustrate the technical means and effects adopted by the present invention to achieve the intended purpose, the following detailed description, in conjunction with the accompanying drawings and preferred embodiments, details the specific implementation, structure, features, and practical problems that can be solved by the radial sealing surface microtexture of a cycloidal rotor engine according to the present invention.

[0079] Please refer to Figures 1-3. This invention describes a microtexture on the surface of a radial sealing plate of a cycloidal rotor engine. The purpose is to create a sealing structure with herringbone grooves 101 on the curved surface of the radial sealing plate. Gas enters through the grooves of the herringbone grooves 101 and the upper air inlet 201 and lower air inlet 202 of the radial sealing plate. The pressure reaches its maximum value within the grooves of the herringbone grooves 101. Correspondingly, the gas is discharged from the upper air outlet 203 and the lower air outlet 204, realizing the exhaust from the high-pressure area on the right to the low-pressure area on the left. Several herringbone grooves 101 are evenly distributed axially on the curved surface of the radial sealing plate. The non-grooved area between two pairs of axially adjacent herringbone grooves 101 is the sealing weir area 102, and the non-grooved area outside the herringbone grooves 101 is the sealing dam area 103.

[0080] In this invention, the herringbone groove 101 is an axisymmetric shape, and the herringbone groove 101 on the radial sealing sheet is symmetrical along the symmetry center line 104 of the radial sealing sheet.

[0081] In this invention, gas enters the groove through the upper air inlet 201 and the lower air inlet 202. A negative pressure is generated by the pressure difference at various points in the radial sealing plate's curved herringbone groove 101, thereby causing the radial sealing plate 1 to adhere to the rotor.

[0082] As shown in Figure 1, the top view of the slotted curved surface of the herringbone groove type 101 seal of the present invention shows the structure of the radial sealing sheet 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.

[0083] The herringbone groove 101 is the microtexture on the surface of the radial sealing sheet 1 shown in Figure 1, mainly composed of multiple 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. These areas are not grooved and are used to increase the sealing effect and prevent gas leakage. The sealing dam area 103 is located in the ungrooved area outside the herringbone grooves 101 and its function is to further enhance the sealing performance of the radial sealing sheet. The symmetry center line 104 represents the symmetry center or geometric center of the structure of the radial sealing sheet 1 and is used for reference or alignment.

[0084] The herringbone groove 101 refers to the V-shaped channels formed on the surface of the radial sealing plate 1. These channels are arranged along the axial direction of the radial sealing plate, resembling a herringbone (V-shape). 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 inlet and flows through these herringbone grooves 101. Furthermore, the V-shape of the channels causes the gas to split and converge during the flow, forming a local pressure gradient. This pressure difference enhances the sealing effect to a certain extent, preventing the gas from rapidly leaking directly from the upper inlet 201 and lower inlet 202 to the upper outlet 203 and lower outlet 204, thereby improving the overall sealing performance of the radial sealing plate.

[0085] The sealing weir area 102 is the non-grooved area between the herringbone grooves 101; these areas are smooth and flat without any grooves. The function of the sealing weir area 102 is to act as a blocking area for gas flow, preventing gas from flowing between different grooves; these ungrooved areas, by increasing the effective contact area of ​​the radial sealing sheet, block the flow path of gas between two adjacent grooves, further enhancing the sealing performance; thus, it can effectively prevent gas from flowing along the radial sealing sheet surface along an unintended path, thereby reducing leakage.

[0086] The sealing dam area 103 is the ungrooved area outside the herringbone groove 101. Similar to the sealing weir area 102, the sealing dam area 103 serves as an additional barrier to prevent gas leakage from the edges of the radial sealing strip. In actual operation, the sealing dam area 103 can form a tight contact with the cycloidal rotor engine housing or stator, thereby preventing gas from escaping through the outer edge of the radial sealing strip and ensuring the integrity of the seal.

[0087] The symmetry centerline 104 represents the symmetry center or geometric center of the radial sealing plate. The symmetry centerline 104 may serve as a reference line during design and manufacturing to ensure the symmetry and uniform distribution of the component structures such as the herringbone groove 101, the sealing weir area 102, and the sealing dam area 103. This is crucial for ensuring uniform stress and consistent wear of the radial sealing plate during operation, thereby guaranteeing the stable operation of the cycloidal rotor engine. As shown in Figure 1, in the top view of the grooved curved surface of the herringbone groove seal, the groove angle points towards the rotor's rotation direction. Gas enters the groove through the upper air inlet 201 and the lower air inlet 202, creating different pressures at different locations within the groove, generating a negative pressure. This creates an adsorption force between the radial sealing plate and the rotor, ensuring tight contact and reducing gas leakage. Due to the surface groove, the contact area between the radial sealing plate and the rotor is reduced, thus reducing frictional losses between them.

[0088] In terms of gas flow, as the rotor rotates, gas enters the slot through the upper inlet 201 and the lower inlet 202; then the gas flows along the V-shaped path of the herringbone groove 101. This complex flow path increases flow resistance and creates different pressure zones.

[0089] In terms of pressure changes, due to the different geometry of the herringbone groove 101 and the groove, the gas forms different pressure zones during the flow process, forming a pressure gradient; the pressure gradient formed by the gas in the groove generates a negative pressure effect (located in the sealing dam area 103), which causes an adsorption force between the radial sealing plate and the rotor.

[0090] 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, and extends the service life of the radial sealing plate 1.

[0091] 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 operating efficiency.

[0092] Figure 2-3 shows a wireframe diagram of the radial sealing plate 1 with herringbone groove 101. The groove depth is 1-5 micrometers. To make the groove depth more intuitive, it has been enlarged. Specifically, the herringbone groove 101 presents multiple parallel herringbone structures. The upper air inlet 201 and the lower air inlet 202 enter in the direction of rotation of the rotor 4, ensuring that the gas can smoothly enter the groove. Specifically, multiple parallel herringbone grooves 101 are evenly distributed on the surface of the radial sealing plate 1, forming a continuous flow path and pressure change area. Specifically, although the actual groove depth is 1-5 micrometers, the enlarged display in the model makes the shape and arrangement of the herringbone groove 101 clearer. Specifically, through the design of the upper air inlet 201, the lower air inlet 202, and the grooves, the gas flows along the complex path of the herringbone groove 101, forming different pressure gradients and negative pressure effects.

[0093] As shown in Figure 2, in the cycloidal rotor engine, the upper air inlet 201, lower air inlet 202, upper air outlet 203, and lower air outlet 204 are the key nodes for air intake and exhaust, respectively. Gas flows inside the sealing plate through the herringbone groove 101 structure, achieving effective sealing through pressure difference and friction. The upper air inlet 201, lower air inlet 202, upper air outlet 203, and lower air outlet 204 operate independently, ensuring the efficient operation of the cycloidal rotor engine. The entire sealing system, through complex fluid dynamics design, achieves gas control and sealing, minimizing leakage risks and improving the efficiency and stability of the cycloidal rotor engine.

[0094] Specifically, the upper air inlet 201 and the upper air outlet 203 constitute the gas pressure and flow path, involving gas pressure control, flow path management, and optimized design of the sealing structure.

[0095] From the perspective of controlling gas pressure and flow path, the following gas flow process occurs:

[0096] S1. Introduction of High-Pressure Gas (Upper Inlet 201): When the cycloidal rotor engine is running, gas enters the upper part of the radial sealing plate through the upper inlet 201. At this time, the gas pressure is relatively high. Due to the herringbone grooves 101 on the radial sealing plate, the gas first undergoes a pressure distribution adjustment after entering. The structure of the herringbone grooves 101 guides the gas into multiple branch paths, which not only extend the gas flow distance but also increase its contact surface area. Inside the channels, due to the shape and arrangement of the herringbone grooves 101, the gas is subjected to a certain frictional force. As the gas flows within the channels, some pressure is released and consumed. At the same time, the gas flow path becomes more tortuous, which effectively reduces the gas flow velocity, thereby reducing its kinetic energy and suppressing gas leakage.

[0097] S2. Formation of the low-pressure zone (upper outlet 203): As the gas is guided by the herringbone groove 101, it gradually reaches the other end of the radial sealing strip, near the upper outlet 203. Due to the design of the groove, the gas pressure in this area is significantly lower than when it enters. The formation of the low-pressure zone helps guide the gas to flow naturally to the upper outlet 203 and prevents backflow of gas within the system. Furthermore, the gradually narrowing structure of the herringbone groove 101 allows the gas pressure to gradually decrease from the upper inlet 201 to the upper outlet 203. This pressure gradient ensures that the gas can flow along the designed path and be smoothly discharged from the system. In terms of enhancing the sealing effect, during the gas flow through the herringbone groove 101, the friction between the gas and the groove wall not only slows down the gas speed but also further increases the sealing effect of the radial sealing strip. This friction causes some of the gas's kinetic energy to be converted into heat energy, thereby reducing its fluidity and minimizing potential leakage.

[0098] Regarding the enhanced sealing effect, as gas flows through the herringbone groove 101, the friction between the gas and the groove wall not only slows down the gas velocity but also further enhances the sealing effect of the radial sealing strip. This friction causes some of the gas's kinetic energy to be converted into heat energy, thereby reducing its fluidity and minimizing potential leakage. Regarding the pressure difference within the groove, inside the herringbone groove 101, due to its curved shape and narrowing, localized high-pressure and low-pressure zones are formed during gas flow. The high-pressure zone is located near the upper air inlet 201, while the pressure gradually decreases as the gas flows along the groove, forming a low-pressure zone. This pressure difference largely prevents reverse gas flow and leakage.

[0099] During the operation of the cycloidal rotor engine, the gas flows along a predetermined path within the sealing plate, achieving a good sealing effect through effective pressure management and friction, preventing gas leakage and improving the working efficiency of the cycloidal rotor engine. Gas at the upper inlet 201 enters the radial sealing plate under high pressure and flows along the herringbone groove 101. The groove's structural design effectively controls the gas flow path through friction and pressure gradient, causing the gas to gradually decelerate and flow smoothly to the low-pressure area. Gas at the upper outlet 203, guided by the groove, is discharged from the system at a lower pressure and speed, thus completing the gas flow path.

[0100] Specifically, the lower air inlet 202 and the lower air outlet 204 constitute the gas pressure and flow path, involving gas pressure control, flow path management, and optimized design of the sealing structure.

[0101] From the perspective of gas path control and pressure management, the following gas flow process is involved:

[0102] S1. Introduction of High-Pressure Gas (Lower Inlet 202): When the gas enters the lower part of the sealing plate through the lower inlet 202, it is under higher pressure. Similar to the upper layer, the herringbone groove 101 guides the incoming gas through multiple tortuous paths, which increase the length and surface area of ​​the gas flow, thereby helping to control the gas velocity and pressure. The design of the lower herringbone groove 101 is similar to that of the upper layer. The structure of the groove causes friction as the gas flows through the radial sealing plate, and some pressure is dissipated. This friction not only controls the gas flow speed but also reduces the kinetic energy of the gas to a certain extent, preventing it from leaking from the side edge of the groove.

[0103] S2. Formation of the low-pressure zone (lower outlet 204): As gas flows through the herringbone channel 101 and gradually reaches the lower outlet 204, the gas pressure gradually decreases, forming a low-pressure zone. This low-pressure zone helps the gas to be smoothly discharged from the lower layer of the system and prevents gas from flowing back to the inlet. The tapering design of the herringbone channel 101 from the lower inlet 202 to the lower outlet 204 creates a pressure gradient. This pressure gradient forces the gas to flow along a predetermined path and gradually loses kinetic energy as it flows through each channel, ensuring that the gas can be smoothly discharged without backflow.

[0104] In terms of enhancing the sealing effect, as gas flows through the lower herringbone groove 101, the friction between the gas and the groove wall further slows down the gas velocity and increases the sealing effect. Friction not only helps reduce the gas flow velocity but also increases the radial sealing plate's control over the gas, reducing potential leakage risks. Regarding the utilization of pressure difference, the lower gas path design also utilizes the pressure difference within the herringbone groove 101. Gas enters in a high-pressure zone, and as it flows along the herringbone groove 101, it gradually enters a low-pressure zone. This pressure difference not only propels the gas along the designed path but also effectively prevents gas leakage from inside the groove.

[0105] Similarly, the lower layer is designed similarly to the upper layer, utilizing the friction and pressure difference generated by the herringbone groove 101 structure to control gas flow. The high-pressure gas near the lower intake 202 is gradually depressurized through the groove and finally discharged from the lower outlet 204, ensuring that the gas flow path inside the radial seal is controlled. Through effective sealing and flow management, the risk of leakage is minimized, maintaining the engine's efficient operation.

[0106] Gas from the lower inlet 202 enters the radial sealing plate under high pressure and flows along the path of the herringbone groove 101. The structure of the herringbone groove 101 slows down the flow velocity of the gas and controls its flow path through friction and pressure gradient. Gas at the lower outlet 204 is guided by the groove and discharged from the system at a lower pressure and velocity, completing the gas flow path in the lower layer.

[0107] Figure 3 illustrates the key structure of the stator of the cycloidal rotor engine, particularly its mounting surface and spring mounting position. The mounting surface 301 of the rotor engine stator supports and fixes the stator, ensuring a tight fit with the rotor, while the bottom spring mounting position 302 is the fixed position of the spring, providing continuous elasticity during operation to maintain the sealing effect between the radial sealing plate and the stator.

[0108] The mounting surface 301 of the rotor engine stator refers to one or more specially designed planes on the rotor engine stator for contacting and fixing with other key components of the cycloidal rotor engine (such as radial seals, housing, and support structure). The mounting surface 301 of the rotor engine stator is precision machined to ensure that it provides a flat and stable contact surface for seamless cooperation with other components.

[0109] The mounting surface 301 of the stator of the cycloidal rotor engine is the main support point of the stator. Through the mounting surface 301, the stator can be firmly installed on the housing or other fixed components of the cycloidal rotor engine, ensuring that the stator will not move or loosen during the operation of the cycloidal rotor engine. The contact between the mounting surface 301 of the stator and other components is through the radial sealing plate or housing, keeping the stator in its working position. Since the fitting accuracy between the rotor and stator in the cycloidal rotor engine is crucial, the mounting surface 301 of the stator must ensure that the stator maintains its ideal position throughout the entire operation.

[0110] In terms of ensuring sealing performance, the sealing effect directly affects the working efficiency and performance of the cycloidal rotor engine. The precision of the mounting surface 301 of the rotor engine stator ensures strict clearance control between the stator and the radial sealing plate, thereby achieving good airtightness. Regarding the fit with the radial sealing plate, the radial sealing plate needs to fit tightly against the surface of the stator, and the mounting surface 301 of the rotor engine stator serves as a positioning reference, ensuring this sealing effect; therefore, any slight error will lead to gas leakage, thereby reducing the efficiency of the cycloidal rotor engine. From the perspective of affecting the system's operating efficiency, the precision 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 uneven or does not meet design requirements, it will cause the stator to shift position, resulting in poor sealing, increased friction between the rotor and stator, and even malfunction of the cycloidal rotor engine. 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, and extend the service life of the cycloidal 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, and reduce excessive wear or mechanical stress concentration.

[0111] In a specific installation scenario, the mounting surface 301 of the rotor engine stator functions as follows:

[0112] During the assembly of the cycloidal rotor engine, the mounting surface 301 of the rotor engine stator serves as a critical positioning reference, ensuring that the stator can be precisely installed in the designed position. This process requires extremely high precision, as any slight deviation will affect the final sealing effect and the balance of rotor operation.

[0113] During operation of the cycloidal rotor engine, the mounting surface 301 of the rotor engine stator must maintain its structural integrity and precision. 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.

[0114] During the 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.

[0115] The bottom spring mounting point 302 is a position on the radial sealing plate or stator structure specifically used to fix the spring. The bottom spring mounting point 302 usually has a certain groove or fixing structure so that the spring can be accurately and stably placed in the designed position.

[0116] To provide continuous elasticity, a spring is installed at the bottom spring mounting point 302. The spring force presses the radial sealing plate firmly against the stator surface. Because the elasticity is continuous, it ensures that the radial sealing plate maintains tight contact with the stator under different operating conditions (such as temperature changes and pressure fluctuations). Since the radial sealing plate needs to maintain tight contact between the high-speed rotating rotor and the stationary stator, the spring force compensates for gap changes caused by factors such as thermal expansion and contraction of materials and wear, preventing gas leakage. To compensate for wear and temperature changes, during the long-term operation of the cycloidal rotor engine, the radial sealing plate will wear, leading to an increase in the gap between it and the stator.

[0117] The spring is installed at the bottom spring mounting point 302. The spring force presses the radial sealing plate firmly against the surface of the stator. This force is continuous, ensuring that the radial sealing plate maintains tight contact with the stator under different operating conditions (such as temperature changes and pressure fluctuations). Since the radial sealing plate needs to maintain tight contact between the high-speed rotating rotor and the stationary stator, the spring force compensates for gap changes caused by factors such as thermal expansion and contraction of materials and wear, preventing gas leakage.

[0118] The spring is mounted at the bottom spring mounting point 302. This mounting point securely positions the spring in the correct location, preventing displacement or detachment during operation and ensuring stable functioning. The bottom spring mounting point 302 not only secures the spring but also facilitates maintenance and replacement. When maintenance or replacement is needed, this mounting point allows engineers to easily remove the old spring and install the new one, maintaining efficient engine operation.

[0119] Figures 4, 5, and 6 illustrate the relative positions and structures of the radial seal 1 and the rotor 4 in the cycloidal rotor engine. The radial seal tightly surrounds the rotor, and its shape precisely matches the rotor surface to prevent gas leakage, ensuring the efficient operation of the cycloidal rotor engine.

[0120] The radial sealing plate 1 is a key component for forming a seal between the rotor and stator. Surrounding the rotor, it is located in the contact area between the rotor 4 and the stator, preventing gas leakage through tight contact. As shown in Figure 4, the radial sealing plate exhibits a complex closed-curve shape, designed to match the shape of the rotor 4 and ensure a good seal throughout operation. The radial sealing plate 1 forms an airtight barrier by adhering to the outer surface of the rotor 4, preventing high-pressure gas inside the engine from leaking to the outside. Because the radial sealing plate 1 continuously contacts and rubs against the surface of the rotor 4 during operation, it has good wear resistance, extending its service life and maintaining the sealing effect. The rotor 4 is the core component of the cycloidal rotor engine; the area enclosed by the radial sealing plate in Figure 4 is the rotor 4. The rotor 4 rotates during the operation of the cycloidal rotor engine, driving gas flow and generating power. The shape of the rotor 4 matches the radial sealing plate, forming a complex curved shape to ensure that the radial sealing plate 1 can tightly adhere to the rotor surface during rotation. The rotation of the rotor 4 causes gas compression or expansion, thus completing the working cycle of the cycloidal rotor engine.

[0121] The outer surface of the rotor 4 is in direct contact with the radial sealing plate; the radial sealing plate 1 is tightly attached to the outer surface of the rotor 4, maintaining airtightness as the rotor 4 rotates to prevent gas leakage. The rotational motion of the rotor 4 not only drives the cycloidal rotor engine to work, but also ensures that the gas flows according to the airflow path inside the cycloidal rotor engine through its shape and the cooperation of the radial sealing plate 1, thereby maintaining the normal operation of the cycloidal rotor engine.

[0122] Figure 7 illustrates a schematic diagram of the airflow path through the microtexture on the radial seal surface of a cycloidal rotor engine. By controlling the pressure difference and flow path, the system effectively controls the gas flow velocity and direction, ensuring a good seal and preventing gas leakage during application. This structure can be used in mechanical systems requiring high-precision sealing and flow control, such as cycloidal rotor engines. The arrows in the figure indicate the airflow path, showing the gas inlet and outlet, represented by solid and dashed lines respectively. From the gas flow path, the solid arrows indicate the gas inlet path, where the gas enters the microtexture on the radial seal surface; the dashed arrows indicate the gas outlet path, where the gas exits after passing through the microtexture on the radial seal surface.

[0123] Gas enters the radial sealing sheet from the upper inlet 201 and upper outlet 203 on the left side of the diagram. After passing through a series of herringbone groove structures, it is discharged from the lower inlet 202 and lower outlet 204 on the right side.

[0124] From the perspective of gas flow principles, gas enters the radial sealing plate 1 through the upper inlet 201 and upper outlet 203 on the left side. After flowing through multiple curved surfaces and channels inside the radial sealing plate 1, it exits from the lower inlet 202 and lower outlet 204 on the right side. The herringbone groove 101 structure inside the radial sealing plate 1 guides the gas flow along the designed path. These herringbone grooves 101 are curved to increase the contact area between the gas and the groove wall by extending the gas flow path, thereby controlling the gas flow rate and pressure. The herringbone grooves 101 also create a local pressure difference by changing the gas flow direction, further enhancing the sealing effect and reducing gas leakage from the side edges.

[0125] In terms of gas flow control, when gas enters through the upper inlet 201 and upper outlet 203, the gas pressure gradually decreases within the curved channel. This pressure difference propels the gas along a predetermined path, eventually discharging it through the lower inlet 202 and lower outlet 204. As the gas flows through these herringbone channels 101, changes in pressure and velocity create a high-pressure zone at the inlet and a low-pressure zone at the outlet. This helps prevent gas leakage from the radial seals and maintains stable internal pressure.

[0126] Double herringbone groove 101

[0127] The microtexture on the surface of the radial sealing sheet of the cycloidal rotor engine described in this invention is shown in Figures 1-3. Multiple herringbone grooves 101 (with upper and lower layers) are formed on the surface of the radial sealing element, creating a double-layered structure. The opening direction of each herringbone groove 101 is consistent with the rotation direction of the rotor. Gas can enter the groove opening 201 through these grooves.

[0128] Furthermore, the herringbone grooves 101 are distributed on the surface of the radial sealing sheet, forming two layers of grooves. Each layer of herringbone grooves 101 is arranged in parallel, with the upper layer on the outer side and the lower layer on the inner side; the herringbone grooves 101 in each layer are arranged parallel to each other; each herringbone groove 101 maintains a certain interval and parallel relationship with other grooves, extending from the edge of the radial sealing sheet towards the center;

[0129] The two layers of the double-layer herringbone groove 101 structure are connected by the arrangement between the layers; the herringbone groove 101 is divided into an upper layer and a lower layer; the upper and lower herringbone grooves 101 maintain the same parallel arrangement pattern, and the opening directions of the upper herringbone groove 101 and the lower herringbone groove 101 are consistent to ensure the consistency and continuity of gas flow;

[0130] Specifically, the herringbone grooves 101 can be connected to each other in parallel or staggered arrangements; further, the herringbone grooves 101 are connected to each other, and the herringbone grooves 101 in each layer are arranged in parallel to each other to form multiple independent flow channels; each herringbone groove 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 in the adjacent groove, thereby maintaining their respective pressure gradients and flow characteristics;

[0131] Specifically, the herringbone groove 101 is divided into two layers: an upper groove and a lower groove. The opening directions of the upper and lower grooves are the same, and high-pressure gas enters both the upper and lower herringbone grooves simultaneously from the groove opening 101. The upper and lower herringbone grooves 101 maintain a certain vertical distance, which ensures the independence of each groove layer while allowing gas to flow freely between layers. The openings of the upper and lower grooves are aligned in the vertical direction, allowing gas to pass through both the upper and lower herringbone grooves simultaneously, generating greater adsorption force and enhancing the sealing effect.

[0132] Furthermore, the opening direction of the herringbone groove 101 is consistent with the rotation direction of the rotor (i.e., the center line of symmetry 104 is symmetrical), that is, the opening direction of the herringbone groove 101 always points towards the direction of the rotor rotation, so that the gas can follow the flow path and smoothly enter the upper air inlet 201 and the upper air outlet 203 in the groove, and form the required flow and pressure change in the groove.

[0133] Specifically, the rotation direction of the rotor relative to a fixed reference frame (such as the casing or mounting base of a cycloidal rotor engine) does not change with the change of the viewing angle; the rotation direction of the rotor can be clockwise or counterclockwise, both observed from a fixed perspective (usually from above or in front), and does not change with the change of the viewing angle.

[0134] Specifically, each herringbone groove 101 is composed of two symmetrical herringbone structures. Each groove expands from the center to both sides to form a herringbone shape. 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 rotation and flows along the designed path to form effective pressure changes and gradients.

[0135] Specifically, each herringbone groove 101 is symmetrical on both sides, that is, the angle and length of the two herringbone structures are the same, which makes the gas flow path in the groove balanced and avoids flow instability; the symmetry of the herringbone groove 101 makes the gas form a uniform pressure gradient in the groove.

[0136] Alternatively, in the double-layer structure design, the herringbone grooves 101 can be arranged in an alternating pattern, that is, the upper herringbone grooves 101 and the lower herringbone grooves 101 alternate in the longitudinal direction. Gas enters the upper herringbone groove and the lower herringbone groove at the same time, which increases the adsorption force between the radial seal and the rotor, making the sealing effect more stable.

[0137] The upper herringbone groove 101 and the lower herringbone groove 101 are arranged in an alternating vertical direction, with the opening of the upper herringbone groove 101 located in the middle of the lower herringbone groove 101, ensuring the complexity and continuity of the gas flow path.

[0138] The opening direction of both the upper herringbone groove 101 and the lower herringbone groove 101 is consistent with the rotation direction of the rotor, so that the gas can smoothly enter the groove and flow along the airflow path.

[0139] Each herringbone groove 101 maintains the same angle to ensure a balanced gas flow path and a stable pressure gradient.

[0140] The two sides of the herringbone groove 101 are symmetrical, ensuring a balanced gas flow path within the groove. This symmetry is maintained in both the upper and lower layers, ensuring the stability of the radial sealing sheet. The staggered arrangement of the upper and lower herringbone grooves 101 creates alternating flow paths in the vertical direction, further enhancing the complexity of the gas flow.

[0141] In summary, 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 sheet has multiple parallel or staggered herringbone grooves 101 from the edge to the center; the opening direction of each herringbone groove 101 is consistent with the rotation direction of the rotor, ensuring that gas can smoothly enter the groove.

[0142] The herringbone groove 101 has a specific depth and width to optimize gas flow and pressure changes. It is precisely designed through geometric parameters to achieve the best sealing effect. Each herringbone groove 101 in the double-layer structure exists independently, but together they form a complex combined structure, making the gas flow path in the groove more complex.

[0143] The number of grooves in the herringbone groove 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.

[0144] Specifically, the density of the herringbone groove 101 is the number of grooves per unit area, which depends on the requirements of the radial sealing sheet and the operating parameters;

[0145] 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, for applications requiring high sealing performance, can increase the number of herringbone grooves per unit area, thereby increasing the frequency of pressure changes in the radial sealing sheet and improving the sealing effect. The low-density design, for applications with high requirements for friction loss, can reduce the number of herringbone grooves per unit area, thereby reducing the contact area and friction loss of the radial sealing sheet.

[0146] Specific parameter examples, for instance, the fixed spacing between each herringbone groove 101 is 5 mm; the number of grooves and groove density are as follows: in terms of the number of grooves, if the radial sealing strip width is 100 mm, there may be 20 grooves (5 mm spacing) in a high-density design and 10 grooves (10 mm spacing) in a low-density design; in terms of groove density, the high-density design has more grooves per unit area, for example, 4 grooves per square centimeter; the low-density design has fewer grooves per unit area, for example, 2 grooves per square centimeter.

[0147] Specifically, the double-layer herringbone groove 101 divides the contact area between the radial sealing sheet and the rotor into multiple smaller areas, which reduces friction and increases the sealing effect through the pressure change of the gas in the groove.

[0148] Furthermore, the contact area between the radial sealing plate and the rotor is the area where the radial sealing plate actually contacts the rotor surface;

[0149] Furthermore, the contact area of ​​the rotor is mainly located in the interval between the herringbone grooves 101. The specific number and position of the contact area depend on the number and arrangement of the grooves. That is, multiple parallel or intersecting herringbone grooves 101 are formed on the surface of the rotor, and each groove will divide the contact surface into several parts.

[0150] Furthermore, the spaced portion of the groove is the solid portion between the herringbone grooves 101 that has not been cut; the edge of the groove is a high-pressure area near the edge of the groove, although the groove itself is not a contact surface, a tiny contact area is formed near the edge of the groove.

[0151] For example, the radial sealing sheet has five parallel herringbone grooves 101, and the interval between the grooves is the part that actually contacts the rotor; the specific location of the contact area is as follows:

[0152] Contact area 1: The space between the first herringbone groove 101 and the second groove;

[0153] Contact area 2: The gap between the second and third slots;

[0154] Contact area 3: The gap between the third and fourth slots;

[0155] Contact area 4: The interval area between the fourth and fifth slots;

[0156] Contact area 5: The gap between the fifth groove and the edge of the radial sealing plate.

[0157] The double-layer herringbone groove 101 optimizes the gas flow path and pressure distribution, and is divided into gas flow transmission, pressure transmission and force transmission.

[0158] Specifically, in the gas flow transmission, when the rotor rotates, the gas enters the upper air inlet 201 and the upper air outlet 203 through the symmetrical center line 104 of the herringbone groove 101. The opening direction of the herringbone groove 101 is consistent with the rotor rotation direction, allowing the gas to be smoothly introduced into the groove. The double-layer herringbone groove 101 has a double-layer herringbone structure, with the upper herringbone groove 101 and the lower herringbone groove 101 arranged alternately. The gas enters the upper herringbone groove 101 and the lower herringbone groove 101 simultaneously, making the seal between the rotor and the radial sealing plate more stable. The gas flow path continuously changes direction and speed during the flow process according to the geometry 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, realizing exhaust from the high-pressure area on the right to the low-pressure area on the left.

[0159] Specifically, the pressure transmission is achieved because the complex flow path of the herringbone groove 101 causes the gas flow velocity and direction to change continuously within the groove, forming different pressure zones. The pressure change of the gas within the groove creates a negative pressure effect between the radial sealing plate and the rotor through the principle of fluid dynamics. This negative pressure causes the radial sealing plate to fit tightly against the rotor, 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 and lower herringbone grooves 101 more continuous and stable, ensuring that a uniform negative pressure zone is formed on the entire surface of the radial sealing plate.

[0160] Specifically, the force transmission, namely the adsorption force generated by the negative pressure effect in the groove, causes the radial sealing plate to come into close contact with the rotor surface, generating a negative pressure effect force transmission; the negative pressure makes the radial sealing plate fit the rotor more tightly, reducing the sliding friction on the contact surface, and the resulting negative pressure effect reduces the friction between the radial sealing plate and the rotor; the reduction of friction reduces the wear and energy loss of the radial sealing plate and the rotor, thereby extending the service life of the radial sealing plate and improving the overall efficiency of the cycloidal rotor engine.

[0161] Sealed weir area 102

[0162] The microtexture on the surface of the radial sealing sheet of the cycloidal rotor engine described in this invention is shown in Figures 1-3. The sealing weir area 102 is the middle part located between two adjacent herringbone grooves 101, which is a grooveless area, thus avoiding disturbance of airflow during the transition.

[0163] 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 airflow from the herringbone groove 101 to the sealing weir area 102.

[0164] Specifically, the sealing weir area 102 and the adjacent herringbone groove 101 form a continuous surface without physical separation, effectively dividing the herringbone groove 101 into several pairs and providing necessary obstruction in the airflow path.

[0165] Specifically, the sealing weir area 102, through its grooveless design, forms a complementary structure with the herringbone groove 101, blocking and controlling the airflow;

[0166] Furthermore, a continuous, complementary, and complete sealing structure is formed between the sealing weir area 102 and the herringbone groove 101. As a result, the pressure difference and negative pressure effect generated by the herringbone groove 101 are enhanced in the sealing weir area 102, thereby improving the sealing effect. The sealing weir area 102 divides the herringbone groove 101 into several pairs, forming multiple 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.

[0167] Furthermore, the sealing weir area 102 and the sealing dam area 103 work together, with the sealing weir area 102 providing primary blocking and the sealing dam area 103 providing 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.

[0168] Furthermore, the sealing weir area 102, through its grooveless surface, transmits 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; 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 transmitting 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 sheet.

[0169] Sealed dam area 103

[0170] The microtexture on the surface of the radial sealing sheet of the cycloidal rotor engine described in this invention is shown in Figures 1-3. The sealing dam area 103 is located on the outer edge of the herringbone groove 101 and is a grooveless area, which avoids the disturbance of airflow during the transition. The sealing dam area 103 is a continuous and smooth surface without any grooves, which can block the escape of airflow and reduce wear.

[0171] Specifically, the sealing dam area 103 is located at the outer edge of the herringbone groove 101 and is arranged along the rotor rotation direction. In Figures 1-3, the sealing dam area 103 is usually shown as the outer edge of the radial sealing sheet, forming an additional sealing protection area.

[0172] Specifically, there is no physical separation between the sealing dam area 103 and the adjacent herringbone groove 101, forming a continuous and seamless connection, which allows for a smooth transition of airflow 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 gas from escaping from the outside of the radial sealing sheet.

[0173] Furthermore, the sealing dam area 103, through its own grooveless area, forms a continuous and complementary structure with the herringbone groove 101, further blocking and controlling the airflow; the smooth surface of the sealing dam area 103 reduces the direct impact of the airflow and lowers the risk of wear.

[0174] Furthermore, the sealing dam area 103 is located outside the herringbone groove 101, providing 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 rotor rotation direction;

[0175] Furthermore, the sealing dam area 103, through its grooveless surface, 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 sheet; the sealing dam area 103 plays a final blocking and protection role in the airflow path, ensuring that the airflow forms a stable sealing effect on the surface of the radial sealing sheet.

[0176] Example 1: Microtexture on the surface of the radial sealing sheet of a cycloidal rotor engine according to the present invention

[0177] This embodiment achieves a highly efficient and stable radial sealing sheet through detailed structural design and operating procedures. The ingenious design of the herringbone groove 101 and the reasonable installation steps significantly improve the sealing effect and service life of the cycloidal rotor engine. This sealing structure is suitable for various high-pressure, high-speed cycloidal rotor engines, effectively improving their operating efficiency and reliability.

[0178] This embodiment provides a sealing structure with herringbone grooves 101 on the curved surface of the radial sealing plate of a cycloidal rotor engine. The specific structure is described as follows: Gas enters through the grooves of the herringbone grooves 101 and the upper air inlet 201 and upper air outlet 203 of the radial sealing plate, reaching maximum pressure within the grooves of the herringbone grooves 101. Several herringbone grooves 101 are evenly distributed axially 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 grooves 101 is a sealing dam area 103. The herringbone grooves 101 are axisymmetric, and the herringbone grooves 101 on the radial sealing plate are symmetrical along the symmetry center line 104 of the radial sealing plate. The gas enters the groove through the opening 201, and the pressure difference at various points within the herringbone groove 101 of the radial sealing plate creates a negative pressure, causing the radial sealing plate to adhere to the rotor. Finally, the gas is discharged from the upper outlet 203 and the lower outlet 204, realizing the exhaust from the high-pressure zone on the right to the low-pressure zone on the left.

[0179] Furthermore, the herringbone groove 101 structure described in this invention needs to be confirmed during implementation to ensure the positional structure of the components during operation. Specifically, the herringbone groove 101 is confirmed to have several pairs of straight-edged herringbone grooves 101 formed on the curved surface of the radial sealing sheet; each pair of herringbone grooves 101 has an equal depth and is designed as an axisymmetric shape, symmetrically distributed along the symmetry center line 104 of the radial sealing sheet. Specifically, the upper air inlet 201 and the upper air outlet 203 are the locations where gas enters the herringbone groove 101, ensuring the airflow begins. Specifically, the sealing weir area 102 is the non-grooved area located between two axially adjacent pairs of herringbone grooves 101. Specifically, the sealing dam area 103 is the non-grooved area located outside the herringbone groove 101, set along the rotor rotation direction.

[0180] Furthermore, this embodiment provides a sealing structure with herringbone grooves 101 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. In component preparation, confirm that the radial sealing plate (with a double-layer herringbone groove 101 structure), rotor, fixing bolts, and mounting fixture are ready. Specifically, the radial sealing plate has a double-layer herringbone groove 101 structure; the rotor is an engine rotor component that mates with the radial sealing plate; the fixing bolts and mounting fixture are used to fix the radial sealing plate. In tool preparation, confirm that a torque wrench, laser alignment tool, cleaning tools (such as alcohol and brushes), and mounting fixture are ready.

[0181] Assembly Step 1: Preliminary Inspection and Cleaning

[0182] (1) Inspection of components: First, check the radial sealing sheet to confirm that the double herringbone groove 101 on the radial sealing sheet has been processed according to the design requirements; then check that the groove depth of the herringbone groove 101 is 1-5μm, and that there is a grooveless sealing weir area 102 between each pair of grooves, and a sealing dam area 103 is provided on the outside.

[0183] (2) Cleaning components: Use alcohol and a brush to clean the radial seals and rotor surfaces to ensure they are free of impurities and dirt.

[0184] Assembly Step 2: Radial sealing plate positioning and installation of double-layer herringbone groove 101

[0185] (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.

[0186] (4) Initial fixing: Use the installation clamp to initially fix the radial sealing plate in position, ensuring that it fits tightly against the rotor surface; confirm that the upper air inlet 201 and 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 symmetrical center line 104 of the radial sealing plate.

[0187] Assembly Step 3: Install the sealing weir area 102

[0188] (1) Align the sealing weir area 102: Position the sealing weir area 102 on the radial sealing sheet to ensure that the sealing weir area 102 is located between two adjacent pairs of herringbone grooves 101 in the axial direction; confirm that the sealing weir area 102 and the herringbone grooves 101 are seamlessly connected to form a smooth transition.

[0189] (2) Fixing the sealing weir 102: Use appropriate clamps and tools to fix the sealing weir 102 to ensure that it is stable and without gaps.

[0190] Assembly Step 4: Install Sealed Dam Area 103

[0191] (1) Align the sealing dam area: Position the sealing dam area 103 at the outer edge of the herringbone groove 101 and arrange it along the direction of rotor rotation; confirm 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.

[0192] (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 without gaps.

[0193] Step 5: Adjust and lock

[0194] (5) Adjust position: Adjust the position of the radial sealing strip to make it fully aligned with the rotor surface; ensure that the herringbone groove 101 is symmetrically distributed along the symmetrical center line 104 of the radial sealing strip; then check the alignment of the radial sealing strip, sealing weir area 102 and sealing dam area 103 to ensure that all components are correctly positioned.

[0195] (6) Tighten the radial seal: Use a torque wrench to tighten the fixing bolts to ensure that the radial seal is firmly fixed and to prevent any loosening.

[0196] Specifically, this embodiment provides a sealing structure with herringbone grooves 101 on the curved surface of the radial sealing plate of a cycloidal rotor engine. In order to be successfully installed on the cycloidal rotor engine, preliminary preparations and processing of the radial sealing plate are necessary.

[0197] Preliminary preparations include material preparation, tool preparation, and environmental preparation. Specifically, material preparation involves selecting high-quality silicon carbide or cemented carbide materials to fabricate the radial sealing sheet; tool preparation includes laser processing equipment, installation clamps, torque wrenches, and cleaning tools (such as alcohol, brushes, etc.); and environmental preparation involves ensuring the installation environment is clean, dust-free, and dry to prevent impurities from affecting the installation quality.

[0198] According to the design of this invention, the surface of the radial sealing sheet is laser-processed with double-layer herringbone grooves 101. Specifically, in the laser processing, double-layer herringbone grooves 101 are formed on the surface of the radial sealing sheet using laser processing equipment, with a groove depth of 1-5 μm; ensuring 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 set along the rotor rotation direction; ensuring the edge shape of the herringbone grooves 101, selecting straight lines, arcs, spiral lines or sawtooth lines in the processing according to requirements. Furthermore, attention must be paid to processing accuracy during laser processing to ensure that the groove depth and groove shape meet the design requirements. Furthermore, quality inspection is required after laser processing. The finished product (radial sealing sheet with double-layer herringbone groove 101 microtexture) is cleaned to ensure no processing residue; the groove depth and groove shape are checked using inspection tools such as microscopes to ensure that the finished product after laser processing meets the installation requirements.

[0199] Furthermore, the sealing structure with herringbone grooves 101 on the curved surface of the radial sealing plate provided in this embodiment must undergo installation verification (or operational testing) after assembly in order to be applied to a cycloidal rotor engine. Installation verification (or operational testing) includes airtightness testing, operational observation, wear testing, and high-speed testing.

[0200] Specifically, in the airtightness test, the engine is started and the airtightness test is conducted to check the sealing effect between the radial seal and the rotor surface; by monitoring leakage and pressure changes, it is ensured that the sealing effect meets the design requirements; 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 seal and promptly detect and handle any abnormalities; specifically, in the wear test, when the cycloidal rotor engine runs at low speed for a period of time, it is necessary to check the working status of the radial seal 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 seal can still maintain a good sealing effect at high speeds.

[0201] Furthermore, the sealing structure provided in this embodiment, which features a herringbone groove 101 on the curved surface of the radial sealing plate of the engine, requires regular inspection of the radial sealing plate in actual operating conditions. Specifically, it is necessary to periodically inspect the state of the microtexture on the radial sealing plate, especially the upper air inlet 201 and upper air outlet 203 on the high-pressure air intake side; at the same time, it is necessary to observe the integrity of the sealing weir area 102 and the sealing dam area 103 to ensure that there is no wear or damage.

[0202] Example 2: The edge line of the herringbone groove 101 described in this invention is a straight line.

[0203] The advantage of a straight edge is that it provides basic sealing effect and structural strength. Following all aspects of the general embodiment (Embodiment 1), as mentioned above, except that the edge of the herringbone groove 101 is straight, all other design components and parameters remain unchanged. The double-layer herringbone groove 101 with a straight edge provided in this embodiment is relatively simple to design and manufacture, and is suitable for sealing scenarios requiring uniform pressure and negative pressure distribution, such as the sealing of ordinary cycloidal rotor engines and low-to-medium speed operating conditions in industrial applications.

[0204] Furthermore, the double-layer herringbone groove 101 with straight edge shape provides a sealing effect by ensuring a stable pressure distribution at the straight edge, which helps to evenly distribute negative pressure. The flow path formed by the straight edge is relatively simple, with a low turbulence effect, making it suitable for sealing scenarios that require smooth flow.

[0205] Specifically, in terms of pressure distribution and negative pressure effect, the straight edge shape can achieve uniform pressure distribution, ensuring consistent pressure across the entire radial sealing sheet surface; after the gas enters the groove, it flows along a straight path, generating negative pressure through pressure differences at different locations, ensuring that the radial sealing sheet is tightly adsorbed onto the rotor surface.

[0206] Specifically, in terms of flow path and turbulence effect, the flow path formed by the straight edge is simpler, reducing the complexity of the airflow and making the flow more stable. Due to the straight edge design, the turbulence effect is lower when the airflow flows in the groove, which is suitable for sealing scenarios that require stable flow and reduces the impact of airflow disturbance on the sealing effect.

[0207] Furthermore, in terms of applicable scenarios, the straight edge profile is suitable for sealing ordinary cycloidal rotor engines that require uniform pressure and negative pressure distribution, ensuring stable engine operation 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 long service life, making it suitable for most industrial application scenarios.

[0208] Furthermore, in terms of processing radial sealing sheets, the design of straight edge profiles is relatively simple, requiring no complex curves or multi-layered structures, making them suitable for standardized production. Straight edge profiles also facilitate high-precision manufacturing through laser processing technology, ensuring that the groove depth and shape of each pair of grooves are consistent, thus guaranteeing a sealing effect.

[0209] Example 3: The edge shape of the herringbone groove 101 of the present invention is arc-shaped.

[0210] The advantage of curved edges is that they help generate turbulence as fluid passes through, increasing energy dissipation. Following all aspects of the general embodiment (Embodiment 1), as described above, except that the edge shape of the herringbone groove 101 is curved, all other design components and parameters remain unchanged. The curved double-layer herringbone groove 101 solution provided in this embodiment has a smooth curve and is suitable for high-precision sealing scenarios requiring stable airflow and reduced wear, such as high-precision cycloidal rotor engines and high-speed cycloidal rotor engines.

[0211] The curved double-layer herringbone groove 101 provides a sealing effect. The curved edge can smoothly guide the airflow, reduce airflow turbulence, and maintain flow stability. The curved shape can alleviate stress concentration when the airflow changes direction, reduce local stress, and thus reduce wear.

[0212] In terms of airflow guidance and stability, the curved edge profile smoothly guides airflow, reducing turbulence during turns and making the flow more stable. The smooth curve allows airflow to flow smoothly along the curved edge, avoiding the flow instability that may be caused by straight edges. Due to the curved shape, airflow is less likely to form turbulence and eddies when flowing within the groove, thus reducing airflow turbulence, maintaining flow stability, and helping to improve the sealing effect.

[0213] From the perspective of stress distribution and wear control, the arc shape can effectively alleviate stress concentration during airflow changes, avoiding localized high stress caused by abrupt airflow changes. This smooth transition reduces stress concentration and lowers the local stress of the radial seal. By reducing stress concentration and airflow turbulence, the arc edge profile can significantly reduce wear and extend the service life of the radial seal, making it particularly suitable for high-precision and high-speed sealing applications.

[0214] In terms of applicable scenarios, the curved edge profile design is suitable for cycloidal rotor engine applications that require stable airflow and high-precision sealing, ensuring sealing performance in high-precision environments. Under high-speed operating conditions, the curved edge profile can effectively reduce airflow turbulence and wear, providing a stable sealing effect, making it suitable for high-speed cycloidal rotor engines.

[0215] The design of the arc edge profile in the processing of radial sealing sheets can be optimized according to specific application scenarios, adjusting the curvature and distribution of the arc to achieve the best airflow guidance and stress distribution effect; laser processing technology can accurately realize the design of the arc edge, ensuring that the groove depth and shape of each pair of grooves are consistent, and guaranteeing a high-quality sealing effect.

[0216] Example 4: The edge shape of the herringbone groove 101 described in this invention is a spiral shape.

[0217] The advantage of a spiral edge is that it further enhances the turbulence effect and increases the residence time of the fluid on the sealing surface. Following all aspects of the general embodiment (Example 1), as mentioned above, except that the edge shape of the herringbone groove 101 is spiral, all other design components remain unchanged. The spiral-shaped double-layer herringbone groove 101 scheme provided in this embodiment presents a rotating curve. The spiral edge guides the airflow along the spiral path, increasing the complexity of the flow path, significantly enhancing the pressure difference effect and 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 and viscosity effects, such as high-pressure cycloidal rotor engines.

[0218] The spiral-shaped double-layer herringbone groove 101 provides a sealing effect because the spiral edge can guide the airflow along the spiral path, increasing the complexity of the flow path and enhancing the pressure difference effect and viscosity effect. Due to the complex flow of air in the spiral path, the negative pressure effect is stronger and the sealing effect is better.

[0219] From the perspective of airflow guidance and pressure difference effect, the spiral edge profile can guide airflow along the spiral path, increasing the complexity of the flow path. The spiral path design requires the airflow to undergo more bends and turns when flowing within the slot, increasing the flow resistance. Due to the complex flow of airflow in the spiral path, the pressure difference at different locations is more pronounced, forming a stronger pressure difference effect. This can generate a greater negative pressure when the airflow passes through, thereby enhancing the adhesion between the radial seal and the rotor surface.

[0220] From a viscous perspective, the spiral edge profile increases the complexity of the flow path, thereby increasing the contact area between the airflow and the channel wall, and thus enhancing the viscous effect. This enhanced viscosity slows down the airflow velocity within the channel.

[0221] From the perspective of negative pressure effect, due to the complex flow of air in the spiral path, the negative pressure effect is stronger, which makes the adsorption force between the radial sealing plate and the rotor greater, thus ensuring the stability and reliability of the seal.

[0222] In terms of applicable scenarios, the spiral edge profile design is suitable for high-pressure cycloidal rotor engine seals that require enhanced pressure differential and viscosity effects, ensuring sealing performance under high-pressure environments. In applications with complex flow paths and high-efficiency sealing requirements, the spiral edge profile can provide better sealing performance and stability.

[0223] The design of the spiral edge profile in the processing of radial sealing sheets can be optimized according to specific application scenarios, adjusting the angle and curvature of the spiral to achieve the best airflow guidance and pressure difference effect; laser processing technology can precisely realize the design of the spiral edge, ensuring that the groove depth and shape of each pair of grooves are consistent, guaranteeing a high-quality sealing effect.

[0224] Example 5: The edge line of the herringbone groove 101 of the present invention is serrated.

[0225] The advantage of a serrated edge is that it increases the pressure difference on the sealing surface through localized pressure drop, thereby improving sealing performance. Following all aspects of the general embodiment (Embodiment 1), as mentioned above, except that the edge of the herringbone groove 101 is serrated, all other design components and parameters remain unchanged. The serrated double-layer herringbone groove 101 solution provided in this embodiment has multiple peaks and valleys, making it suitable for high-intensity sealing scenarios requiring stronger sealing and adsorption forces, such as cycloidal rotor engines under extreme operating conditions.

[0226] The serrated double-layer herringbone groove 101 provides a sealing effect by generating a stronger turbulence effect through the serrated edges, which enhances gas mixing and pressure difference effects. The serrated edges also increase the shear force of the airflow, further enhancing the adhesion between the radial sealing plate and the rotor surface.

[0227] From the perspective of turbulence and gas mixing, the serrated edge, with its multiple peaks and valleys, generates a strong turbulence effect as airflow passes through. This turbulence effect creates complex flow paths within the slot, increasing the degree of gas mixing. Due to the enhanced turbulence, the velocity changes within the slot are more drastic, thus increasing the pressure difference between different locations and creating a stronger pressure differential effect. This pressure differential effect further improves the adhesion between the radial seal and the rotor surface.

[0228] From the perspective of shear force and adsorption force, the multiple peaks and valleys of the serrated edge can increase the shear force of the airflow, making the airflow within the groove more complex. This shear force can effectively enhance the adsorption force between the radial sealing plate and the rotor surface; by enhancing the shear force and pressure difference effect of the airflow, the serrated edge profile can significantly improve the sealing effect, enabling the radial sealing plate to maintain stable sealing performance under high-intensity operating conditions.

[0229] In terms of applicable scenarios, the serrated edge design is suitable for high-strength sealing scenarios that require stronger sealing and adsorption forces, ensuring the performance of cycloidal rotor engines under extreme conditions. Moreover, under high pressure and high temperature conditions, the serrated edge design can provide stronger sealing force and stability, making it suitable for demanding industrial applications.

[0230] The design of the serrated edge profile in the processing of radial sealing sheets can be optimized according to specific application scenarios. The size and spacing of the serrations can be adjusted to achieve the best turbulence effect and shear force. Laser processing technology can precisely realize the design of the serrated edge, ensuring that the groove depth and shape of each pair of grooves are consistent, thus guaranteeing a high-quality sealing effect.

[0231] Example 6: Hybrid edge profile of the herringbone groove 101 of the present invention

[0232] The hybrid edge profile, as mentioned above, combines the technical features of different edge profiles in embodiments 2-5, further enhancing the sealing performance of the radial sealing sheet. Following all aspects of the general embodiment (Embodiment 1), except that the edge profile of the herringbone groove 101 is a hybrid edge profile (i.e., combining straight lines, arcs, spirals, and serrated edges on the same radial sealing sheet), all other design components and parameters remain unchanged. The hybrid edge profile double-layer herringbone groove 101 solution provided in this embodiment is suitable for complex sealing scenarios requiring multiple effects, such as comprehensive sealing needs under various operating conditions.

[0233] The sealing principle of the hybrid edge-line type mainly involves forming a liquid film, increasing the sealing pressure differential, generating turbulence, and achieving a uniform pressure distribution. Specifically, forming a liquid film occurs during the sealing process, where the fluid forms a liquid film at the edge of the herringbone groove 101. The presence of this liquid film fills the sealing gap, reducing leakage channels and thus improving sealing performance. The liquid film also provides a uniform pressure distribution, ensuring the integrity and stability of the sealing surface. Specifically, increasing the sealing pressure differential occurs because the serrated section, through its special shape, generates a local pressure drop as fluid passes through, thereby increasing the pressure difference across the sealing surface. This pressure difference helps improve the sealing effect because a larger pressure difference can effectively prevent fluid leakage. Specifically, generating turbulence occurs because the design of the arc and spiral sections creates turbulence near the sealing surface. Turbulence increases the fluid's energy dissipation, reducing the possibility of leakage. Furthermore, turbulence can disrupt the laminar flow state of the fluid, further improving the sealing effect.

[0234] The uniform pressure distribution, achieved through a rationally designed mixed edge profile, ensures a more uniform pressure distribution in the liquid film, preventing excessively high or low local pressures. This uniform pressure distribution enhances the stability and reliability of the seal, reducing the risk of seal failure. Specifically, in the mixed edge profile design of the herringbone groove 101, straight edge profiles, curved edge profiles, spiral edge profiles, and serrated edge profiles can be combined to enhance the effect. Specifically, the combination of straight and curved lines creates alternating straight and curved lines at the edge of the herringbone groove 101; the straight sections provide a stable seal, while the curved sections increase the elasticity and adaptability of the seal. Specifically, the combination of straight and spiral lines creates a spiral sealing line on the sealing surface, enhancing the sealing effect; the presence of the spiral line increases fluid turbulence, improving seal reliability. Specifically, the combination of curved and serrated lines creates a complex profile at the edge of the herringbone groove 101; the curved sections provide better sealing performance, while the serrated sections increase the pressure differential, improving seal stability.

[0235] By combining different edge profiles, uniform pressure distribution and negative pressure effect can be achieved across the entire radial seal, ensuring stable sealing performance. Specifically, the combination of curved and straight edge profiles smoothly guides airflow, reducing airflow turbulence and stress concentration, thereby reducing wear on the radial seal. Conversely, the combination of spiral and serrated edge profiles significantly enhances the pressure difference and turbulence effects of the airflow, improving sealing performance and adsorption capacity. Finally, the hybrid edge profile design allows the radial seal to adapt to various operating conditions, improving its versatility and adaptability.

[0236] In terms of radial sealing sheet processing, the design of mixed edge lines can be optimized according to specific application scenarios, adjusting the proportion and layout of various edge lines to achieve the best sealing effect; laser processing technology can accurately realize the design of mixed edge lines, ensuring that the groove depth and shape of each pair of grooves are consistent, thus guaranteeing a high-quality sealing effect.

[0237] In terms of application scenarios, the hybrid edge profile design is suitable for complex sealing scenarios requiring multiple effects. The hybrid edge profile provides stronger sealing force and stability, making it suitable for demanding industrial applications. Specifically, under high-pressure conditions, the serrated and straight sections can provide sufficient structural strength and sealing pressure differential. Specifically, under high-speed conditions, the curved and spiral lines can enhance turbulence and reduce leakage. Specifically, under high-temperature conditions, the combination of different profiles can adapt to material expansion and contraction caused by temperature changes, maintaining sealing performance.

[0238] The working principle of the radial sealing surface microtexture of the cycloidal rotor engine described in this invention is as follows:

[0239] Firstly, the design and working principle of the double-layer herringbone groove 101

[0240] The double-layer herringbone groove 101 is designed on the surface of the radial sealing sheet, with two layers of herringbone grooves 101 located at different heights or depths. This layered distribution at 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 groove 101 are arranged alternately, with the opening of the upper herringbone groove 101 aligned with the middle of the lower herringbone groove 101. This alternating arrangement increases the complexity of gas flow and the diversity of paths. Therefore, the double-layer herringbone groove 101 provides multiple sealing barriers, requiring the gas to pass through multiple complex paths to leak out. The double-layer structure allows for a more uniform distribution of negative pressure adsorption on the surface of the radial sealing sheet, reducing the problem of excessive or insufficient local pressure, thereby effectively reducing the vibration (beating) phenomenon of the radial sealing sheet.

[0241] In terms of its herringbone shape, each layer of the double-layer herringbone groove 101 has a herringbone shape, i.e., a V-shaped structure. The opening direction matches the rotation direction of the rotor, ensuring that gas can smoothly enter the groove. The two sides of the herringbone groove 101 are symmetrical, ensuring a balanced gas flow path. The symmetrical structure maintains consistency in both the upper and lower layers, forming a stable pressure gradient. Therefore, the geometry of the herringbone groove 101 (such as straight lines, arcs, spirals, serrated lines, 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 fluid flow path and pressure difference, and can be adjusted and optimized according to actual conditions.

[0242] As the rotor rotates, gas enters the grooves through the openings of the herringbone grooves 101, and the gas flow begins. The upper herringbone groove 101 receives the gas first, and the gas flows along a V-shaped path, then alternately enters the lower herringbone groove 101. Due to the staggered arrangement of the upper and lower herringbone grooves 101, the gas flow path within the grooves becomes complex. This complex path helps increase the resistance to gas flow, thereby creating different pressure gradients within the grooves.

[0243] Based on gas lubrication theory, the design reduces friction and enhances sealing by forming a gas film between the radial seal and the rotor. The double-layer herringbone groove 101 design, based on gas lubrication theory, optimizes gas flow and pressure distribution through a complex groove structure. The complexity of the gas flow path and the formation of the pressure gradient create a negative pressure effect within the groove, thereby enhancing the adsorption force between the radial seal and the rotor.

[0244] In terms of gas flow, the gas enters the groove through the symmetrical center line 104 of the opening 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 and lower grooves of the double-layer herringbone groove 101 are arranged alternately, and the gas first enters the upper herringbone groove 101, and then enters the lower herringbone groove 101 along the alternating flow path, forming a complex flow path;

[0245] In terms of pressure changes, due to the different geometries and flow resistance at different locations within the tank, different pressure zones are formed when the gas flows within the tank. The herringbone design and double-layer structure of the tank cause the gas to continuously change direction and speed during flow, generating different pressure gradients. Each layer of the double-layer structure can generate an independent pressure gradient, and the staggered arrangement of the upper and lower herringbone grooves 101 causes these gradients to superimpose, forming a more complex and stable pressure change.

[0246] From the perspective of negative pressure effect, due to the pressure gradient within the groove, the gas forms a negative pressure region at certain locations; the negative pressure effect causes an adsorption force between the radial sealing sheet and the rotor; the negative pressure effect makes the radial sealing sheet fit more tightly against the rotor surface, reducing gas leakage; furthermore, in the double-layer structure, the negative pressure effects of the upper and lower herringbone grooves 101 are superimposed, forming a double-layer superposition effect of negative pressure, making the overall negative pressure effect more significant and enhancing the tightness of the radial sealing sheet.

[0247] From the perspective of 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 within the grooves, the gas will form different flow paths and velocities within the grooves. Because the flow paths and velocities differ at different points within the grooves, different pressure distributions will form at different locations within the grooves. The pressure difference effect arises from the pressure difference at different locations within the grooves; this pressure difference causes gas to flow from high-pressure areas to low-pressure areas. Typically, the pressure is higher at the corners within the grooves and lower in other areas. This pressure difference leads to the formation of negative pressure areas within the grooves. These negative pressure areas generate adsorption forces, tightly adhering the radial sealing plate to the rotor surface, thereby enhancing the sealing effect and reducing the vibration and movement of the radial sealing plate.

[0248] From the perspective of fluid viscosity effects, the double-layer herringbone groove 101 design consists of two herringbone groove structures 101 on the radial sealing surface. The fluid viscosity effect occurs when gas flows through the herringbone groove 101; the groove walls impede the gas flow. Specifically, within the boundary layer formed near the groove walls, the gas flow velocity is lower, while the velocity is higher in the central region, creating a velocity gradient. This viscosity effect further enhances the pressure difference effect within the groove. This design increases the complexity of the fluid path within the groove, further enhancing the pressure difference and viscosity effects, thereby improving the adsorption force and sealing effect.

[0249] Secondly, the design and working principle of the sealing weir area 102.

[0250] The sealing weir area 102, which is a grooveless area between two adjacent pairs of herringbone grooves 101, is designed with a smooth surface without any thinning or grooving. The smooth surface of the sealing weir area 102 forms a continuous sealing barrier, preventing gas leakage through the gaps between the herringbone grooves 101 inside the radial sealing sheet.

[0251] The sealing weir area 102 has no grooves, preventing gas flow and thus stopping gas leakage. The sealing weir area 102 creates multiple continuous groove-free areas on the radial sealing sheet, which work together to further improve the overall sealing performance of the radial sealing sheet.

[0252] The sealing weir area 102 can balance the pressure distribution on the radial sealing sheet, reduce the phenomenon of local pressure concentration, thereby reducing the vibration phenomenon of the radial sealing sheet and improving the stability of the radial sealing sheet.

[0253] The sealing weir area 102 is designed with a smooth surface, which reduces friction when in contact with the rotor surface, thereby reducing wear. Because the sealing weir area 102 reduces friction and wear, the radial seal can maintain its long-term use under high pressure and high temperature environments, reducing the need for frequent replacements and extending the service life of the radial seal.

[0254] Thirdly, the design and working principle of the sealed dam area 103.

[0255] The sealing dam area 103 is the ungrooved area outside the herringbone groove 101. The sealing dam area 103 is not thinned, and compared to the grooved area, it retains the original thickness, strength, and material integrity of the radial sealing sheet, giving the radial sealing sheet higher compressive strength and structural stability in the sealing dam area 103. When high-pressure gas impacts the radial sealing sheet, the sealing dam area 103, due to its greater thickness and strength, can effectively resist deformation, preventing overall or partial structural damage to the sealing dam area 103.

[0256] The sealing dam area 103 is set at a critical position in the gas flow path, and is evenly distributed along the edge of the radial sealing sheet, covering the critical area of ​​the radial sealing sheet, especially the part of the gas flow path that is prone to impact.

[0257] The sealing dam area 103 disperses the impact force of high-pressure gas over a larger area, reducing local stress concentration. The stress dispersion formed by the sealing dam area 103 can prevent deformation and damage to the radial sealing sheet due to excessive local stress. When the cycloidal rotor engine is running, during the flow of high-pressure gas, the sealing dam area 103, as the first line of defense, can absorb and mitigate some of the impact energy, protecting the subsequent sealing structure.

[0258] Fourth, the layout (coordination) and working principle of the sealing weir area 102 and the sealing dam area 103.

[0259] (1) Coordination of sealing function between sealing weir area 102 and sealing dam area 103

[0260] The sealing weir 102 prevents gas leakage inside the radial sealing strip through its grooveless design, while the sealing dam 103 provides an additional layer of sealing through its location and thickness, preventing gas leakage from outside the radial sealing strip. Therefore, the sealing weir 102 and the sealing dam 103 together form a multi-layered sealing barrier.

[0261] The smooth surface of the sealing weir area 102 is evenly distributed on the radial sealing sheet, which helps to distribute the pressure borne by 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.

[0262] (2) Coordination of the supporting functions of the sealed weir area 102 and the sealed dam area 103

[0263] The combination of the sealing weir region 102 and the sealing dam region 103 makes the radial sealing sheet more stable when subjected to high-pressure gas impact. The sealing weir region 102 provides basic support, while the sealing dam region 103 further enhances the overall stability of the radial sealing sheet by increasing its thickness and strength.

[0264] The grooveless design of the sealing weir area 102 reduces wear, while the strength and thickness of the sealing dam area 103 improve wear resistance and impact resistance. Together, they can significantly extend the service life of the radial sealing sheet.

[0265] (3) From the perspective of gas flow path control, the coordination between the sealing weir area 102 and the sealing dam area 103

[0266] When gas flows into the herringbone groove 101, the sealing weir area 102, as a groove-free area, blocks the direct flow of gas inside the radial sealing sheet. Therefore, the sealing weir area 102 effectively prevents gas from leaking out from inside the radial sealing sheet, ensuring the integrity of the seal.

[0267] The sealing dam area 103 is located outside the herringbone groove 101, forming an additional sealing barrier. This barrier effectively blocks gas from seeping in from the outside, further enhancing the sealing effect. Even if there are some minor leaks in the herringbone groove 101 area, the sealing dam area 103 can block these gases, preventing them from eventually leaking out of the sealing device.

[0268] (4) From the perspective of pressure management, the coordination between the sealing weir area 102 and the sealing dam area 103

[0269] As a grooveless, smooth contact surface, the sealing weir 102 helps to distribute pressure more evenly across the radial sealing sheet. The sealing weir 102 avoids localized stress concentration, reducing deformation or damage to the seal under high pressure. The smooth contact interface forms a buffer within the sealing weir 102, facilitating a smooth pressure transition and reducing stress peaks.

[0270] By increasing the thickness and strength of the radial sealing sheet, the sealing dam 103 provides an additional layer of pressure buffer. Even under high pressure conditions, the strength of the sealing dam 103 can withstand the pressure, preventing the radial sealing sheet from deforming or being damaged as a whole. This further improves the pressure resistance of the radial sealing microtexture described in this invention under high temperature and high pressure conditions.

[0271] Furthermore, this invention provides a comprehensive solution to the problems of vibration, leakage, and wear of radial seals in cycloidal rotor engines, as well as cylinder block vibration marks and seal failure, through the double-layer herringbone groove 101 radial seal described in this invention. The specific solution is as follows:

[0272] Firstly, regarding the vibration phenomenon of cycloidal rotor engines.

[0273] Double herringbone groove 101

[0274] Structurally, the double-layer herringbone groove 101 of this invention is formed on the surface of the radial sealing sheet. The double-layer herringbone groove 101 has a "V" shape, with its opening facing the high-pressure intake side. Its shape can be a straight line, an arc, a spiral, or a serrated line. The double-layer herringbone groove 101 has two levels of "V"-shaped grooves, allowing airflow to pass through a more complex path.

[0275] From the perspective of airflow path, the double-layer herringbone groove 101 opens on the high-pressure inlet side, allowing gas to enter the groove. When high-pressure gas flows into the double-layer herringbone groove 101 from the high-pressure side of the rotor, the geometry and complex flow channels of the double-layer herringbone groove 101 cause changes in velocity and flow path as the gas flows through the channels. The herringbone grooves 101 on the radial sealing plate are symmetrically distributed, ensuring uniform distribution of airflow as it enters and flows through the channels. The sealing weir area 102 between the grooves and the sealing weir area enhance the sealing effect.

[0276] The upper herringbone groove 101 has an opening on the high-pressure inlet side, allowing gas to enter the groove. 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 airflow velocity slows down, and the pressure increases, forming a high-pressure zone. As the airflow moves within the groove, in the middle of the upper herringbone groove 101, the gas continues to flow, and the flow path gradually becomes smoother, the velocity increases, and the pressure decreases, creating a pressure difference within the groove and forming a low-pressure zone. At the corners within the upper herringbone groove 101, the gas flow direction changes, the velocity decreases, and the pressure increases, forming a local high-pressure zone. At the outlet of the upper herringbone groove 101, the gas approaches the outlet area, the velocity further increases, and the pressure decreases, creating a pressure difference within the groove and forming a low-pressure zone. In the lower groove, similar to the upper herringbone groove 101, the airflow also experiences changes in velocity and pressure, forming more high-pressure and low-pressure zones. The double-layer herringbone groove 101 structure creates 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.

[0277] Due to the double-layer herringbone channel 101 structure, a significant pressure difference is generated between the high-pressure zone and the low-pressure zone, resulting in a negative pressure area within the channel. The high-pressure zone is mainly located at the inlet and corners within the channel, while the low-pressure zone is mainly located in the middle and outlet areas of the channel.

[0278] High-pressure regions typically appear in areas where gas flow is obstructed or the flow rate is low, such as the inlet region and corners of the double-layer herringbone channel 101. In the inlet region of the double-layer herringbone channel 101, when gas first enters the channel, the flow rate decreases due to obstruction by the channel walls, resulting in increased pressure. At the corners of the channel (or in areas with significant changes in corners or curvature), the gas flow direction changes, the flow rate decreases, and the pressure increases. These corners form localized high-pressure regions. Low-pressure regions typically appear in areas where gas flow is relatively smooth and the flow rate is high, such as the middle and outlet regions of the double-layer herringbone channel 101 and specific locations within the channel. In the middle and outlet regions of the double-layer herringbone channel 101, gas flows through the inlet into the middle of the channel; as the flow path lengthens, the flow rate increases and the pressure decreases. Especially in areas where the channel narrows or a nozzle effect is formed, the flow rate further increases and the pressure further decreases. At specific locations within the channel, due to the channel's geometry and complex gas flow paths, the flow velocity in some areas will be significantly higher than in other areas, thus forming a low-pressure zone.

[0279] When the pressure in the low-pressure region is significantly lower than that in the high-pressure region, a negative pressure region is formed. The negative pressure in the low-pressure region generates an adsorption force, tightly adhering the radial sealing sheet to the rotor surface. The adsorption force is an inward suction force that acts on the entire surface of the radial sealing sheet, ensuring close contact between the radial sealing sheet and the rotor surface. The double-layer herringbone groove 101 structure creates a continuous adsorption effect, ensuring the uniform distribution and continuous action of the negative pressure adsorption force across the entire surface of the radial sealing sheet.

[0280] Due to the fixing effect of the negative pressure adsorption force, the radial sealing strip is fixed to the rotor surface during operation, reducing its free vibration and movement. The negative pressure adsorption force effectively suppresses the vibration and impact of the radial sealing strip, thereby suppressing the tapping phenomenon. The negative pressure adsorption force ensures a tight fit between the radial sealing strip and the rotor surface, reducing gas leakage. The double-layer herringbone groove 101, while guiding airflow and forming negative pressure, optimizes the contact surface between the radial sealing strip and the rotor, further improving the radial sealing performance.

[0281] Secondly, regarding the cylinder block vibration pattern of the cycloidal rotor engine.

[0282] Double herringbone groove 101

[0283] As shown in Figure 4, the double-layer herringbone groove 101 features an axisymmetric design and a uniformly distributed groove structure. By optimizing the airflow path and pressure distribution, it effectively solves the cylinder vibration pattern problem. The axisymmetric design ensures a uniform distribution of airflow and adsorption force, reducing the vibration pattern problem caused by asymmetrical design; the uniformly distributed groove structure ensures that the radial sealing sheet is evenly stressed, avoiding local stress concentration, thereby mitigating the cylinder vibration pattern phenomenon.

[0284] The double-layer herringbone groove 101 structure is symmetrically distributed along the center line of the radial sealing sheet, forming an axisymmetric structure; the axisymmetric design ensures that when the radial sealing sheet contacts the rotor surface, the airflow flows uniformly in all directions, forming uniform negative pressure and adsorption force.

[0285] The double-layer herringbone groove 101 forms an axisymmetric design.

[0286] From the perspective of balancing airflow pressure, the axisymmetric design of the double-layer herringbone groove 101 creates a symmetrical pressure distribution when the airflow flows across the radial sealing surface. This symmetrical pressure distribution avoids localized high-pressure areas caused by asymmetrical design. Furthermore, the symmetrical pressure distribution reduces localized high pressure and stress concentration, thereby preventing the formation of vibration marks. Uniform stress distribution significantly reduces wavy wear on the cylinder block surface.

[0287] From the perspective of uniform adsorption force, the axisymmetric structure ensures that the airflow is evenly distributed on the surface of the radial sealing plate, and the negative pressure adsorption force is also evenly distributed. This uniform adsorption force ensures stable contact between the radial sealing plate and the rotor surface, reducing wear caused by vibration and uneven friction. Furthermore, the uniform adsorption force reduces irregular movement and relative sliding between the radial sealing plate and the rotor surface, preventing excessive localized wear caused by vibration, thereby reducing vibration marks.

[0288] From the perspective of airflow path, when 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 both the left and right directions upon entering the groove. The airflow flows along a symmetrical path within the groove, preventing excessive pressure accumulation on any one side. As the airflow moves within the groove, the axisymmetric design ensures that the airflow follows the symmetrical path of the herringbone groove 101. The two arms of the herringbone groove 101 are symmetrically distributed, causing the airflow to split into two streams within the groove, flowing along the two arms of the "V" shape respectively. This symmetrical design results in a uniform pressure distribution within the groove, preventing the formation of localized high-pressure areas.

[0289] Furthermore, the airflow path goes through three stages: entering the double-layer herringbone groove 101 from the high-pressure zone, airflow within the groove, and airflow transfer between the grooves. When the airflow enters the herringbone groove 101 from the high-pressure zone, due to the axisymmetric design of the herringbone groove 101, the airflow is evenly distributed to the left and right directions upon entering the groove; the airflow flows along a symmetrical path within the groove, and the symmetrical flow does not create excessive pressure accumulation on one side; when the airflow flows within 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 within the groove, flowing along the two arms of the "V" shape respectively. Due to the symmetrical design, the airflow forms a uniform pressure distribution within the groove, avoiding the generation of local high-pressure areas. When the airflow moves between the grooves, it 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 a symmetrical path, and the airflow will not deviate laterally, thus preventing excessive pressure accumulation on one side.

[0290] Furthermore, the reduction in cylinder block vibration marks is attributed to the axisymmetric design of the double-layer herringbone groove 101, primarily through balancing airflow pressure and uniform adsorption force. Regarding balancing airflow pressure, the axisymmetric design of the double-layer herringbone groove 101 creates a uniform, symmetrical pressure distribution as the airflow flows over the radial sealing plate surface, avoiding localized high-pressure areas caused by asymmetrical design. This uniform pressure distribution reduces stress concentration, thus preventing the formation of vibration marks. Regarding uniform adsorption force, the axisymmetric design of the double-layer herringbone groove 101 creates a uniform negative pressure adsorption force on the radial sealing plate surface, ensuring stable contact between the radial sealing plate and the rotor surface. This uniform negative pressure adsorption force reduces 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 ensures a symmetrical airflow path, avoiding localized high-pressure areas and stress concentration, thus reducing the formation of cylinder block vibration marks. Through scientific and rational airflow management within the cylinder block, the cylinder block vibration mark problem is effectively solved, extending the engine's service life.

[0291] The double-layer herringbone groove 101 is evenly distributed along the axial direction.

[0292] The double-layer herringbone grooves 101 are evenly distributed along the axial direction, ensuring that each groove is uniformly arranged on the surface of the radial sealing plate, thus guaranteeing that airflow and pressure are evenly distributed across the entire surface of the radial sealing plate. The evenly distributed groove design allows the radial sealing plate to be evenly stressed during operation, avoiding local stress concentration and thereby reducing the formation of cylinder vibration marks.

[0293] Uniform stress distribution: The uniformly distributed groove design allows the radial seal to be subjected to uniform stress during operation, avoiding local stress concentration and thus reducing the formation of cylinder vibration marks.

[0294] From the perspective of uniform stress distribution, the uniformly distributed double-layer herringbone groove 101 structure ensures that the radial seal is subjected to uniform stress during operation, preventing the formation of local high-stress areas. This uniform stress distribution reduces stress concentration and lowers the probability of cylinder block vibration marks. Due to the uniform stress distribution, the radial seal is under balanced stress throughout the entire operation process, reducing the possibility of excessive local wear, thereby reducing the phenomenon of vibration marks on the cylinder block surface. With the uniformly distributed double-layer herringbone groove 101 design, each groove bears similar pressure and stress, and the radial seal is subjected to uniform stress overall. The uniform stress distribution reduces the possibility of wavy wear on the cylinder block surface, thereby reducing the formation of cylinder block vibration marks.

[0295] From the perspective of optimizing airflow path management, the uniformly distributed channels make the airflow path more complex and uniform, so that the airflow will not concentrate in a certain area and form an impact force. The turning and dispersion of the airflow in the channels reduces the concentrated impact of the airflow on a certain area, thereby reducing the impact of the airflow on the radial seal. The uniform airflow management makes the airflow flow more smoothly in the channels, reducing the vibration and wear caused by the airflow, thereby further preventing the formation of cylinder block vibration marks.

[0296] Thirdly, regarding the air leakage phenomenon of the cycloidal rotor engine.

[0297] Double herringbone groove 101

[0298] As mentioned above, as shown in Figure 5, the geometric design of the double-layer herringbone groove 101 results in a complex gas flow path within the groove, leading to varying velocity and pressure distributions. At the groove inlet, airflow is obstructed, creating a high-pressure zone; in the middle and at the outlet, the airflow velocity increases, creating a low-pressure zone. Gas entering the opening area of ​​the double-layer herringbone groove 101 from the high-pressure side experiences a decrease in velocity and an increase in pressure, again forming a high-pressure zone. As the gas flows along the groove, the airflow accelerates, and the pressure decreases, creating a low-pressure zone. The pressure difference between the high-pressure and low-pressure zones creates a negative pressure in the low-pressure zone. The negative pressure in the low-pressure zone attracts the radial sealing plate to the rotor surface, ensuring tight contact between the radial sealing plate and the rotor surface. The double-layer herringbone groove 101 forms an effective differential pressure seal, reducing gas leakage.

[0299] In the double-layer herringbone groove 101, both the upper and lower grooves have several pairs of herringbone grooves 101 on the radial sealing surface, with the upper and lower grooves arranged alternately. Airflow simultaneously enters from the inlet of the upper herringbone groove 101 and the inlet of the lower herringbone groove 101, flowing along the two arms of the herringbone groove 101. Each path adjustment and turn increases the airflow resistance, making the overall airflow path tortuous and complex.

[0300] The complex airflow path mainly involves three stages: initial path, flow within the upper and lower channels, and path adjustment during channel transfer.

[0301] When the airflow is in the initial path, the high-pressure gas first enters the opening of the upper herringbone groove 101.

[0302] As the airflow moves within the upper slot, it undergoes both channel flow and branching flow. Channel flow occurs when the airflow follows a "V"-shaped path within the upper slot; due to the structure of the herringbone slot 101, the airflow needs to constantly change direction within the slot, making the flow path tortuous. Branching flow occurs when the airflow splits into two streams within the two arms of the herringbone slot 101, each spreading outward along one of the arms of the slot 101.

[0303] As the airflow moves within the lower channel, it undergoes a new flow path and an alternating arrangement. The new flow path involves the airflow following a new "V"-shaped path, continuing to experience similar turning and branching flows as in the upper channel. The alternating arrangement arises because the lower and upper channels are interleaved, requiring the airflow to undergo complex turning and adjustments upon entering the lower channel, further complicating the flow path.

[0304] Furthermore, the flow paths of the airflow in both the upper and lower herringbone grooves 101 are as follows:

[0305] (1) Airflow inlet: Airflow enters from the openings of the upper and lower troughs (upper air inlet 201 and upper air outlet 203);

[0306] (2) Airflow path 1: The airflow flows along the two arms of the herringbone groove 101;

[0307] (3) Airflow path 2: Inside the channel, the airflow continues to flow along both arms until the end of the channel;

[0308] (4) Airflow convergence point: The airflow converges at the end of the slot (lower air inlet 202 and lower air outlet 204).

[0309] In summary, the design of the double-layered herringbone channel 101 increases the complexity of the airflow path by adding more turning and path adjustments within the channel. The airflow undergoes multiple turns and branching flows within the upper and lower herringbone channels 101. From the inlets of the upper and lower herringbone channels 101, the airflow flows along the two arms of the herringbone channels 101, experiencing similar turns and branching flows again. Each path adjustment and turn increases airflow resistance, making the overall airflow path tortuous and complex. The staggered double-layered channel design requires the airflow to pass through multiple intersecting areas during path adjustments, further increasing the complexity of the flow path.

[0310] The sealing weir area 102 prevents leakage between the grooves on the radial sealing plate.

[0311] From the gas flow path, gas always attempts to flow from high-pressure areas to low-pressure areas via different paths. Especially on the radial sealing plate, the grooves are potential escape routes for gas. The sealing weir area 102, located between the double herringbone grooves 101 (between the grooves), is a continuous surface without grooves, forming a groove-free area. This ensures that the sealing weir area 102 has no grooves or gaps, preventing gas from escaping through it. Because the sealing weir area 102 has no grooves, when gas attempts to leak through these areas, it encounters a continuous surface with no path to follow. The sealing weir area 102 forms a continuous, uninterrupted plane, preventing gas flow through these areas. The sealing weir area 102 utilizes the control of the gas flow path to ensure that gas can only flow within specific channels and cannot leak through the groove-free areas of the radial sealing plate. This enhances the overall sealing performance of the radial sealing plate.

[0312] The sealing dam area 103 prevents leakage from the outer edge of the radial sealing strip.

[0313] The sealing dam area 103 is located at the outer edge of the herringbone groove 101 and is the groove-free area on the outer side of the radial sealing strip. Since the sealing dam area 103 has no groove, it means there are no openings or interruptions on the outer edge of the radial sealing strip, forming a continuous, complete, and smooth sealing interface that prevents gas leakage. The sealing dam area 103 acts as an additional barrier layer on the radial sealing strip, effectively adding an extra barrier to prevent gas from easily leaking or escaping through the outer edge of the radial sealing strip. This effectively seals the outer edge of the radial sealing strip.

[0314] As gas flows under high pressure into the herringbone groove 101, it may seek a path to escape from the outer edge of the radial seal. Since the sealing dam area 103 is located at the outer edge of the radial seal and has no grooves, these areas form a natural barrier, effectively preventing gas leakage. The grooveless design of the sealing dam area 103 utilizes the control of the gas flow path to ensure that gas can only flow within specific channels and cannot leak through the outer edge of the radial seal. Therefore, the sealing dam area 103 maintains the airtightness of the radial seal edge, preventing gas from escaping from the outer edge, thereby enhancing the edge sealing effect.

[0315] In the design of the double-layer herringbone groove 101, the sealing weir area 102 and the sealing dam area 103 form a combined seal.

[0316] The sealing weir area 102 is located in the grooveless area between the herringbone grooves 101, preventing gas leakage between the grooves. The sealing dam area 103 is located in the grooveless area at the outer edge of the herringbone groove 101, preventing gas leakage from the outer edge of the radial sealing strip.

[0317] Specifically, neither the sealing weir area 102 nor the sealing dam area 103 has grooves, forming a continuous groove-free region. This creates multiple layers of protection for each part of the radial sealing sheet, making it difficult for gas to 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 utilizes the combination of the groove-free region and the additional barrier layer to ensure that gas encounters the barrier of the groove-free region at any possible leakage path, thus preventing easy leakage and achieving a highly efficient radial sealing effect.

[0318] In the design of the double-layer herringbone groove 101, the grooveless design of the sealing weir area 102 and the sealing dam area 103 complements each other to form four sealing layers. Details are as follows:

[0319] (1) First sealing layer: upper herringbone groove 101;

[0320] (2) Second sealing layer: sealing weir area 102;

[0321] (3) Third sealing layer: lower herringbone groove 101;

[0322] (4) Fourth sealing layer: sealing dam area 103.

[0323] The opening of the upper herringbone groove 101 faces the high-pressure side, and the high-pressure gas first enters these grooves; the complex flow path in the grooves increases the airflow resistance, forming a preliminary pressure difference effect and negative pressure adsorption force, and begins to seal the gas (preliminary sealing).

[0324] The sealing weir area 102 is located between the upper herringbone grooves 101 and is a continuous surface without grooves. The grooveless area formed by the sealing weir area 102 prevents gas from passing between the grooves, further blocking gas leakage. The sealing weir area 102 forms an intermediate seal, ensuring that even if a small amount of gas leaks in the upper channel, it cannot enter the adjacent channel through the sealing weir area 102, thus ensuring the airtightness between the channels.

[0325] The lower herringbone groove 101 is located below or intersects with the upper groove. After passing through the upper groove, the high-pressure gas enters the lower groove. The lower groove branches out into another complex flow path, further increasing the airflow resistance and pressure difference effect, forming a stronger negative pressure adsorption force, further sealing the gas, and forming a deep seal.

[0326] The sealing dam area 103 is located at the outer edge of the double-layer herringbone groove 101 and is a groove-free continuous surface. The groove-free area formed by the sealing dam area 103 acts as a last line of defense, providing an additional barrier layer to prevent gas from escaping from the outer edge of the radial sealing sheet. Even if gas leaks in the first few layers of sealing, the sealing dam area 103 can prevent the final gas leakage, achieving edge sealing.

[0327] Multiple sealing layers, through the ingeniously designed double-layer herringbone groove 101, sealing weir area 102, and sealing dam area 103, form a comprehensive sealing system. Each layer increases the resistance to airflow and the complexity of the flow path, blocking and adsorbing gas layer by layer to ensure a high degree of sealing effect.

[0328] Fourth, regarding the wear phenomenon of cycloidal rotor engines.

[0329] This invention, through the selection of preferred materials (silicon carbide or cemented carbide), precise design of the herringbone groove 101 (including the structure, depth, and geometric parameters of the double-layer groove), and laser processing technology (high precision and smooth surface), enables the double-layer herringbone groove 101 radial sealing sheet to significantly reduce wear, enhance sealing effect, and improve the operational stability and service life of the radial sealing sheet. The combination of these technologies allows the radial sealing sheet to maintain good performance even under high-load, high-friction environments, reducing wear and extending engine life.

[0330] The micron-level groove depth and the microtexture formed by multiple channels fully utilize the superior characteristics of microtexture, effectively optimizing airflow path and pressure distribution, reducing wear, improving the service life of radial seals and the overall performance of cycloidal rotor engines.

[0331] Double herringbone groove 101

[0332] The geometric parameters of the double-layer herringbone groove 101 are groove depth 1-5 and quantity 2-10 pairs of double-layer herringbone grooves 101.

[0333] The groove depth range of the double-layer herringbone groove 101, from 1 to 5 μm, is at the micrometer level, sufficient to create a significant pressure difference effect and negative pressure adsorption force, thereby enhancing the sealing effect. The micrometer-level groove depth allows for a finer and more uniform pressure distribution when airflow passes through the groove, reducing the formation of local high-pressure areas and lowering the risk of wear caused by stress concentration. The micrometer-level groove depth also reduces excessive material weakening, ensuring the structural integrity of the radial sealing sheet under high load conditions. This also allows the radial sealing sheet to maintain good mechanical properties and durability during long-term operation, reducing wear. From the perspective of micro-channels, the double-layer herringbone groove 101, as a micro-texture, forms fine channels on the surface of the radial sealing sheet with a groove depth of 1-5 μm. These channels can significantly change the flow characteristics of the airflow, enhancing the hydrodynamic effect. From the perspective of negative pressure adsorption, the micro-texture formed by the double-layer herringbone groove 101 with a groove depth of 1-5 μm can generate a stable negative pressure adsorption force when airflow passes through, ensuring a tight fit between the radial sealing sheet and the rotor surface, reducing wear caused by vibration.

[0334] The number of double-layer herringbone grooves 101, ranging from 2 to 10 pairs, creates multiple complex paths for airflow on the radial sealing surface. These microtextured paths (2-10 pairs of double-layer herringbone grooves 101) optimize airflow distribution, reduce concentrated impact on a single path, enhance negative pressure adsorption, ensure stable contact between the radial sealing surface and the rotor, and reduce relative movement and wear caused by vibration. Multiple microtextured layers provide a multi-layered protection mechanism; even if one groove is worn, other grooves can still function effectively, extending the overall service life of the radial sealing sheet. Simultaneously, the 2-10 pairs of double-layer herringbone grooves 101 can agitate the airflow, causing it to continuously change direction and adjust between different grooves, increasing flow resistance and pressure variations, further enhancing the sealing effect. Multiple grooves result in a more uniform stress distribution on the radial sealing surface, avoiding stress concentration problems that easily occur in single-groove designs and reducing localized wear. Therefore, the 2-10 pairs of double-layer herringbone grooves 101 form multiple fine flow channels on the radial sealing surface. These flow channels work together to optimize the airflow path and improve the hydrodynamic performance.

[0335] From a pressure distribution perspective, the double-layer herringbone groove 101 creates a pressure difference in the airflow within the groove, forming a negative pressure in the low-pressure area, which adsorbs the radial sealing plate onto the rotor surface. The microtexture of the double-layer herringbone groove 101 guides the airflow, resulting in different pressure distributions within the groove. The low-pressure area generates a negative pressure, adsorbing the radial sealing plate onto the rotor surface. The resulting negative pressure adsorption force ensures a stable fit between the radial sealing plate and the rotor surface, reducing frictional wear caused by vibration.

[0336] From the perspective of negative pressure adsorption, the microtexture of the double-layer herringbone groove 101 causes the airflow to encounter more resistance and deflection when flowing within the groove, forming local high-pressure and low-pressure regions, thus enhancing the negative pressure effect. The negative pressure adsorption force ensures that the radial sealing plate is tightly fitted to the rotor surface, reducing relative movement caused by vibration. This tight fit reduces the relative movement between the radial sealing plate and the rotor surface, lowering the wear rate.

[0337] Sealed weir area 102

[0338] As part of the microtexture, the sealing weir region 102 significantly reduces the impact of airflow on the radial sealing sheet through its grooveless, smooth design. The sealing weir region 102 remains smooth and continuous at the micron level, free from groove interference. Located between the herringbone grooves 101, the grooveless, continuous surface of the sealing weir region 102 provides an additional barrier, reducing the impact of airflow on the radial sealing sheet. The sealing weir region 102 is also a microtexture; its smooth surface reduces the impact of airflow on the radial sealing sheet, preventing high-pressure airflow from concentrating at certain points and reducing localized wear. The grooveless sealing weir region 102, acting as an additional barrier, reduces the impact of airflow on the radial sealing sheet. The grooveless sealing weir region 102 reduces the number of times airflow directly impacts the surface of the radial sealing sheet, reducing wear caused by high-pressure airflow; simultaneously, the grooveless sealing weir region 102 ensures uniform airflow distribution, reducing stress concentration and localized wear.

[0339] Sealed dam area 103

[0340] As part of the microtexture, the sealing dam area 103 significantly reduces the impact of airflow on the outer edge of the radial seal through its grooveless, smooth design. Located at the outer edge of the herringbone groove 101, the sealing dam area 103 is a grooveless region. Optimized at the micron level, it forms a grooveless microtextured outer region, ensuring the airtightness of the outer edge. The grooveless design of the sealing dam area 103 creates a smooth surface, reducing the direct impact of airflow on the radial seal. By reducing the direct impact of airflow, the sealing dam area 103 effectively protects the outer edge of the radial seal, reducing wear. The microtextured design of the sealing dam area 103 ensures the airtightness of the outer edge, preventing airflow from escaping from the outside of the radial seal. By preventing airflow escape, the sealing dam area 103 enhances the overall sealing effect of the radial seal, ensuring stable pressure within the cylinder. The sealing dam area 103 reduces high-pressure airflow concentration, dispersing the airflow as it passes through the radial seal, preventing high-pressure airflow from concentrating at certain points, thereby reducing localized wear. The airflow flows uniformly 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 strip and reducing wear caused by high-pressure airflow. The grooveless sealing dam area 103 reduces stress concentration by uniformly distributing the airflow, avoiding excessive wear in local areas, and ensuring the uniformity of stress distribution on the outer edge of the radial sealing strip, thereby enhancing the durability of the radial sealing strip.

[0341] The radial sealing strip's surface microtexture is made of high-hardness materials (silicon carbide and cemented carbide).

[0342] The microtexture on the surface of the radial seal plate of the cycloidal rotor engine described in this invention utilizes high-hardness materials (silicon carbide and cemented carbide). Silicon carbide possesses extremely high hardness and wear resistance, is not easily deformed, and effectively reduces wear during contact with the rotor. Cemented carbide, composed of high-hardness metal carbides and a metal binder, exhibits high wear resistance and toughness, making it suitable for use in high-friction environments. Silicon carbide and cemented carbide can withstand greater loads during operation, reducing frictional wear between the top arc of the radial seal plate and the rotor surface, thereby extending the service life of the radial seal plate and reducing replacement frequency.

[0343] Laser processing technology is used for both the materials (silicon carbide and cemented carbide). This technology allows for precise control of the shape and dimensions of the double-layer herringbone grooves 101, ensuring the uniformity and accuracy of each groove. This results in a more uniform surface for the radial sealing plate, reducing localized stress concentration and wear caused by surface unevenness. The smooth surface produced by laser processing also reduces the coefficient of friction between the radial sealing plate and the rotor, decreasing initial wear and improving the durability of the radial sealing plate during long-term operation.

[0344] The properties of high-hardness materials (silicon carbide and cemented carbide) ensure the smooth operation of the radial seals in the cycloidal rotor engine. During initial operation, the high hardness and wear resistance of the materials reduce wear between the radial seals and the rotor surface. The herringbone groove 101 design creates a pressure differential within the grooves, and the negative pressure suction force ensures a tight fit between the radial seals and the rotor surface, reducing frictional wear. During long-term operation, the synergistic effect of the high-hardness materials and the herringbone groove 101 design allows the radial seals to maintain stable performance, reducing wear caused by friction and vibration. The high precision and smooth surface achieved through laser processing further reduce wear and extend the service life of the radial seals.

[0345] This invention, through the application of microtexture design, demonstrates significant advantages in controlling the airflow path, optimizing pressure distribution, and reducing friction and wear of the radial sealing strip 101. The microtexture not only effectively reduces the coefficient of friction and wear rate but also enhances the adhesion stability between the radial sealing strip and the rotor surface, extending the service life of the radial sealing strip and improving the overall performance and reliability of the cycloidal rotor engine. The technical solution described in this invention, through micron-level precision design, fully leverages the synergistic effect of materials and structure, effectively solving the problem of radial sealing strip wear in the long term.

[0346] In summary, this invention, through the design of a reasonable sealing structure (such as a double-layer herringbone groove 101 structure, axisymmetric design, uniformly distributed groove structure, groove-free sealing weir area 102 and sealing dam area 103, etc.), can solve the problems of vibration, air leakage, wear, and cylinder block vibration marks. Furthermore, the microtexture on the radial sealing sheet described in this invention can effectively mitigate the occurrence of eccentric failure in the radial seal of a cycloidal rotor engine, ensuring 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 microtexture on the surface of a radial sealing sheet of a cycloidal rotor engine, the rotor engine comprising a rotor (4) and a stator, the stator comprising three arc-shaped sidewalls, characterized in that: The radial sealing sheet (1) has a plurality of herringbone grooves (101), a sealing weir area (102) and a sealing dam area (103) on its surface, and a rotor (4) is provided on the opposite side of the radial sealing sheet (1). The herringbone grooves (101) are evenly arranged in the circumferential and length directions in the middle area of ​​the radial sealing plate (1). Each herringbone groove (101) has an upper air inlet (201) and a lower air inlet (202) to enter as a gas inlet, and then flow into the groove. The pressure reaches the maximum value 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), realizing the 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 plate (1) contacts the rotor and optimize the gas flow path. The sealing weir area (102) is located 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 herringbone grooves (101) to achieve primary blocking and airflow control. The sealing dam area (103) is located on the outer edge of the radial sealing sheet (1) and is arranged along the rotation direction of the rotor (4). There is no physical separation between it and the double-layer herringbone groove (101), forming a continuous and seamless connection to achieve a smooth airflow transition.

2. The microtexture on the surface of the radial sealing sheet of a cycloidal rotor engine according to claim 1, characterized in that: The double-layer herringbone groove (101) is distributed on the surface of the radial sealing sheet (1), and is divided into two layers of grooves, with the upper herringbone groove (101) on the outside and the lower herringbone groove (101) on the inside. The upper and lower herringbone grooves (101) of the double-layer herringbone groove (101) can be arranged alternately to maintain the continuity of the gas flow path; The upper and lower herringbone grooves (101) of the double-layer herringbone groove (101) maintain an equal vertical distance, ensuring that each herringbone groove (101) is relatively independent, allowing the gas to flow freely between the layers. The double-layer herringbone groove (101) structure is symmetrically distributed along the symmetrical center line (104) of the radial sealing plate (1), forming an axisymmetric structure, so that when the radial sealing plate (1) contacts the surface of the rotor (4), the airflow flows uniformly 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. The gas flow pattern changes drastically in the groove, and then the gas is discharged from the upper air outlet (203) and the lower air outlet (204) and flows out. Due to the negative pressure effect, the double-layer herringbone groove (101) forms a high-pressure zone and a low-pressure zone in the groove; the high-pressure zone is mainly located in the upper air inlet (201) and the lower air inlet (202), as well as in the middle of part of the groove; the low-pressure zone 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.

3. The microtexture on the surface 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 to each other, maintaining a fixed interval and parallel relationship, extending from the edge of the radial sealing sheet (1) to the center to form multiple independent flow channels; the high-pressure gas first enters the upper herringbone groove (101), and after passing through the upper channel, the gas enters the lower herringbone groove (101), increasing the airflow resistance and pressure difference effect.

4. The microtexture on the surface of the radial sealing plate of a cycloidal rotor engine according to claim 2 or 3, characterized in that: Each herringbone groove (101) is evenly arranged on the surface of the radial sealing sheet (1), maintaining equal spacing and equidistant parallel relationship relative to other herringbone grooves (101), extending from the edge of the radial sealing sheet (1) towards the center; Each herringbone groove (101) consists of two symmetrical herringbone structures, divided into an upper herringbone groove (101) and a lower herringbone groove (101), ensuring that the gas flow path in the groove is balanced. The symmetrical structure can maintain consistency in both 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 microtexture on the surface of the radial sealing sheet of a cycloidal rotor engine according to claim 2, characterized in that: The herringbone groove (101) spacing area is located in the interval between the herringbone grooves (101), forming multiple parallel or intersecting herringbone grooves (101), each groove dividing 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 multiple 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 can actually contact the contact area of ​​the rotor (4); the herringbone groove (101) spacing area is also a small contact area formed near the edge of the groove, and the contact area is located in the high pressure area near the edge of the groove.

6. The microtexture on the surface of the radial sealing sheet of a cycloidal rotor engine according to claim 1, characterized in that: The sealing weir area (102) forms multiple continuous grooveless areas, located in the middle part between two adjacent herringbone grooves (101), and is evenly distributed along the axial direction of the radial sealing piece (1). It is 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 multiple independent sealing units. Each unit can generate effective pressure difference and negative pressure effect, and thus can 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 multiple continuous grooveless areas located on 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 grooveless area, without physical separation, directly forming a continuous seamless connection, so that the airflow can smoothly transition from the herringbone groove (101) to the sealing dam area (103), preventing gas from escaping from the outer side of the radial sealing plate (1). 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 (1). The sealing weir area (102) and the sealing dam area (103) cooperate with each other in the airflow movement, so that each part of the radial sealing sheet (1) forms 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 microtexture on the surface of the radial sealing sheet 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) work together to form a multi-layer sealing system with a total of four sealing layers, as detailed below: (1) First sealing layer (preliminary sealing): upper herringbone groove (101); (2) Second sealing layer (intermediate seal): sealing weir area (102); (3) Third sealing layer (deep seal): lower herringbone groove (101); (4) Fourth sealing layer (edge ​​seal): seal the dam area (103); The initial sealing is achieved by separating the sealing weir area (102) between each upper herringbone groove (101), so that the airflow 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 grooveless area formed by the sealing weir area (102) prevents gas from passing between the grooves, so that even if a small amount of gas leaks in the upper channel, it cannot enter the adjacent channel through the sealing weir area (102), thus achieving airtightness between the channels. The deep sealing is achieved by the lower herringbone groove (101) being located below or staggered from the upper groove, and the high-pressure gas passing through both the upper and lower grooves simultaneously, which increases the airflow resistance and pressure difference effect, forming a stronger negative pressure adsorption force. The edge seal is a sealing dam area (103) located at the outer edge of the double herringbone groove (101), forming a grooveless continuous surface; 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 piece (1); so that even if gas leaks out in the first three layers of seal, the sealing dam area (103) can prevent the final leakage of gas.

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

9. The microtexture on the surface of the radial sealing sheet of a cycloidal rotor engine according to claims 1 and 2, characterized in that: The depth of the double-layer herringbone groove (101) is 1-5μm, forming a fine flow channel on the surface of the radial sealing sheet (1); the number of double-layer herringbone grooves (101) is 2-10 pairs, so that the airflow continuously turns between multiple channels; The geometry of the double-layer herringbone groove (101) is herringbone, and the edge line of its structure is one or more of straight lines, arcs, spirals, and serrations. The spiral-shaped double-layer herringbone groove (101) is a rotating curve. The spiral edge guides the airflow along the spiral path, making the flow path more complex and enhancing the pressure difference effect and viscosity effect. The serrated double-layer herringbone groove (101) has multiple peaks and valleys, which can generate a stronger turbulence effect, enhance gas mixing and pressure difference effect, enhance the shear force of airflow, and enhance the adsorption force between the radial sealing plate and the rotor surface.

10. The microtexture on the surface of the radial sealing sheet of a cycloidal rotor engine according to claims 1-9, characterized in that: The radial sealing sheet (1) is made of silicon carbide 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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