Rotating mechanism, sealing mechanism and sealing method thereof

Abstract

The present disclosure relates to a rotary mechanism, a sealing mechanism, and a sealing method thereof. The rotary mechanism includes: a main convex rotor having a rotating disk and a piston connected to the edge of the rotating disk; an auxiliary concave rotor having a concave portion that mates with the piston; a main stator and an auxiliary stator, each accommodating the main convex rotor and the auxiliary concave rotor, respectively. A cavity serving as a cylinder is formed within the main stator along the path of piston rotation. The sealing mechanism includes a concave and / or convex first flow-blocking portion provided on the rotating disk and a first corresponding flow-blocking portion provided on the main stator that loosely mates with the first flow-blocking portion. The first flow-blocking portion has a first concave and / or convex portion on its circumferential surface, and the first corresponding flow-blocking portion has a flat structure or a first corresponding convex and / or concave portion that loosely mates with the first concave and / or convex portion on its circumferential surface. The present disclosure prevents fluid leakage in the rotary mechanism, ensures uniform force on the piston, and prevents deformation. Furthermore, the present disclosure allows for flexible implementation of various air-fuel mixing and combustion modes, thereby improving thermal efficiency and power-to-weight ratio.

Description

Technical Field

[0001] The present disclosure relates to the technical fields of internal combustion engines, expanders, compressors, pumps, etc., and in particular, to a rotating mechanism, especially an internal combustion engine, and a sealing mechanism and sealing method thereof. Background Art

[0002] An internal combustion engine is a power machine that converts thermal energy into mechanical energy by burning a mixture of air and fuel. It can be primarily categorized as a continuous combustion gas turbine, an intermittent combustion reciprocating piston internal combustion engine, and an eccentric shaft rotor internal combustion engine. Gas turbines (including turbojets, turbofans, and turboshafts) offer high speeds, high power, and a high power-to-weight ratio, but their continuous combustion results in very high fuel consumption and high manufacturing costs. Reciprocating piston internal combustion engines utilize the reciprocating motion of a piston within a single cylinder to achieve the four strokes of intake, compression, expansion, and exhaust. While these engines offer advantages such as low fuel consumption and low manufacturing costs, they also suffer from low power-to-weight ratios, low speeds, and energy waste from reciprocating motion. Both types of internal combustion engines are in large-scale production. Eccentric shaft rotor internal combustion engines have the advantages of high speed and compact size, but they also suffer from disadvantages such as high fuel consumption, poor sealing, high friction and wear, poor durability, incomplete combustion, and substandard emissions, leading to their near-discontinuation in production. Rotary engines with eccentric shafts or other types (such as rectangular pistons) have long suffered from problems of incomplete combustion and poor sealing, which have become a century-old problem hindering the development of rotary engines. Summary of the Invention

[0003] According to various embodiments of the present disclosure, a rotating mechanism and a sealing mechanism and a sealing method thereof are provided, which can solve some problems existing in the prior art, especially configuration and sealing problems that lead to incomplete combustion and fluid leakage.

[0004] According to a first aspect of the present disclosure, a sealing mechanism for a rotating mechanism is provided, the rotating mechanism comprising:

[0005] a rotor having a rotating disk;

[0006] The stator houses the rotor.

[0007] According to the present disclosure, the sealing mechanism includes: a concave and / or convex first flow blocking portion arranged on the end surface of the turntable; a convex and / or concave first corresponding flow blocking portion arranged on the inner surface of the stator and loosely matched with the first flow blocking portion; wherein the first flow blocking portion is flatly constructed on its peripheral surface or has a first concave portion and / or convex portion, and the first corresponding flow blocking portion is flatly constructed on its peripheral surface or has a first corresponding convex portion and / or concave portion that loosely matches with the first concave portion and / or convex portion.

[0008] The size of the flow block is typically much larger than that of a (labyrinth or other) seal. The flow block of the sealing mechanism disclosed herein can significantly alter the direction of working fluid leakage, significantly extending the leakage path of the working fluid. This solves the problem of insufficient sealing space in traditional rotary mechanisms and allows for the deployment of more seals and a variety of seal types along the leakage path to prevent working fluid leakage. The composite structure and the extended leakage path combined with the extensive use of multiple seals can essentially resolve the problem of working fluid leakage in rotary mechanisms.

[0009] In one embodiment of the first aspect of the present disclosure, a second concave portion and / or convex portion is partially flatly constructed or provided on the end surface of the turntable, and a corresponding second convex portion and / or concave portion, which is clearance-matched with the second concave portion and / or convex portion, and / or a brush seal and / or a lamella seal are partially flatly constructed or provided on the inner surface of the stator. The brush seal and / or lamella seal can significantly reduce fluid leakage, further improving sealing performance.

[0010] In one embodiment according to the first aspect of the present disclosure, the first recess and / or protrusion and the first corresponding protrusion and / or recess, as well as the second recess and / or protrusion and the corresponding second protrusion and / or recess, form a spiral seal and / or a labyrinth seal and / or a gap seal and / or a hole-slot seal and / or a honeycomb seal. The spiral seal provided on the flow-blocking portion drives the fluid in a direction opposite to the direction in which the working fluid leaks. The labyrinth seal and / or the hole-slot seal and / or the honeycomb seal generate a pressure drop and vortex, thereby reducing fluid leakage pressure, further suppressing fluid leakage, and improving sealing performance.

[0011] In one embodiment of the first aspect of the present disclosure, a sealing medium is provided in the gap between the turntable and the stator, including part or all of the area between the at least two flow-blocking portions. The sealing medium may be one or more of grease, lubricating fluid, magnetic fluid, and a self-lubricating material. The use of the sealing medium in the gap between the turntable and the stator can prevent fluid leakage.

[0012] In one embodiment according to the first aspect of the present disclosure, the rotor has a piston connected to the edge of the rotating disk, and the stator wraps around the piston so that a cavity serving as a cylinder is formed on the rotation path of the piston.

[0013] In one embodiment of the first aspect of the present disclosure, the turntable includes a third flow block located on the bottom and / or side of the piston, partially surrounding the piston and cylinder. This third flow block significantly alters the leakage direction and extends the leakage path, preventing the working fluid from leaking directly toward the turntable's central axis, thereby further improving sealing. In one embodiment of the present disclosure, the third flow block includes a third concave and / or convex portion on its outer surface, further enhancing sealing.

[0014] In one embodiment according to the first aspect of the present disclosure, the piston has a fourth recess on its top side. The specially designed pressure relief groove on the piston top side causes a pressure drop and vortex in the leaking gas, inhibiting gas flow to the opposite side, thereby improving sealing.

[0015] In one embodiment according to the first aspect of the present disclosure, the rotor is a main convex rotor, the stator is a main stator, the main convex rotor has a piston, and the piston is connected to the edge of the turntable. The rotating mechanism also includes an auxiliary concave rotor and an auxiliary stator for accommodating the auxiliary concave rotor. The auxiliary concave rotor has an auxiliary turntable and an annular extension surrounding the auxiliary turntable. The annular extension has a concave portion that cooperates with the piston, and the piston can be accommodated by and pass through the concave portion when rotating. In one embodiment according to the first aspect of the present disclosure, the auxiliary turntable of the auxiliary concave rotor has a concave and / or convex second flow resistance portion arranged on its end face, and the auxiliary stator has a convex and / or concave second corresponding flow resistance portion arranged on its inner surface that is gap-matched with the second flow resistance portion. In this way, the leakage direction of the auxiliary ring is greatly changed, the leakage path is greatly extended, and the problem of insufficient sealing space in traditional auxiliary rotating mechanisms is solved.

[0016] In one embodiment of the first aspect of the present disclosure, the auxiliary stator has a circumferential flow collecting groove and a flow guide groove connected thereto on its inner side. In another embodiment of the present disclosure, a flow slinging groove is provided on the main male rotor and / or the auxiliary female rotor turntable. This improves sealing performance.

[0017] In one embodiment of the present disclosure, the rotating mechanism is an internal combustion engine, an expander, a compressor, or a pump, where the pump may be, for example, a vacuum pump or a liquid pump.

[0018] According to a second aspect of the present disclosure, a rotation mechanism is provided, comprising:

[0019] A main convex rotor has a rotary disk and a piston connected to the edge of the rotary disk; a main stator accommodates the main convex rotor, wherein a cavity serving as a cylinder is formed inside the main stator on a rotation path of the piston.

[0020] In the present disclosure, the rotating mechanism includes the sealing mechanism according to the first aspect of the present disclosure. The design and advantages described above for the sealing mechanism according to the present disclosure are also applicable to the rotating mechanism according to the present disclosure.

[0021] In one embodiment according to the second aspect of the present disclosure, the rear surface of the piston with reference to its rotation direction is a plane or a concave surface; the front surface of the piston with reference to its rotation direction is a convex surface or a concave surface or a plane.

[0022] In one embodiment according to the second aspect of the present disclosure, the piston is circular, oval, or rectangular with rounded corners. The circular or oval piston allows for more complete combustion of gas within the annular or oval ring-shaped cylinder of the same shape, resulting in higher combustion efficiency. It also provides for more uniform thermal stress on the piston, preventing thermal deformation of the piston that could cause cylinder seizure.

[0023] In one embodiment of the second aspect of the present disclosure, the rotary mechanism further includes an autonomously operating sealed liquid circulation device. This sealed liquid circulation device comprises an inlet and a liquid collection portion formed on the main stator, and a guide circuit connecting the inlet portion of the low-pressure liquid flow block located above the main shaft with the liquid collection portion of the high-pressure gas flow block located below the main shaft. The liquid can be used, for example, for sealing, cooling, and lubrication. This allows the sealed liquid to be automatically circulated in a closed loop to prevent gas leakage, thereby improving sealing performance.

[0024] In one embodiment of the second aspect of the present disclosure, the rotary mechanism further includes a liquid recovery, storage, and replenishment mechanism for cooperating with the sealed liquid circulation device when the rotary mechanism is in a stopped state. The liquid recovery, storage, and replenishment mechanism includes a one-way drive mechanism, a liquid recovery and storage mechanism, and a liquid replenishment tube. This allows for closed-loop recovery of liquid that leaks into the cylinder due to various reasons after shutdown, as well as replenishment of liquid lost to volatilization and other causes to the sealed liquid circulation device.

[0025] In one embodiment according to the second aspect of the present disclosure, the rotating mechanism further includes a cylinder cut-off mechanism, which cuts off the cylinder so that the cylinder can be changed in volume as the piston rotates. In one embodiment according to the second aspect of the present disclosure, the cylinder cut-off mechanism is an auxiliary concave rotor or a card, the auxiliary concave rotor has an auxiliary turntable and an annular extension surrounding the auxiliary turntable, the annular extension has a notch that cooperates with the piston, and the cylinder is cut off by the annular extension or the card of the auxiliary concave rotor and can be changed in volume as the piston rotates. In one embodiment according to the second aspect of the present disclosure, the rotating mechanism further includes a main shaft connecting the main stator and the main convex rotor and an auxiliary shaft connecting the auxiliary stator and the auxiliary concave rotor, and a spiral portion is provided on the main shaft, and when the main shaft rotates during operation, the spiral portion drives the fluid or grease in the direction opposite to the leakage.

[0026] In one embodiment according to the second aspect of the present disclosure, the rotating mechanism includes a main gear connected to the main shaft and an auxiliary gear connected to the auxiliary shaft. The transmission ratio between the main gear and the auxiliary gear is 1:n, where n ≥ 1. The larger n, the smaller the auxiliary concave rotor. This can reduce the size and weight of the auxiliary concave rotor and improve the power-to-weight ratio of the rotating mechanism.

[0027] In one embodiment according to the second aspect of the present disclosure, the rotating mechanism includes a compression ring, which includes an air intake chamber and a compression chamber. In one embodiment according to the second aspect of the present disclosure, the compression ring also includes a valve for adjusting the air intake amount of the cylinder. Utilizing this valve, the air intake amount of the cylinder can be adjusted as needed, the compression ratio can be flexibly adjusted, and the power of the rotating mechanism can be controlled. In one embodiment according to the second aspect of the present disclosure, the rotating mechanism includes an expansion ring, which includes an expansion chamber and an exhaust chamber. In one embodiment according to the second aspect of the present disclosure, the expansion ring also includes an exhaust pipe and / or a fuel nozzle and / or a spark plug.

[0028] In one embodiment according to the second aspect of the present disclosure, the rotating mechanism includes a connecting pipe provided with a one-way valve connecting the multifunctional air chamber between the expansion chamber of the expansion ring and the compression chamber of the compression ring, which has a fuel nozzle and / or a spark plug and has multiple functions of air storage and / or air mixing and / or combustion. In this way, multiple mixing and combustion modes of air and fuel can be flexibly achieved. In one embodiment according to the second aspect of the present disclosure, the rotating mechanism injects a single or different fuel in the multifunctional air chamber through an additional fuel injection mechanism and / or in the expansion chamber through a fuel nozzle. In one embodiment according to the second aspect of the present disclosure, the rotating mechanism ignites the mixture of air and fuel in the multifunctional air chamber and / or in the expansion chamber by compression ignition or through the spark plug. In one embodiment according to the second aspect of the present disclosure, the rotating mechanism can operate intermittently as needed through sparking, and / or control the temperature of the expansion ring cylinder, which can save fuel.

[0029] In one embodiment of the second aspect of the present disclosure, the rotary mechanism further includes a one-way exhaust gas return mechanism connected between the multifunctional air chamber and the exhaust chamber, configured to partially return exhaust gas from the exhaust chamber to the multifunctional air chamber for mixing with compressed air. This improves power efficiency and exhaust gas utilization, and reduces NOx emissions.

[0030] In one embodiment according to the second aspect of the present disclosure, the rotating mechanism further comprises a fairing housing and a fan, the fairing housing at least accommodating a compression ring and / or an expansion ring and a fan, and a fan having a plurality of holes between the expansion ring and the compression ring. The profile forms an air duct in the fairing shell, guiding the air to the back of the expansion ring that is not directly blown by the fan. The fan assists in pressurizing the intake air, and the fairing shell uses the air duct to guide the airflow so that the front and back of the hot expansion ring can be cooled by air, avoiding the air flowing directly to the air inlet of the compression ring. The cold air absorbs and carries away the heat energy of the expansion ring and turns into hot air. The compression ring inhales the hot air and compresses it to participate in work, realizing a closed loop to recover the heat energy lost by the expansion ring during cooling, thereby improving thermal efficiency. At the same time, the hot air makes it easier for fuel with a higher ignition point to achieve compression ignition. In one embodiment according to the second aspect of the present disclosure, the fan, expansion ring, compression ring, and gear are connected in sequence through a main shaft.

[0031] In one embodiment according to the second aspect of the present disclosure, the rotating mechanism further includes an electromagnetic device, which includes an induction coil and a carrying portion that carries the induction coil, and a magnet disposed on the main gear. The magnet rotates relative to the induction coil, thereby generating electricity. The magnitude, direction, and frequency of the current in the induction coil are controlled so that the magnet drives the gear to rotate, thereby generating power. In one embodiment according to the second aspect of the present disclosure, the rotating mechanism further includes a piston position maintaining device, the piston position maintaining device includes a magnetic force generating mechanism fixedly disposed near the main gear and a magnet disposed on the main gear, wherein the magnetic force generating mechanism includes a magnet, a pressure relief member, a spring, and a casing. In one embodiment according to the second aspect of the present disclosure, the rotating mechanism is a hybrid power device, a range extender, an internal combustion engine, an expander, a compressor, or a pump.

[0032] According to a third aspect of the present disclosure, a method for sealing a rotating mechanism according to the above content is proposed. According to the method of the present disclosure, a sealing mechanism is provided for the rotating mechanism, the sealing mechanism comprising: a concave and / or convex first flow blocking portion provided on the end surface of the rotating disk; and a convex and / or concave first corresponding flow blocking portion provided on the inner surface of the main stator and having a clearance fit with the first flow blocking portion, wherein the first concave and / or convex portion is flatly constructed or provided on the peripheral surface of the first flow blocking portion, and the first corresponding convex and / or concave portion is flatly constructed or provided on the peripheral surface of the first flow blocking portion and has a clearance fit with the first concave and / or convex portion.

[0033] In one embodiment according to the third aspect of the present disclosure, a third flow-blocking portion is provided at the edge of the turntable, partially surrounding the bottom and / or side of the piston and the cylinder. On the inner surface of the auxiliary stator, the leaked gas is guided along the guide groove to the circumferential confluence groove away from the leakage gap so as to converge and be brought back to the cylinder by the rotation of the recessed portion. In a partial or entire area between at least two of the flow-blocking portions, a sealing medium is provided in the gap between the turntable and the stator to prevent leakage of the working fluid. The sealing liquid is allowed to autonomously return from the flow-blocking portion in the high-pressure gas area below the main shaft near the cylinder to the flow-blocking portion in the low-pressure liquid area above the main shaft near the main shaft by utilizing the pressure difference.

[0034] In one embodiment according to the third aspect of the present disclosure, a single or different fuels and / or an air and fuel mixture are injected and burned in a multifunctional air chamber and / or expansion chamber. Here, the combustion of the air and fuel mixture is carried out by spark plug ignition or by compression ignition. Therefore, the location and combustion method of the fuel injection and the combustion of the air and fuel mixture can be flexibly selected. In one embodiment according to the third aspect of the present disclosure, a fan blows external air into the fairing shell to form an air duct to guide the airflow, and the air cools the hot expansion ring. The cold air takes away the heat energy of the expansion ring and turns into hot air, which is sucked into the compression ring to participate in the work of intake compression, so that the heat energy lost by the cooling of the expansion ring is recovered in a closed loop.

[0035] In one embodiment according to the third aspect of the present disclosure, according to the operating condition plan, after the internal combustion engine completes the i-th combustion cycle, fuel injection is stopped during the subsequent i+j-th spark cycle, and exhaust gas is partially mixed with compressed air through the multi-functional chamber and returned to the expansion chamber to expand and perform work. Fuel injection is stopped during the subsequent i+j+p-th spark cycle without stopping air compression, and fuel injection and air compression are stopped during the i+j+p+q-th spark cycle, where i ≥ 1 and j, p, and q ≥ 0. In this way, the values ​​of i, j, p, and q can be adjusted to meet power requirements and fuel conservation requirements under various operating conditions.

[0036] The designs and advantages described above for the rotating mechanism and the sealing mechanism thereof according to the present disclosure are also applicable to the method according to the present disclosure. BRIEF DESCRIPTION OF THE DRAWINGS

[0037] To better understand the above and other objects, features, advantages, and functions of the present disclosure, reference may be made to the preferred embodiments shown in the accompanying drawings. Like reference numerals in the accompanying drawings refer to like components. Those skilled in the art should understand that the accompanying drawings are intended to schematically illustrate preferred embodiments of the present disclosure and have no limiting effect on the scope of the present disclosure. The components in the drawings are not drawn to scale.

[0038] Figure 1 is an overall top cross-sectional view of a rotating mechanism according to an exemplary embodiment of the present disclosure;

[0039] Figure 2 yes Figure 1 A side sectional view of the rotating mechanism;

[0040] Figure 3 is an exploded view of the rotating mechanism;

[0041] Figure 4 is a perspective view of the non-spinning housing of the rotating mechanism;

[0042] Figure 5 yes Figure 4 A front view of a fanless rotating mechanism;

[0043] Figure 6 yes Figure 5 A front view of the rotating mechanism without the rotor and the front half of the main / auxiliary stator, wherein the auxiliary stator shows an embodiment of a sling slot;

[0044] Figure 7 yes Figure 4 A front view of the rotating mechanism with the rotor but without the front half of the main / auxiliary stator;

[0045] Figure 8 is a front view of the main convex rotor and the auxiliary concave rotor of the rotating mechanism;

[0046] Figure 9 The figure shows the circumferential flow collecting groove and the flow guiding groove on the auxiliary stator of the rotating mechanism;

[0047] Figure 10 It is a partially exploded three-dimensional diagram of the rotating mechanism;

[0048] Figure 11 This is a three-dimensional diagram of the assembly of the multifunctional air chamber of the rotating mechanism;

[0049] Figure 12 yes Figure 4 A top perspective view of the rotating mechanism;

[0050] Figure 13 is a perspective view of the electromagnetic device of the rotating mechanism;

[0051] Figure 14 Shown Figure 13 Another magnetic force generating mechanism of the piston position holding device;

[0052] Figures 15A-15C This is a combined three-dimensional diagram of the main convex rotor and the auxiliary concave rotor of the rotating mechanism, which respectively shows three embodiments of the turntable: no third flow blocking portion, a third flow blocking portion in the shape of a medium wine glass, and a third flow blocking portion in the shape of a tall wine glass;

[0053] Figures 16A-16C Five different designs of the rotary disc and piston of the main convex rotor of the rotary mechanism are shown;

[0054] Figures 17A-17C Three groups of six different designs of the rotating disc of the main convex rotor of the rotating mechanism are shown;

[0055] Figure 18 is a partial cross-sectional view of the main stator and main convex rotor of the internal combustion engine;

[0056] Figures 19A-19DFour sets of eight different design embodiments of the first flow-blocking portion on the rotary disk and the first corresponding flow-blocking portion on the main stator are shown;

[0057] Figure 20 An embodiment of an integrated design of a first flow-blocking portion on a rotating disk and a first corresponding flow-blocking portion on a main stator is shown;

[0058] Figure 21 The principle of suppressing gas leakage by using a spiral seal and a labyrinth seal is shown through the first obstruction part and the first corresponding obstruction part, the first / second convex part and / or concave part, and the first / second corresponding concave part and convex part;

[0059] Figure 22 This is a schematic diagram of the principle of the sealed liquid circulation device and the liquid recovery, storage and replenishment mechanism of the rotary mechanism;

[0060] Figure 23 The design of the piston top side of the rotary mechanism is shown;

[0061] Figures 24A to 24E The gas-driven side design of the piston is shown;

[0062] Figure 25A 、 Figure 25B It is the matching diagram of different quantities of main convex rotor and auxiliary concave rotor;

[0063] Figure 26 A diagram showing the coordination of the main convex rotor and the auxiliary concave rotor, with one auxiliary concave rotor being saved; and

[0064] Figures 27A-27D The working principle diagram of the split synchronous four-in-one stroke circular rotary engine of the rotating mechanism is shown. DETAILED DESCRIPTION

[0065] The accompanying drawings describe in detail the specific embodiments and examples of the present disclosure. What is described here is only the preferred embodiment of the present disclosure. Those skilled in the art may conceive of other ways to implement the present disclosure based on the preferred embodiment, and other ways also fall within the scope of the present disclosure.

[0066] See also Figures 1 to 3, which shows a rotating mechanism 100 according to an exemplary embodiment of the present disclosure. It should be noted that the rotating mechanism 100 according to the present disclosure can be, for example, a hybrid power device, a range extender, an internal combustion engine, an expander, a compressor, a vacuum machine (vacuum pump) or a liquid pump, but is not limited thereto, and can cover various types of rotating mechanisms. In internal combustion engine, expander, and compressor applications, the working fluid is a gas or a mixed gas. In pump applications, the working fluid can be either a gas or a liquid. The following mainly introduces the specific embodiment of the rotating mechanism 100 according to the present disclosure by taking an internal combustion engine that includes the functions of an expander and a compressor as an example. As can be seen from these figures, the rotating mechanism 100 (for example, an internal combustion engine in these figures) is mainly composed of a fairing shell 50, a fan 60, an expansion ring (expander), a compression ring (compressor), a multifunctional air chamber 80, gears, etc., which are connected front and back by shafts and operate synchronously. In some embodiments, the compression ring with the function of compressing air can be replaced by other types of compressors. The expansion ring and the compression ring have similar structures. Their basic components are the main and auxiliary ring structures, including the main male rotor 10 and the auxiliary female rotor 20 as well as the main stator 30 and the auxiliary stator 34. The main stator 30 and the auxiliary stator 34 serve as fixed housings to accommodate the main male rotor 10 and the auxiliary female rotor 20 that can rotate around the axis. Figure 1 、 Figures 3 and 4 、 Figure 12 The rotating mechanism 100 also includes a main shaft 82 and an auxiliary shaft 83. The main shaft 82 connects the main male rotor 10 and the main stator 30, while the auxiliary shaft 83 connects the auxiliary female rotor 20 and the auxiliary stator 34 via bearings. The main shaft 82 and the auxiliary shaft 83 are each supported in a bearing. The rotating mechanism 100 also includes a main gear 71 connected to the main shaft 82 and an auxiliary gear 72 connected to the auxiliary shaft 83. Synchronous operation between the main male rotor 10 and the auxiliary female rotor 20 is achieved through a main / auxiliary gear transmission. Instead of the main gear 71 and auxiliary gear 72, synchronous operation between the main male rotor 10 and the auxiliary female rotor 20 can also be achieved using a belt or other means. This allows the auxiliary female rotor 20 to rotate in coordination with the main male rotor 10.

[0067] Figures 15A-15C 、 Figures 16A-16C 、 Figures 17A-17C as well as Figure 18 Various rotor embodiments according to the present disclosure are shown. Both the primary male rotor and the secondary female rotor include a turntable. In some large-scale embodiments, the turntable is greater than 120 mm thick. In some medium-sized embodiments, the turntable is between 40 and 120 mm thick. In some small-scale embodiments, the turntable is less than 40 mm thick. Figure 15B and Figure 15C Corresponding respectively Figure 16B Two configuration designs in . Figure 18 yes Figure 17BA cross-sectional view of a configuration embodiment. It can be seen that the main convex rotor 10 has a turntable 1 and a piston 2 configured as a convex arm, and the piston 2 is connected to the edge of the turntable 1. Only one piston and one auxiliary ring is allowed, but it will cause problems of axial asymmetry and continuous impact on the shaft, which is not conducive to long-term operation. In a preferred embodiment of the present disclosure, at least two pistons 2 are provided, which are evenly and symmetrically distributed on the peripheral edge of the turntable 1, and the working thrust can achieve force balance; and two auxiliary rings are evenly and symmetrically distributed on both sides of the main convex rotor. It should be pointed out that the number of pistons 2 is not limited to two, and more evenly distributed pistons 2 can be provided as needed, such as three (see Figure 25A ), four (see Figure 25B ), five, six, and so on. Two pistons can achieve 4 ignitions per rotation. Three pistons can achieve 9 ignitions per rotation. Four pistons can achieve 16 ignitions per rotation. This makes it easy for the rotating mechanism 100 as an internal combustion engine to improve the power-to-weight ratio, that is, the ratio of power to weight. However, a larger number of pistons will reduce the compression and expansion strokes, which need to be balanced. Inside the main stator 30 serving as a fixed shell, a cavity serving as a cylinder 40 is formed on the rotation path of the piston 2 to wrap around the piston 2. The cylinder 40 can be used to accommodate a working fluid and a rotating piston.

[0068] When the auxiliary concave rotor 20 and the main convex rotor 10 rotate in cooperation with each other, their rotation directions are opposite and they do not touch each other, but are separated by a small gap to avoid collision, scratching, or even jamming. Figure 1-Figure 7 As well as Figure 15 and Figure 18 The two shown in FIG can be set according to the number of pistons 2, for example, three (such as Figure 25A As shown), four (as Figure 25B As shown), etc., and their number usually matches the number of pistons 2, for example. In the embodiment of the present disclosure, a plurality of auxiliary concave rotors 20 are evenly and symmetrically distributed around the main convex rotor 10. The auxiliary concave rotor 20 has an auxiliary turntable 25 and an incompletely closed annular extension 28 surrounding the auxiliary turntable 25. The cross-sectional shape of the annular extension 28 is the same as the cross-sectional shape of the piston, and acts as an on-off switch for the cylinder and the piston. The annular extension 28 has a concave portion 3 that cooperates with the piston 2. When the main convex rotor 10 and the auxiliary concave rotor 20 rotate together to a certain angle, the piston 2 can just pass through the concave portion 3 with a very small gap, while the cylinder is cut off by the annular extension 28 at other operating angles, and the cylinder volume is variable through the rotation of the piston. See Figure 1 、 Figures 3 and 4 、 Figure 12 、 Figure 25A 、 Figure 25BIn an exemplary embodiment of the present disclosure, the transmission ratio of the main gear 71 and the auxiliary gear 72 can be 1:n, where n≥1. A transmission ratio of, for example, 1:1, 1:2, 1:3, 1:4, etc., means that for every rotation of the main gear 71, the auxiliary gear 72 rotates n circles, such as 1 circle, 2 circles, 3 circles, or 4 circles, thereby realizing the rotational coordination of the auxiliary concave rotor and the concave portion with the piston. The number of concave portions 3 of each auxiliary concave rotor 20 depends on the transmission ratio and the number of pistons. For example, in a three-ring two-piston structure with a transmission ratio of 1:1:1 auxiliary:main:auxiliary, each auxiliary concave rotor has two axially symmetrical concave portions, so that after one rotation, the two axially symmetrical pistons pass through the two concave portions respectively. For example, in a three-ring two-piston structure with a transmission ratio of 2:1:2 auxiliary:main:auxiliary, each auxiliary concave rotor has only one concave portion, so that after one rotation, the two axially symmetrical pistons pass through the same concave portion. According to a preferred embodiment, see Figure 26 Two main male rotors 10 and three auxiliary female rotors 20 are arranged side by side, with one auxiliary female rotor 20 arranged between the two main male rotors 10. The recessed portion 3 of this auxiliary female rotor 20 is shared by the pistons 2 on the two main male rotors 10 in turn, thereby saving one auxiliary female rotor and improving the power-to-weight ratio. The method of saving the number of auxiliary female rotors and improving the power-to-weight ratio by reusing the auxiliary female rotor on more than two main male rotors is not limited to Figure 26 For example, three main convex rotors can reuse two auxiliary concave rotors.

[0069] Depend on Figures 1 to 3 It can be seen that in the exemplary embodiment of the present disclosure, the expansion ring and the compression ring are spaced apart in parallel and are connected at appropriate locations through conduits or channels and multifunctional air chambers 80. The main convex rotor 10 near the main gear 71 and the auxiliary concave rotor 20 near the auxiliary gear 72 are in the same layer, that is, the compression ring is located at the rear end, forming a first layer of main convex rotors 10' and a first layer of auxiliary concave rotors 20'. Correspondingly, the main convex rotor 10 near the fan away from the main gear 71 and the auxiliary concave rotor 20 away from the auxiliary gear 72 are in the same layer, that is, the expansion ring is located at the front end, forming a second layer of main convex rotors 10" and a second layer of auxiliary concave rotors 20".

[0070] The following describes the working principle of the rotary mechanism 100 as an internal combustion engine according to the present disclosure. Figure 3 、 Figure 12 as well as Figures 27A-27DAs the main convex rotor 10 and the auxiliary concave rotor 20 rotate in coordination with each other, the cylinder 40 is cut off and divided by the piston 2 and the auxiliary concave rotor 20 into an intake chamber 41 and a compression chamber 42 located in the compression ring, and an expansion chamber 43 and an exhaust chamber 44 located in the expansion ring, the volumes of which can be dynamically changed. In some embodiments, alternatively, the auxiliary concave rotor is not necessary, and a card for cutting off the cylinder 40 can also be provided, so that the cylinder 40 is divided into several chambers with variable volumes. The auxiliary concave rotor and the card are both cylinder cutting mechanisms, which are used to form a cylinder with variable volume by cooperating with the piston. Among them, the intake chamber 41 and the compression chamber 42 are formed in the cylinder 40' defined by the main convex rotor 10' and the main stator 30' of the first layer (compression ring), and the expansion chamber 43 and the exhaust chamber 44 are formed in the cylinder 40" defined by the main convex rotor 10" and the main stator 30" of the second layer (expansion ring). During the intake stage, see Figure 27A , at the first layer, the air in the duct enters the air intake chamber 41 through, for example, the two first air intake ports 18' of the cylinder 40'. A valve 38 for adjusting the air intake volume can be provided at the first air intake port 18', for example. With the valve 38, the air intake volume can be adjusted as needed, and the power of the rotating mechanism can be flexibly controlled. As the piston 2' rotates, the air intake chamber 41 gradually increases, forming a negative pressure to inhale more air. At the same time, the compression chamber 42 located on the other side of the piston 2' gradually decreases. At this time, the first one-way valve 22' (or the second one-way valve 22") connected to the first air outlet 19' at the compression chamber 42 can remain closed, thereby compressing the air in the compression chamber 42 (or the multi-functional air chamber 80), see Figure 27B . In an alternative embodiment of the present disclosure, the compression ring can also be omitted, and an electric compressor can be used alone to achieve air intake and compression. When the air in the compression chamber 42 is compressed to a certain extent, for example, the air pressure exceeds the one-way valve threshold, thereby opening the first one-way valve 22', the compressed air is transferred from the compression chamber 42 of the first layer (compression ring) to the multifunctional air chamber 80 for storage via the conduit or channel and the first one-way valve 22'. The multifunctional air chamber 80 has multiple functions such as air storage and / or air mixing and / or combustion. In one embodiment A of the present disclosure, the multifunctional air chamber only plays the role of air storage. The timing of ignition and combustion of the internal combustion engine 100 is when the piston of the main convex rotor of the second layer (expansion ring) happens to pass through the notch of the auxiliary concave rotor and before and after the second air intake 18". At this time, opening the second one-way valve 22" allows the compressed air to be transferred from the multifunctional air chamber 80 to the expansion chamber 43 of the second layer expansion ring cylinder 40". Figure 27C. At this time, in the expansion ring, for example, a (high-pressure direct injection) fuel nozzle 21 is used to spray an appropriate amount of fuel into the expansion chamber 43, forming a mixture of compressed air and fuel with an appropriate air-fuel ratio in the expansion chamber 43, and the mixture is ignited by the spark plug 23 of the expansion chamber. A preferred embodiment B of the present invention does not use the spark plug 23 to ignite the mixed gas, but controls the temperature, pressure, air-fuel ratio, compression ratio and other parameters of the expansion chamber to meet the compression ignition conditions to achieve direct compression ignition (full process or after spark plug heat engine). . The burning mixture generates a large amount of heat energy in the expansion chamber 43, expands rapidly, and pushes the piston 2" of the expansion ring to rotate and work in the cylinder 40, so that the expansion chamber 43 rapidly increases. At the same time, the exhaust chamber 44 separated by the second layer (expansion ring) piston 2" is reduced, and the gas therein is discharged through the second outlet 19". Figure 27D The combustion exhaust gas is discharged to the outside through, for example, an exhaust pipe 73 connected to the outlet of the exhaust chamber 44, or further processed, such as passing through a three-way catalytic converter and / or a particulate filter before being discharged into the tail jet outlet. This completes a complete cycle consisting of the four strokes of intake, compression, expansion, and exhaust. As the piston continues to rotate, the next cycle begins, and this cycle repeats itself over and over again.

[0071] In one embodiment of the present disclosure, it can also be exemplarily provided that various sensors such as Hall sensors, position sensors, oxygen sensors, temperature sensors, concentration sensors, pressure sensors, and pressure relief valves, pressure regulating valves, etc. are provided at locations including but not limited to the first air inlet 18', the second air inlet 18", the first air outlet 19', the second air outlet 19", the multifunctional air chamber 80, the first one-way valve 22', the second one-way valve 22", the exhaust pipe 73, the main stator 30, the auxiliary stator 34, the gears 71 / 72, etc., so as to control the intake flow rate, the outlet flow rate, the compression ratio, the air-fuel ratio, the gas pressure, the temperature, the fuel injection amount, the rotation speed, etc. See Figure 1 、 Figure 2 as well as Figures 11 to 12 In a preferred embodiment of the present disclosure, the multifunctional air chamber 80 of the rotating mechanism 100 is connected to the expansion chamber 43 and the compression chamber 42 via the connecting pipe 84, and an additional fuel injection mechanism 16 and an additional spark plug 85 can be additionally or alternatively (or optionally) provided on the multifunctional air chamber 80. Figure 11, a first one-way valve 22' and a second one-way valve 22" can also be installed on the connecting pipe 84, and a corresponding third one-way valve 22"' can be installed on the one-way exhaust gas return mechanism 70. They have different working temperatures, pressures, and functions in different positions, and the corresponding appearance and models can be the same or different, and are controlled by electricity (magnetism) and / or machinery. The first one-way valve 22' between the compression chamber 42 and the multi-functional air chamber 80 is used to control the intake volume and pressure of the compressed air from the compression chamber 42 into the multi-functional air chamber 80, and can relieve excess air and pressure into the air duct as needed. The second one-way valve 22" between the multi-functional air chamber 80 and the expansion chamber 43 controls the opening or closing of the channel from the multi-functional air chamber 80 to the expansion chamber 43 based on an electrical signal or a pressure threshold. The third one-way valve 22"' between the exhaust gas return mechanism and the multi-functional air chamber 80 controls the amount of exhaust gas discharged from the exhaust chamber 44 to the multi-functional air chamber 80. In the present disclosure, fuels may include, but are not limited to, hydrogen, gasoline, diesel, heavy oil, methanol, ethanol, ammonia, natural gas, biofuels, etc. In a preferred embodiment of the present disclosure, water vapor may also be sprayed into the expansion chamber to cool it down and expand it to produce work.

[0072] In one embodiment of the present disclosure, in order to save fuel, the injection of fuel and ignition combustion can be stopped when the power demand of the internal combustion engine is low. This working mode is called sparking. There are two sparking working modes, stopping intake compression and stopping fuel injection, or not stopping intake compression and only stopping fuel injection. A) In the former, the first one-way valve 22' is opened, and the transferred uncompressed air directly enters the expansion chamber 43 through the multifunctional air chamber 80 to form a direct passage; B) In the latter, the internal combustion engine operates as normal but does not inject fuel. The compression ring continues to compress the air and stores it in the multifunctional air chamber. When the ignition time comes, the second one-way valve 22" is opened to send the compressed air (or the exhaust gas after combustion) into the expansion chamber for expansion and work. Both modes use the inertial flywheel energy storage effect to continue to maintain rotation and work. Both sparking working modes can cool the cylinder. In one embodiment of the present disclosure, the temperature of the internal combustion engine and / or the expansion ring and / or the cylinder can be controlled by sparking, and the internal combustion engine can be operated intermittently as needed. When it is detected that the temperature of the expansion ring and / or the cylinder is higher than the threshold, the internal combustion engine actively enters the sparking mode or intermittent mode. Operating mode to reduce cylinder temperature. Since the main / auxiliary rotors have an inertial flywheel energy storage effect, the fuel saving effect of the internal combustion engine jump spark working mode disclosed in the present invention is far superior to that of traditional reciprocating piston engines and eccentric shaft rotor engines. In one embodiment of the present invention, through intermittent operation in a jump spark mode, two axially symmetrical pistons can achieve ignition (combustion) 0 times, 2 times or 4 times per rotation. Three evenly distributed pistons can achieve ignition (combustion) 0 times, 3 times, 6 times or 9 times per rotation. Four evenly and symmetrically distributed pistons can achieve ignition (combustion) 0 times, 2 times, 4 times, 6 times, 8 times, 10 times, 12 times, 14 times or 16 times per rotation. This achieves flexible power output on demand, which can output at full power and save fuel greatly when cruising or idling.

[0073] In a preferred embodiment of the present disclosure, the rotating mechanism 100 further includes a one-way exhaust gas return mechanism 70 connected between the multifunctional air chamber (80) and the exhaust chamber 44, which is configured as a one-way pipeline, for example, to allow part of the exhaust gas discharged from the exhaust chamber 44 during the operation of the internal combustion engine to pass through the multifunctional air chamber 80 and mix with compressed air, dilute the oxygen concentration of the mixed gas, increase the specific heat capacity of the mixed gas, reduce the combustion temperature, and inhibit the generation of harmful substances such as NOx during the high-temperature oxygen-rich combustion process; and allow the components in the exhaust gas that may not be fully burned (such as CO, HC, etc.) to continue to burn or oxidize, thereby reducing the emission of harmful substances in the exhaust gas. This working process is EGR exhaust gas recirculation during the operation of the internal combustion engine. In an embodiment of the present disclosure, there can be one or more air storage chambers or air storage tanks or air storage / mixing multifunctional air chambers (preferably with a three-way catalytic converter purification function) specifically for storing exhaust gas, storing the combustion exhaust gas purified by the three-way catalytic converter, and during the internal combustion engine spark operation, the exhaust gas is mixed with compressed air in the mixing chamber or expansion chamber and then expanded to perform work, thereby cooling the cylinder.

[0074] In another embodiment C of the present disclosure, the multifunctional air chamber 80 functions as both an air storage and air mixing chamber. When the time for ignition and combustion arrives, an appropriate amount of fuel is injected into the multifunctional air chamber 80 via the additional fuel injection mechanism 16, where it is mixed with the stored compressed air at an appropriate air-fuel ratio (the temperature and pressure at this point ensure that the mixed gas does not undergo compression ignition). The second one-way valve 22" is then opened by electrical (magnetic) control, transferring the mixed gas into the expansion chamber 43. The spark plug 23 in the expansion chamber ignites the fuel, causing it to expand and produce work.

[0075] In another preferred embodiment D of the present disclosure, the multifunctional air chamber 80 performs the functions of gas storage, gas mixing and combustion. Compressed air with a temperature, pressure and appropriate compression ratio suitable for compression ignition is prepared in the multifunctional air chamber 80, and when the ignition and combustion timing arrives, an additional fuel injection mechanism 16 is added to inject an appropriate amount of fuel for direct compression ignition. Pressure is generated by electrical (magnetic) control or by the heat energy released by combustion in the multifunctional air chamber 80 so that the second one-way valve 22' is opened to transfer the combustion gas to the expansion chamber 43 of the second layer (expansion ring) to continue combustion, expansion and work. The one-way closure of the first one-way valve 22' allows the burning high-pressure gas to only pass through the expansion chamber 43 and not the compression chamber 42.

[0076] In yet another embodiment E of the present disclosure, a fuel injection mechanism 16 is added to the multifunctional air chamber 80 to inject an appropriate amount of fuel into the stored compressed air at an appropriate air-fuel ratio (the temperature and pressure at this point prevent the mixture from being compression-ignited). When the ignition timing arrives, the mixture is ignited by an additional spark plug 85. Pressure is generated by electrical (magnetic) control or by the heat energy released by combustion in the multifunctional air chamber 80, causing the second one-way valve 22" to open, transferring the combustion gas to the second-layer (expansion ring) expansion chamber 43 for continued combustion, expansion, and work.

[0077] A preferred embodiment F of the present disclosure supports the partitioned mixed combustion of two fuels. A small amount of lean first fuel is injected into the multifunctional air chamber 80 through the additional fuel injection mechanism 16 and mixed with the stored compressed air for compression ignition. After it is transferred to the expansion chamber through the second one-way valve 22", an appropriate amount of second fuel injected into the fuel nozzle 21 of the expansion chamber is compression ignited. Alternatively, the mixed gas in the multifunctional air chamber 80 is not compression ignited, and after the second one-way valve 22" is opened to transfer it to the expansion chamber, an appropriate amount of second fuel is injected into the fuel nozzle 21 of the expansion chamber, and it is mixed with the mixed gas of the first fuel and air again, and ignited or compression ignited. Preferably, one of the two fuels can be methanol or a fuel containing methanol, which helps to remove carbon deposits or avoid the formation of carbon deposits during the combustion process.

[0078] Since the compression chamber of the compression ring and the expansion chamber of the expansion ring do not affect each other and operate independently, the timing logic is simple. Pre-ignition, detonation, and knocking problems that are difficult to suppress / solve in traditional reciprocating piston engines and eccentric shaft rotor engines (compression ignition) are no longer a problem for the internal combustion engine disclosed herein. The engine disclosed herein is different from traditional engines in that it has torque characteristics similar to those of an electric motor, that is, it can have maximum torque when starting at low speed. The internal combustion engine disclosed herein achieves arbitrary compression ratios within a certain range through variable intake valves and one-way valve control of the multi-functional air chamber, and accurately controls the operating temperature of the expansion chamber through the spark working mode. It is easy to meet the temperature, pressure, compression ratio, air-fuel ratio and other conditions required for compression ignition. Therefore, the (low temperature) HCCI homogeneous charge compression ignition technology that is difficult to achieve in traditional reciprocating piston engines and eccentric shaft rotor engines can be easily achieved in the internal combustion engine disclosed herein. Since the intake compression chamber of the compression ring and the expansion exhaust chamber of the expansion ring do not affect each other and operate independently and synchronously, the intake is compressed at the same time and the expansion is exhausted at the same time. Therefore, the internal combustion engine disclosed in the present invention is also called a "split synchronous four-in-one stroke circular rotary engine" or simply a "split synchronous circular rotary engine."

[0079] In one embodiment of the present disclosure, the main male rotor 10 and main stator 30 in the first layer (compression ring), which form the intake chamber 41 and compression chamber 42, can be made of lightweight, high-strength materials such as aluminum alloy, magnesium-aluminum alloy, engineering ceramics, or special engineering plastics to reduce weight and further improve the power-to-weight ratio. In one embodiment of the present disclosure, the main and auxiliary rotors of the expansion and compression rings are of equal size and coaxially connected front to back. In a preferred embodiment of the present disclosure, the expansion and compression rings can be of different sizes, for example, with the compression ring larger than the expansion ring, or vice versa. The main male rotor is coaxially connected front to back, while the auxiliary rotor is connected coaxially or non-coaxially via gears or belts, allowing for arbitrary adjustment of the compression ratio within a certain range. In one embodiment of the present disclosure, the main male rotor 10 and auxiliary female rotor 20 are statically and dynamically balanced by partially hollowing out material. For example, the annular extension 28 of the auxiliary female rotor 20 is hollowed within the annular extension 28, achieving static and dynamic balance of the auxiliary female rotor 20.

[0080] Depend on Figures 1 to 3 It can be seen that in an exemplary embodiment of the present disclosure, the rotating mechanism 100 further includes a fairing housing 50 and a fan 60. The fairing housing has the function of adjusting the airflow. The fan 60 is installed on the main shaft 82 inside the fairing housing 50. Additionally, the fan 60 can also be set on the auxiliary shaft 83, see Figure 1 、 Figures 3 and 4 、 Figure 12 The number of fans 60 is not limited to this. The main shaft and / or auxiliary shaft can be equipped with any number of fans, for example, only the main shaft when there is one fan, both on the main shaft or on two auxiliary shafts when there are two fans, one on the main shaft and two on the auxiliary shafts when there are three fans, two on the main shaft and two on the auxiliary shafts when there are four fans, and so on. The fairing housing 50 accommodates the fan, the expansion ring, and the compression ring, and has a The shaped portion forms an air duct inside, directing air to the back of the expansion ring, where it is not directly blown by the fan, so that the expansion ring can be cooled both front and back. Optionally, the fairing housing 50 can also accommodate a main gear 71 and an auxiliary gear 72. The fan 60, the expansion ring, the compression ring, and the gear set including the main gear 71 and the auxiliary gear 72 are sequentially connected via a main shaft 82 and / or an auxiliary shaft 83, working in coordination. Thus, through the air duct formed in the fairing housing 50, the fan 60 continuously blows outside air into the fairing housing 50, cooling the hot expansion ring. The cold air absorbs and removes the heat dissipated by the hot expansion ring, transforming into hot air that enters the compression ring's intake chamber 41 to participate in the next power cycle. This closed-loop system recovers heat energy lost to cooling the hot expansion ring, improving thermal efficiency. Heating the air helps raise the compressed air temperature, making compression ignition easier for fuels with higher ignition points, thereby improving combustion efficiency and thermal efficiency. The number, size, and speed of the fans can also be adjusted as needed to further adjust the compression ratio. It should be noted that the fairing housing 50, the main stator 30 and the auxiliary stator 34 can be disassembled into two symmetrical halves, so that the fan 60 and other components, the main male rotor 10 and the auxiliary female rotor 20 can be accommodated therein respectively during assembly, and then closed and assembled, see Figure 3 In some embodiments, the main stator half 30 and the auxiliary stator half 34 are integrally constructed by methods such as laser welding or casting. Alternatively, the housing 50, the main stator 30 / main male rotor 10, and the auxiliary stator 34 / auxiliary female rotor 20 can also be integrally constructed using 3D printing, additive manufacturing, or the like.

[0081] In an exemplary embodiment of the present disclosure, see Figure 13 The rotating mechanism 100 further includes an electromagnetic device 90, which includes a fixed induction coil mechanism close to the main gear 71 and a first magnet 95 provided on the main gear 71. Figures 1 to 3 、 Figure 12 、 Figure 13, the induction coil mechanism may also include, for example, an induction coil 96 and a bearing portion 97 for bearing the induction coil 96. In a preferred embodiment, the induction coil 96 is spirally drawn on the bearing portion 97 which is a PCB printed circuit board. A bearing portion 97 with a coil 96 is provided on one side or both sides of the main gear 71, and the main shaft 82 drives the main gear 71 to rotate relative to the fixed bearing portion 97, so that the first magnet 95 on the main gear 71 rotates relative to the fixed coil 96, thereby the induction coil 96 generates electricity to form a generator. By controlling the magnitude, direction and frequency of the current supplied to the induction coil 96 by the control circuit, this set of electromagnetic devices can be used as a starter and motor to drive the gear and the main shaft to rotate, start the internal combustion engine and / or output power. In this way, the functions of the motor and generator can be realized, so that the internal combustion engine of the present disclosure can become a hybrid device or a range extender. In another exemplary embodiment of the present disclosure, a piston position maintaining mechanism 98 is used to replace the electromagnetic device 90, for example, it is arranged on the bottom surface of the housing 50, such as Figure 14 As shown, the internal combustion engine comprises a housing 94, a second magnet 91 housed therein, and a spring 93. A pressure relief member 92 is provided on the housing 94, which can be configured as a pressure relief hole or a pressure relief valve. The polarity of the second magnet 91 and the polarity of the first magnet 95 repel or attract each other, ensuring that the piston remains in a specific position when it stops rotating. During engine operation, high-pressure air within the spinner housing 50 enters the housing 94 through the pressure relief member 92. Within the housing 94, the high-pressure air pushes the second magnet 91, overcoming the elastic force of the spring 93 and thereby compressing the spring 93. As a result, the position of the second magnet 91 deviates, that is, it is not aligned with the first magnet 95, thereby preventing the normal operation of the rotating mechanism 100. When the rotating mechanism stops operating, the fan 60 no longer blows air into the spinner housing 50, and the high-pressure air in the duct disappears. Without the pressure of the high-pressure gas, the spring 93 returns to its original position. At this time, the second magnet 91 located on the fixed housing 50 attracts the first magnet 95 of opposite polarity located on the main gear 71 to a position aligned with it, thereby driving the main gear 71 to rotate to a specific position, and then causing the main convex rotor 10 and its piston 2, which are coaxially fixedly connected to the main gear 71, to stop at a predetermined position, such as just stopping at a position where the spark plug 23 can ignite and burn. In this position, fuel can be directly injected into the expansion chamber 43 without the drive of the starter, and the mixture of air and fuel in the expansion chamber 43 can be ignited through the spark plug 23, thereby achieving (starter-free) self-starting of the rotating mechanism. The above is only an exemplary embodiment of the piston position maintaining device, and the present disclosure is not limited to this.

[0082] In the operation of the rotating mechanism, the expansion ring relies on the combustion and expansion of the gas to push the piston 2 to do work. In one embodiment of the present disclosure, the surface of the piston 2" of the expansion ring that is pushed by the gas in the expansion chamber, that is, the back with reference to its rotation direction, is designed to be a plane (see Figure 24A and Figure 24E ), it can also be preferably designed as a concave surface (see Figures 24B-24D ), the concave surface makes the piston 2" of the expansion ring more concentrated (the convex surface makes the piston force dispersed), and the arrow E indicates the rotation direction of the piston 2. The other side of the piston 2" opposite to the force-bearing surface (the surface in the exhaust chamber), that is, the front side with reference to its rotation direction, can be a plane (see Figure 24A and Figure 24B ), convex surface (see Figure 24D and Figure 24E ) or concave (see Figure 24C In particular, when the front face of the rotating expansion ring piston 2' (the face in the exhaust chamber) is convex, the gas is forced to squeeze toward the periphery of the piston 2', so that the gap between the piston 2' and the edge of the main stator 30 has a very high gas pressure, thereby preventing the gas burned in the expansion chamber from leaking into the exhaust chamber. In one embodiment of the present disclosure, the back face of the compression ring piston 2' (the face in the intake chamber) is a plane, and can also be preferably designed as a concave surface (see Figure 24B-Figure 24C ), the concave surface makes the suction space larger and the negative pressure greater. The front of the piston 2' of the compression ring (the surface in the compression chamber) is a plane (see Figure 24A and 24B ) or concave (see Figure 24C ), in particular, when it is a concave surface, the gap where the compressed air is squeezed to the periphery of the piston 2' can be reduced, so as to reduce the leakage of the compressed air and help to improve the compression ratio.

[0083] In one embodiment of the present disclosure, as can be seen from FIG. 16 , the cross section of the piston 2 can be, for example, circular (see FIG. Figure 16B ), oval (see Figure 16A ), rounded rectangle (see Figure 16C) and other shapes, but the present disclosure is not limited to this. For example, the compression ring has only two strokes, intake and compression, and does not require combustion, so thermal stress deformation will not occur. Therefore, the shape of the compression ring's piston 2' does not have to be limited to a circle or an ellipse. It can be in many shapes, such as a rectangle or a rounded rectangle, and can have any desired width, thereby achieving any compression ratio within a certain range. The mixed gas in the expansion chamber of the expansion ring needs to burn and expand to push the piston 2" to do work. Compared with a rectangular cylinder, which may not burn completely, a circular or elliptical ring cylinder 40 can make the combustion more complete and the combustion efficiency higher. The piston 2" is preferably circular or elliptical here, which also makes the thermal stress distribution of the piston 2" more uniform, avoiding the piston 2" from being deformed by heat. On the contrary, if the cross-section of the expansion ring's piston 2" is, for example, a rectangle, the uneven thermal stress on its corners may cause the piston 2" to deform, thereby increasing the gap between the main stator 30 and the piston 2", causing gas leakage, thrust and power reduction, and even possible damage to the piston 2" and the stator 30 (cylinder jam) after long-term operation, causing the rotating mechanism to malfunction or be scrapped. Therefore, the design of the circular or elliptical piston disclosed in the present invention not only solves the problem of insufficient combustion in traditional eccentric shaft rotor engines, but also solves the problem of easy thermal stress deformation in certain rectangular piston rotor engines.

[0084] In order to reduce gas leakage, it is expected that the gap between the main stator 30 and its contents, namely the main convex rotor 10, and the gap between the auxiliary stator 34 and its contents, namely the auxiliary concave rotor 20, are as small as possible. However, in reality, considering the limitations of the manufacturing and assembly processes and ensuring the relative rotation of the stator and the rotor to avoid scratching or even jamming, the gap cannot be infinitely small, and poor configuration and sealing design often lead to gas leakage. Gas leakage will cause the pressure and compression ratio of the compression ring to drop, the thrust of the expansion ring piston to drop, the combustion efficiency to drop, the output torque and power of the rotating mechanism to drop, the fuel consumption to increase, and the economy to be affected. The combustion gas leaks directly into the atmosphere and may even cause air pollution. Traditional eccentric shaft or other rectangular piston rotor engines, especially those without a turntable, have long had the problem of poor sealing.

[0085] According to one embodiment of the present disclosure, a special structural design is applied to the rotary disc 1, piston 2, main stator 30, auxiliary stator 34, etc., which can change the direction of leakage of the working fluid multiple times and significantly, significantly extending the leakage path of the working fluid. This allows more seals and different types of seals to be deployed along the leakage path to prevent leakage of the working fluid, thus solving the problem of insufficient sealing space in traditional eccentric shaft or other rotary engines. Figure 1 、 Figure 2 、 Figure 6-Figure 8 、 Figure 10 Figure 15, Figure 17, Figure 18 、 Figures 19A-19D 、 Figures 20 to 22The turntable 1 has a concave and / or convex first flow-blocking portion 4 arranged on its end face, and the main stator 30 has a convex and / or concave first corresponding flow-blocking portion 5 arranged on its inner surface, which is non-contact with the first flow-blocking portion 4, i.e., a clearance fit. The first flow-blocking portion 4 can be, for example, a concentric ring with a roughly rectangular cross-section, and its cross-sectional size is usually much larger than the size of a single comb tooth of a labyrinth seal. It cooperates with the first corresponding flow-blocking portion 5 like a "dam" to block the leakage gas from escaping through the main shaft 82, for example. By setting up multiple flow-blocking portions, the direction of leakage of the working fluid can be greatly changed many times, and the travel path of the fluid leakage can be greatly extended. However, the flow-blocking portion can also be in various shapes such as a semicircular arc, a triangle, a trapezoid, etc. The number of the flow-blocking portions can be one or more, preferably more than two, such as 2, 3, 4, 5, 6, etc. In some embodiments, when multiple flow-blocking portions are provided, they can be the same or different in size, shape, spacing, etc., and can be opposite to or away from each other to form an X-shape, Shape, H shape, etc. (see 17A to 17C ). The design purpose and function of the choke and the labyrinth seal are completely different. The size of the choke is usually much larger than the size of a single comb tooth of the labyrinth seal. The purpose is to significantly change the leakage direction of the working fluid and significantly extend the leakage stroke path, and solve the problem of insufficient sealing space in traditional rotating mechanisms; the labyrinth seal generates pressure drops and vortices through the throttling comb tooth gaps and expansion cavities, converting kinetic energy into heat energy, thereby achieving the purpose and effect of reducing the leakage pressure of the working fluid. It does not have the purpose and effect of significantly changing the leakage direction and significantly extending the leakage path. In some embodiments, the choke extends the leakage path stroke by, for example, 50% or 100% or more than 200%, which is something that a labyrinth seal cannot do. The choke can support a variety of seals, including but not limited to labyrinth seals, gap seals, spiral seals, hole and groove seals, honeycomb seals, brush seals, sheet seals, medium seals, magnetic fluid seals, etc.

[0086] See also Figure 18 、 Figures 19A-19D 、 Figures 20 to 21In one embodiment of the present disclosure, the first flow-blocking portion 4 is flatly constructed on its peripheral surface or has a first concave and / or convex portion 6, and the first corresponding flow-blocking portion 5 is flatly constructed on its peripheral surface or has a first corresponding convex and / or concave portion 7 that is non-contact with the first concave and / or convex portion 6, i.e., a clearance fit. Alternatively, the design may be the opposite, that is, the first corresponding flow-blocking portion 5 has a first concave and / or convex portion 6 on its peripheral surface, and the first flow-blocking portion 4 is flatly constructed on its peripheral surface or has a first corresponding convex and / or concave portion 7 that is non-contact with the first concave and / or convex portion 6, i.e., a clearance fit. There are usually multiple first concave and / or convex portions 6, and their shapes can be, for example, rectangular, semicircular, triangular, trapezoidal, etc. They are distributed along the peripheral surface of the first flow-blocking portion 4 and can be the same or different in terms of size, shape, spacing, etc. In this way, the sealing performance is further improved.

[0087] In one embodiment of the present disclosure, see Figures 19A-19D 、 Figures 20 to 21 The end surface of the turntable 1 is locally flat or provided with a second recess and / or protrusion 8, and the inner surface of the main stator 30 is locally flat or provided with a corresponding second protrusion and / or recess 9 that is non-contact with the second recess and / or protrusion 8, i.e., a clearance fit. Similarly, the second recess and / or protrusion 8 can be, for example, one or more, and its shape can be, for example, rectangular, semicircular, triangular, trapezoidal, etc., and they can be the same or different in size, shape, spacing, etc. In a preferred embodiment of the present disclosure, a brush seal and / or a thin-film seal is provided on the end surface or stator of the turntable 1. In this way, the sealing performance is further improved.

[0088] In a preferred embodiment of the present disclosure, see Figures 19A-19D 、 Figures 20 to 21 The first concave and / or convex portion 6 and the first corresponding convex portion and / or concave portion 7 and the second concave and / or convex portion 8 and the corresponding second convex portion and / or concave portion 9 can, for example, form a spiral seal and / or a labyrinth seal and / or a gap seal and / or a honeycomb seal and / or a slot seal. Preferably, on the section or component of the first flow-blocking portion 4 that is nearly parallel or non-perpendicular to the main axis 82, the first concave and / or convex portion 6 forms a spiral seal (such as Figure 20 In this way, the turntable 1 can be driven in the direction of the spiral drive ( Figure 20 and Figure 21 As shown by the solid arrow H in the figure, along the direction of fluid leakage ( Figure 20 and Figure 21 The dotted arrow G in the figure drives the fluid in the opposite direction, for example, Figure 21The four points D→C, B→A in the figure. The first concave and / or convex portion 6 have opposite spiral directions on both sides of the turntable 1. In some preferred embodiments, the spiral seal may have a composite spiral seal, that is, a static spiral seal in the opposite direction is provided on the (opposite) stator of the dynamic spiral seal wrapped on the turntable, which can further enhance the spiral driving effect. The labyrinth seal, through the comb tooth throttling tooth gap and the expansion cavity structure, generates a pressure drop and a vortex, converts kinetic energy into thermal energy, gradually reduces the gas leakage pressure, further suppresses gas leakage, and improves the sealing performance. The labyrinth seal may preferably adopt a stepped or staggered comb tooth seal or a tortuous seal, etc. In a preferred embodiment of the present disclosure, a hole slot seal and / or a honeycomb seal is deployed on the main stator and / or the auxiliary stator, which also has the effect of generating a pressure drop and a vortex.

[0089] Similarly, in a preferred embodiment of the present disclosure, the auxiliary concave rotor 20 has a concave and / or convex second flow blocking portion 13 provided on its end surface, and the auxiliary stator 34 has a convex and / or concave second corresponding flow blocking portion 14 provided on its inner surface that is non-contact with the second flow blocking portion 13, i.e., in a clearance fit, as shown in FIG. Figure 1 、 Figure 6-Figure 8 、 Figures 15A-15C The second flow blocking portion 13 on the auxiliary concave rotor 20 can be similar to the first flow blocking portion 4 of the main convex rotor 10 in terms of quantity, structure and working mode, and their functions are also similar.

[0090] See also Figure 15B-15C 、 Figure 16B 、 Figures 17A-17C 、 Figure 18 In a preferred embodiment of the present disclosure, the turntable 1 has a third flow blocker 17 located on the bottom and / or side of the piston 2 and cylinder 40, partially surrounding the piston 2 and cylinder 40. Here, the third flow blocker 17 has a cross-section in the shape of a wine glass, for example. The shape of the main stator 30 is then adapted to the third flow blocker 17 to keep the gap between the main stator 30 and the turntable 1 very small. In contrast, Figure 15A The turntable 1 shown does not have the third flow blocker 17. It can be seen that the third flow blocker 17 forms a first type of third flow blocker 17' in the shape of a wine glass when half wrapped around the bottom side of the piston 2 and the cylinder (see Figure 15B 、 Figure 16B ), the degree of its wrapping can be Figure 15A and Figure 15B The third flow blocking portion will significantly change the leakage direction of the working fluid, significantly extend the leakage path, and prevent the working fluid from leaking directly toward the bottom side of the piston 2 (that is, toward the central axis of the turntable 1). The third flow blocking portion 17 forms a second third flow blocking portion 17 in the shape of a high wine glass beside the piston 2 and the cylinder 40 (see Figure 15C 、 Figure 16B), which will significantly change the direction of working fluid leakage, significantly extend the leakage path, and prevent the working fluid from leaking directly toward the side of the piston 2 and the cylinder. The leaked fluid can only move toward the top side of the main stator 30 located at the piston 2 and the cylinder, thereby further improving the sealing performance. The third flow blocking portion 17 has a third concave portion and / or convex portion 12 on its outer surface, see Figures 17A-17C By utilizing the third recess and / or projection 12, the sealing performance can be further improved.

[0091] See also Figure 23 In a preferred embodiment of the present disclosure, the piston 2 has a fourth recess 11 on its top side. Figure 23 As can be seen, the fourth recess 11 on the top side of the piston 2 can be, for example, one or more pressure relief grooves of varying depths, such as rectangular, semicircular, triangular, or trapezoidal shapes. In this exemplary embodiment, there are three grooves. The two smaller grooves on the left and right sides are, for example, 0.01-0.2 mm deep, and the larger groove in the middle is, for example, 1-2 mm deep and 1-2 mm wide. These grooves cause a sudden pressure drop in leaking gas, generating a vortex. This prevents gas leakage between the cylinders on either side of the piston.

[0092] In a preferred embodiment of the present disclosure, the second flow blocking portion 13 and the second corresponding flow blocking portion 14 are flatly constructed on their peripheral surfaces or have a fifth convex portion and / or concave portion and a fifth corresponding concave portion and / or convex portion (see Figure 7 、 Figure 8 ). With reference to the second concave portion and / or convex portion of the rotary disk 1 of the main male rotor 10 , a similar sixth concave portion and / or convex portion structure may be provided on the rotary disk of the auxiliary female rotor 20 .

[0093] In a preferred embodiment of the present disclosure, see Figure 3 、 Figure 6 、 Figure 9 、 Figure 10 The auxiliary stator 34 has a circumferential confluence groove 36 on the inner side of the circumferential edge of the annular extension 28, and has a plurality of guide grooves 35 connected to the circumferential confluence groove 36. The width and depth of the circumferential confluence groove can be, for example, 1 to 3 mm, and the width and depth of the guide groove can be, for example, 0.2 to 1 mm. Their cross-sections can be the same or different, and can be trapezoidal, rectangular, semicircular, etc. The guiding direction of the guide groove 35 is consistent with the rotation direction of the auxiliary concave rotor 20 (such as Figure 93 (as indicated by the arrow "X" in the figure), at least substantially consistent with each other. As a result, gas leaking from the cylinder 40 on the auxiliary rotor 20 side is guided along the guide grooves 35 to the circumferential confluence grooves 36 as the auxiliary rotor 20 rotates, thereby avoiding the leakage gap. The gas reaching the circumferential confluence grooves 36 is carried back into the cylinder 40 by the notch 3 when the piston 2 passes through the notch 3, thereby allowing the gas leaking from the cylinder 40 to the auxiliary rotor area to return to the cylinder 40.

[0094] In a preferred embodiment of the present disclosure, a slinging groove 37 may also be provided on the main convex rotor 10 and / or the auxiliary concave rotor 20, see Figure 7 、 Figure 8 and Figures 15A-15C . For example, for the main cam rotor 10, the sling groove 37 is shown here as having two circles, but the number is not limited to this, and more circles of sling grooves 37 can also be provided. The sling groove 37 on the outer ring near the cylinder 40 can be shallow on the outside and deep on the inside, for example, 0.1 to 2 mm, and is used to throw the fluid leaking from the cylinder 40 back to the cylinder 40 under the action of centrifugal force. The sling groove 37 on the inner ring near the main shaft 82 can be shallow on the outside and deep on the inside, for example, 0.2 to 3 mm, and is used to throw the sealing liquid or grease away from the central axis under the action of centrifugal force and prevent gas from leaking to the central axis. In this way, fluid leakage is further reduced.

[0095] In an exemplary embodiment of the present disclosure, see Figure 1 、 Figure 2 、 Figure 20 、 Figure 22 A spiral portion 81 is provided on the main shaft 82. When the main shaft 82 rotates during operation, the spiral portion 81 drives the fluid in the opposite direction of the fluid leakage. Figure 20 The spiral driving direction indicated by "H" and the gas leakage direction indicated by "G" in the figure. Similarly, a spiral portion can also be provided on the auxiliary shaft 83. The spiral portion 81 has opposite spiral directions on both sides of the turntable 1. A preferred embodiment of the present disclosure is deployed in a part or all of the area at least included between the two flow-blocking portions, and a sealing medium is provided in the gap between the main convex rotor 10 and the main stator 30 and / or between the auxiliary concave rotor 20 and the auxiliary stator 34. The sealing medium may include but is not limited to grease, lubricating fluid, boron nitride, graphite, molybdenum disulfide and other sealing or lubricating media with a very low friction coefficient, as well as liquids that form magnetic fluid seals. When a magnetic fluid sealing medium is used, a magnetic material needs to be provided on the stator at the magnetic fluid deployment position to attract the magnetic fluid to gather and thereby prevent gas leakage. When the main shaft 82 and the auxiliary shaft 83 rotate, the spiral portion 81 drives the liquid or grease in a direction opposite to the fluid leakage direction. In this way, fluid, ie, gas or liquid, that may leak during the operation of the rotating mechanism is prevented from leaking outward through the main shaft 82 and / or the auxiliary shaft 83, thereby improving the sealing performance.

[0096] See also Figure 22 In a preferred embodiment of the present disclosure, the rotating mechanism 100 further includes an autonomous sealing liquid circulation device 15 for autonomously circulating the sealing liquid between the end surface of the turntable 1 and the inner surface of the main stator 30. Figure 22 The solid arrow "M" in the figure indicates the direction in which the sealing liquid is driven by the spiral seal and centrifugal force, while the dashed arrow "G" indicates the direction of gas leakage. Preferably, the device 15 is deployed between two or more flow barriers near the shaft. Sealing liquid can flow in the gap between the main stator 30 and the main cam rotor 10 for sealing, cooling, lubrication, and other purposes. This liquid may include, but is not limited to, engine oil, lubricating oil, cooling oil, multi-purpose oil, water, magnetic fluid, or other low-friction, non-volatile liquids, as well as composite liquids. The sealing liquid circulation device 15, for example, includes an inlet 26 and a liquid collection section 27 provided on the main stator 30, a guide circuit 24 connecting the inlet 26 and the liquid collection section 27, and sealing liquid stored in the liquid collection section 27, accounting for, for example, 30% to 70% of the volume. Replenishment of the sealing liquid is required if the volume falls below, for example, 30%. The inlet 26, for example, is configured as a hole located in the low-pressure liquid flow barrier above the main shaft 82. The opening of the liquid collecting portion 27 is located at the gas high pressure area flow resistance portion below the main shaft 82, so that the pressure difference between the high pressure area and the low pressure area can be used to make the stored sealing liquid automatically circulate back along the guide loop 24 to the introduction portion 26 of the flow resistance portion above the main shaft 82 (such as Figure 22 (as shown by the arrow "T" in the figure), from here it enters the gap between the main stator 30 and the main convex rotor 10. Due to the centrifugal force and the driving force of the spiral seal, the sealing liquid follows the rotor from the flow-blocking part above the main shaft to rotate multiple circles and reaches the opening of the flow-blocking part below the main shaft 82, and is thrown back into the liquid collecting part 27 to restart the circulation. The guide circuit 24 can be designed as one or more return liquid pipes or return liquid channels, etc. The opening of the liquid collecting part 27 is arranged at the intersection area on the flow-blocking part where the expected pressure of the sealing liquid and the leakage gas is balanced. The sealing liquid circulation device 15 can be used on both the expansion ring and the compression ring.

[0097] In a preferred embodiment, a liquid recovery, storage and supply mechanism is provided for replenishing liquid for the sealing liquid circulation device 15 when the rotating mechanism 100 is stopped. Figure 22As shown, it includes a one-way driving mechanism such as a pump, a valve mechanism at the bottom of the cylinder, a sealing liquid recovery and storage mechanism 31 and a fluid replenishing pipe 32. The fluid replenishing pipe 32 connects the sealing liquid recovery and storage mechanism 31 to the liquid collecting part 27 in one direction. In the shutdown state, the gas pressure of the cylinder disappears, and the sealing liquid that has not flowed back to the liquid collecting part 27 due to various reasons such as the tilt of the equipment reaches the bottom of the cylinder 40 of the rotating mechanism 100 under the action of gravity. Open the valve at the bottom of the cylinder so that the sealing liquid falls into the liquid recovery and storage mechanism 31 to complete the recovery, thereby avoiding the liquid being burned and consumed after the next startup. When the rotating mechanism detects that the sealing liquid reserve amount in the liquid collecting part 27 is lower than a threshold value of, for example, 30%, a one-way driving mechanism such as a pump is used to pump the sealing liquid from the liquid recovery and storage mechanism 31 along the fluid replenishing pipe 32 to the liquid collecting part 27 (such as Figure 22 (as shown by the arrow "R" in the figure), thereby replenishing the sealing liquid lost due to volatilization, etc., see Figures 2 to 6 、 Figure 10 and Figure 22 .

[0098] In a preferred embodiment of the present disclosure, when the rotating mechanism 100 according to the present disclosure is a compressor, there is only a compression ring, and the cylinder 40 has only an air intake chamber 41 and a compression chamber 42, but no expansion ring and its expansion chamber 43 and exhaust chamber 44. When the rotating mechanism 100 according to the present disclosure is a vacuum machine (vacuum pump), the environment of the vacuum machine is basically opposite to that of the compressor, that is, the air intake end environment of the compressor is open, and the compressed air is stored or transferred to a closed environment, while the air intake end of the vacuum machine is in a sealed environment, and the air is extracted to an open environment. In a preferred embodiment of the present disclosure, when the rotating mechanism 100 according to the present disclosure is an expander, there is only an expansion ring, and the cylinder 40 has only an expansion chamber 43 and an exhaust chamber 44, and no compression ring and its air intake chamber 41 and compression chamber 42. When the rotating mechanism 100 according to the present disclosure is a liquid pump such as a water pump, it is only necessary to change the medium from gas to liquid, and the working principle is basically the same. In a preferred embodiment of the present disclosure, when the rotating mechanism 100 according to the present disclosure is a range extender, the compression ring and the expansion ring of the internal combustion engine work normally, but the main shaft does not output power to the outside, and the gears and the electromagnetic device cooperate to generate and output electricity as a generator. Alternatively, the main shaft outputs power to a separate generator to generate power and output electricity. In a preferred embodiment of the present disclosure, when the rotating mechanism 100 according to the present disclosure is a hybrid power device, the internal combustion engine performs work to output power, and the gears and the electromagnetic device cooperate to generate power as a generator and output power as an electric motor, thereby realizing hybrid power output. It can be seen that the rotating mechanism 100 according to the present disclosure is widely used.

[0099] The above describes a rotary mechanism according to the present disclosure, such as a hybrid power device, a range extender, an internal combustion engine, an expander, a compressor, a vacuum machine, or a liquid pump, and a sealing mechanism for sealing the same. In addition, the present disclosure also relates to a method for sealing a rotary mechanism 100, such as a hybrid power device, a range extender, an internal combustion engine, an expander, a compressor, a vacuum machine, or a liquid pump, wherein the rotary mechanism 100 is a rotary mechanism 100 according to the above disclosure of the present disclosure. In the method according to the present disclosure, it is provided that, as a sealing mechanism, a concave and / or convex first flow blocker 4 is provided on the end face of the turntable 1, and a convex and / or concave first corresponding flow blocker 5 that is non-contact with the first flow blocker 4, i.e., a clearance fit, is provided on the inner surface of the main stator 30, wherein a first concave and / or convex portion 6 is provided on the peripheral surface of the first flow blocker 4, and the peripheral surface of the first corresponding flow blocker 5 is constructed to be flat or provided with a first corresponding convex and / or concave portion 7 that is non-contact with the first concave and / or convex portion 6, i.e., a clearance fit. This method can significantly change the direction of working fluid leakage and significantly extend the fluid leakage path. The various designs of the rotary mechanism 100 and its sealing mechanism according to the present disclosure are also correspondingly applicable to the method according to the present disclosure, and the method according to the present disclosure can thus achieve the same advantages as the rotary mechanism 100 according to the present disclosure.

[0100] In a preferred embodiment of the method disclosed herein, a spiral seal, a labyrinth seal, a gap seal, a slot seal, a honeycomb seal, a brush seal, a sheet seal, and / or a magnetic fluid seal are used on the turntable 1 to prevent gas leakage. These seals can be achieved by using the various flow-blocking portions, recessed portions, and / or projecting portions described above that cooperate with each other.

[0101] In a preferred design of the method according to the present disclosure, the fluid leaked from the cylinder 40 is guided along the guide groove of the auxiliary stator 34 on the inner surface of the annular extension 28 of the auxiliary stator 34 to converge into the circumferential confluence groove and the fluid is brought back to the cylinder when the recessed portion rotates, thereby reducing fluid leakage toward the central axis of the auxiliary stator 34.

[0102] In a preferred design of the method according to the present disclosure, a sealing medium is provided in a gap between the rotary disk (1) and the stator (30) in a partial or entire area between at least two of the flow blocking portions to prevent leakage of the working fluid.

[0103] In a preferred design of the method according to the present disclosure, the sealing liquid is autonomously returned from the gas high-pressure zone resistance portion near the cylinder 40 below the main shaft to the liquid low-pressure zone resistance portion above the main shaft by using the pressure difference.

[0104] In a preferred embodiment of the method disclosed herein, a jump-fire mode can be used to enable intermittent operation of the internal combustion engine on demand. During a jump-fire, the internal combustion engine stops injecting fuel and igniting combustion. However, due to the energy stored in the flywheels of the primary and auxiliary rings being released, the internal combustion engine can continue to operate, thus saving fuel. This effect is far superior to reciprocating piston and eccentric shaft rotor engines. In a preferred embodiment of the method disclosed herein, the jump-fire mode can be used to precisely control the temperature of the internal combustion engine and / or the expansion ring and / or cylinder. During the jump-fire operation, the temperature of the expansion ring and cylinder 40 of the internal combustion engine gradually decreases.

[0105] In a preferred design of the method disclosed herein, the exhaust gas discharged from the exhaust chamber 44 of the expansion ring is partially returned to the expansion chamber 43 of the expansion ring through the multifunctional air chamber 80. There are two working scenarios: A) the internal combustion engine ignition and combustion work normally, for example, 10% to 30% of the exhaust gas returned from the waste return mechanism 70 is mixed with air through the multifunctional air chamber, in order to reduce NOx emission pollution. B) The internal combustion engine sparks work, and the exhaust gas stored in another air storage chamber or air storage tank (preferably with a three-way catalytic converter purification function) or the air storage / mixing multifunctional chamber or returned from the waste return mechanism 70 is returned to the multifunctional air chamber and mixed with compressed air and transferred to the expansion chamber 43 for expansion and work, thereby improving the work efficiency and saving fuel. In addition, the components in the exhaust gas that may not be fully burned (such as CO, HC) can continue to burn or oxidize in both working scenarios A / B, thereby reducing the emission of harmful substances in the exhaust gas.

[0106] In a preferred design of the method disclosed herein, the internal combustion engine can operate according to an operation plan. For example, after the internal combustion engine completes the i-th (i≥1) combustion cycle as planned, it ignites as planned according to operating conditions. In the subsequent i+j-th (j≥0) ignition cycle, fuel injection is stopped but air compression is continued, so that the exhaust gas stored in the air storage chamber or air storage tank (preferably having a three-way catalytic converter purification function) or the air storage / mixing multifunctional air chamber is partially returned to the expansion chamber 43 through the multifunctional air chamber to expand and perform work. In the i+j+p-th (p≥0) ignition cycle, fuel injection is stopped but air compression is continued. In the i+j+p+q-th (q≥0) ignition cycle, fuel injection is stopped and gas compression is stopped. This continues until the end of the current plan, and the next plan is started, starting from cycles 1 to i+j+p+q. The subsequent p+q cycles utilize the inertial flywheel effect of the main and auxiliary rings to release energy and perform work. The internal combustion engine can operate continuously according to the i+j+p+q cycle mode according to the operation plan, where i ≥ 1, j ≥ 0, p ≥ 0, and q ≥ 0. Flexible adjustment of the values ​​of i, j, p, and q can meet the power requirements and fuel conservation needs under various operating conditions.

[0107] In a preferred design of the method according to the present disclosure, fuel is injected and / or the air-fuel mixture is combusted in the multifunctional chamber 80 and / or the expansion chamber 43. Specifically, for example, fuel may not be injected into the multifunctional chamber 80, but fuel may be injected into the expansion chamber 43 and the compressed air-fuel mixture may be combusted. Alternatively, fuel may be injected into the multifunctional chamber 80, but the compressed air-fuel mixture may not be combusted there, but may be combusted and expanded in the expansion chamber 43 to produce work. Alternatively, fuel may be injected into the multifunctional chamber 80 and the compressed air-fuel mixture may be combusted, while expansion and work may be produced in the expansion chamber 43.

[0108] In a preferred design of the method according to the present invention, the same or different fuels are burned in the multifunctional air chamber 80 and the expansion chamber 43 at different times (in different cycles). For example, the mth (m≥1) cycle first triggers the combustion of the first fuel in the multifunctional air chamber 80, and then the m+nth (n≥1) cycle triggers the combustion of the first fuel in the expansion chamber 43; the cycles are alternating. Alternatively, the mth (m≥1) cycle first triggers the combustion of the first fuel in the multifunctional air chamber 80, and then the m+nth (n≥1) cycle triggers the combustion of the second fuel in the expansion chamber 43; the cycles are alternating. Flexible adjustment of the values ​​of m and n can meet the needs of various working conditions.

[0109] In a preferred design of the method according to the present disclosure, a small amount of the first fuel is injected into the multifunctional air chamber 80 and the mixture of compressed air and fuel is caused to burn, while an appropriate amount of the second fuel is injected into the expansion chamber 43 to continue burning, thereby supporting the partitioning and / or mixed combustion of the two fuels. Preferably, one of the two fuels can be methanol or a fuel containing methanol, which helps to remove carbon deposits or avoid the formation of carbon deposits during the combustion process. If the first fuel and the second fuel are the same fuel, partitioned and stratified combustion can also be achieved. The present disclosure is not limited to the methods listed above, and various methods can also be flexibly adopted as needed.

[0110] In a preferred embodiment of the method according to the present disclosure, the combustion of the air and fuel mixture is carried out by spark ignition or by compression ignition. The combustion of the air and fuel mixture can be carried out in the multifunctional chamber 80 and / or the expansion chamber 43 by spark ignition or by compression ignition, in particular lean homogeneous charge compression ignition.

[0111] While some embodiments of the present disclosure have been described for illustrative purposes, the present disclosure is not limited to these embodiments. Numerous modifications and variations are contemplated by those skilled in the art. Therefore, these embodiments are selected and described to better illustrate the principles and practical applications of the present disclosure and to enable those skilled in the art to understand its contents. That is, all modifications and variations made without departing from the spirit of the present disclosure are intended to fall within the scope of protection of the present disclosure as defined by the appended claims.

Claims

1. A sealing mechanism for a rotating mechanism, the rotating mechanism comprising: A rotor having a rotating disk (1); a stator accommodating the rotor; spindle (82); The sealing mechanism comprises: a convex first flow-blocking portion (4) provided on the end face of the turntable (1), the size of which allows a labyrinth seal and a spiral seal to be deployed thereon; and a concave first corresponding flow-blocking portion (5) provided on the inner surface of the stator and having a clearance fit with the first flow-blocking portion (4); wherein the first flow-blocking portion (4) has a first concave portion and / or convex portion (6) on its peripheral surface, and the first corresponding flow-blocking portion (5) is flatly constructed on its peripheral surface or has a first corresponding convex portion and / or concave portion (7) that has a clearance fit with the first concave portion and / or convex portion (6), wherein the first flow-blocking portion (4) and the first corresponding flow-blocking portion (5) respectively form a labyrinth seal on their corresponding top sections, and respectively form a spiral seal on their corresponding side sections that are nearly parallel to or not perpendicular to the main shaft (82).

2. The sealing mechanism according to claim 1, wherein: The end surface of the turntable (1) is provided with a second concave portion and / or a convex portion (8), and the inner surface of the stator is provided with a corresponding second convex portion and / or concave portion (9) which is clearance-matched with the second concave portion and / or convex portion (8) and / or is provided with a brush seal structure and / or a sheet seal structure.

3. The sealing mechanism according to claim 2, wherein: The second recessed portion and / or raised portion (8) and the corresponding second raised portion and / or recessed portion (9) form a labyrinth seal.

4. The sealing mechanism according to claim 3, wherein: A sealing medium is provided in a part or all of a region between at least two of the first flow blocking parts (4) and in a gap between the rotating disk (1) and the stator (30).

5. The sealing mechanism according to claim 4, wherein: The sealing medium is one or more of grease, lubricating liquid, magnetic fluid, and self-lubricating material.

6. The sealing mechanism according to any one of claims 1 to 5, wherein: The rotor has a piston (2) connected to the edge of the rotary disk (1), and the stator (30) surrounds the piston (2) so that a cavity serving as a cylinder (40) is formed on the rotation path of the piston (2).

7. The sealing mechanism according to claim 6, wherein: The rotary disc (1) has a third flow blocking portion (17) located on the bottom side and / or the side of the piston (2) and the cylinder (40) and partially surrounding the piston (2) and the cylinder (40).

8. The sealing mechanism according to claim 7, wherein: The third flow blocking portion (17) has a third concave portion and / or convex portion (12) on its peripheral surface.

9. The sealing mechanism according to claim 6, wherein: The piston (2) has a fourth recess (11) on its top side.

10. The sealing mechanism according to claim 6, wherein: The rotor is a main convex rotor (10), the stator is a main stator (30), and the rotating mechanism (100) further includes an auxiliary concave rotor (20) and an auxiliary stator (34) for accommodating the auxiliary concave rotor (20). The auxiliary concave rotor (20) has an auxiliary rotating disk (25) and an annular extension (28) surrounding the auxiliary rotating disk (25). The annular extension (28) has a concave portion (3). The concave portion (3) cooperates with the piston (2) so that the piston (2) can be accommodated by and pass through the concave portion (3) during rotation.

11. The sealing mechanism according to claim 10, wherein: The auxiliary rotating disk (25) of the auxiliary concave rotor (20) has a concave and / or convex second flow blocking portion (13) arranged on its end surface, and the auxiliary stator (34) has a convex and / or concave second corresponding flow blocking portion (14) arranged on its inner surface and gap-fitted with the second flow blocking portion (13).

12. The sealing mechanism according to claim 11, wherein: The second flow-blocking portion (13) and the second corresponding flow-blocking portion (14) are flatly constructed on their peripheral surfaces or have a fifth convex portion and / or concave portion and a fifth corresponding concave portion and / or convex portion that are clearance-matched with each other; and the end surface on the auxiliary rotating disk (25) is locally flatly constructed or provided with a sixth convex portion and / or concave portion.

13. The sealing mechanism according to claim 10, wherein: The auxiliary stator (34) has a circumferential confluence groove (36) and a guide groove (35) connected to the circumferential confluence groove (36) on its inner surface wrapping the annular extension portion (28).

14. The sealing mechanism according to claim 10, wherein: A slinging groove (37) is provided on the rotating disk (1) of the main convex rotor (10) and / or the auxiliary concave rotor (20).

15. The sealing mechanism according to any one of claims 1 to 5, wherein: The rotating mechanism (100) is an internal combustion engine, an expander, a compressor or a pump.

16. A rotating mechanism (100), comprising: A main convex rotor (10), the main convex rotor (10) having a rotating disk (1) and a piston (2), the piston (2) being connected to the edge of the rotating disk (1); a main stator (30) accommodating the main convex rotor (10), wherein a cavity for accommodating the piston (2) is formed inside the main stator (30) on the rotation path of the piston (2) as a cylinder (40); Wherein, the rotating mechanism (100) comprises a sealing mechanism according to any one of the preceding claims.

17. The rotating mechanism (100) according to claim 16, wherein: The rear surface of the piston (2) with reference to its rotation direction is a plane or a concave surface, and the front surface of the piston (2) with reference to its rotation direction is a convex surface or a concave surface or a plane surface.

18. The rotating mechanism (100) according to claim 16, wherein: The shape of the piston (2) is circular, oval or rounded rectangular.

19. The rotating mechanism (100) according to any one of claims 16 to 18, wherein: The rotating mechanism (100) further includes an autonomous sealed liquid circulation device (15), the sealed liquid circulation device (15) having an introduction portion (26) and a liquid collecting portion (27) opened on the main stator (30), and a guide circuit (24) connecting the introduction portion (26) of the liquid low-pressure zone resistance portion located above the main shaft and the liquid collecting portion (27) of the gas high-pressure zone resistance portion located below the main shaft.

20. The rotating mechanism (100) according to claim 19, wherein: The rotating mechanism (100) further comprises a liquid recovery, storage and replenishment mechanism for the sealed liquid circulation device (15) in its stopped state, wherein the liquid recovery, storage and replenishment mechanism comprises a one-way drive mechanism, a liquid recovery and storage mechanism (31) and a liquid replenishment pipe (32).

21. The rotating mechanism (100) according to any one of claims 16 to 18, wherein: The rotating mechanism (100) further includes a cylinder cut-off mechanism, which cuts off the cylinder (40), so that the volume of the cylinder (40) can be changed as the piston (2) rotates.

22. The rotating mechanism (100) according to claim 21, wherein: The cylinder shutoff mechanism is an auxiliary concave rotor (20) or a card. The auxiliary concave rotor (20) has an auxiliary rotating disk (25) and an annular extension (28) surrounding the auxiliary rotating disk (25). The annular extension (28) also has a concave portion (3) that cooperates with the piston (2). The cylinder (40) is shut off by the annular extension (28) of the auxiliary concave rotor (20) or the card.

23. The rotating mechanism (100) according to claim 22, wherein: The rotating mechanism (100) further includes a main shaft (82) connecting the main stator (30) and the main convex rotor (10), and an auxiliary shaft (83) connecting the auxiliary stator (34) and the auxiliary concave rotor (20). Spiral portions (81) are provided on the main shaft (82) and the auxiliary shaft (83). When the main shaft (82) and the auxiliary shaft (83) rotate, the spiral portions (81) drive the fluid or grease in a direction opposite to the leakage direction.

24. The rotating mechanism (100) according to claim 23, wherein: The rotating mechanism (100) comprises a main gear (71) connected to the main shaft (82) and an auxiliary gear (72) connected to the auxiliary shaft (83), wherein a transmission ratio between the main gear (71) and the auxiliary gear (72) is 1:n, wherein n≥1.

25. The rotating mechanism (100) according to claim 24, wherein: The rotating mechanism (100) includes a compression ring, and the compression ring includes an air intake chamber (41) and a compression chamber (42) of the cylinder (40).

26. The rotating mechanism (100) according to claim 25, wherein: The compression ring includes a valve (38) for regulating the amount of air intake.

27. The rotating mechanism (100) according to claim 25, wherein: The rotating mechanism (100) includes an expansion ring, and the expansion ring includes an expansion chamber (43) and an exhaust chamber (44) of the cylinder (40).

28. The rotating mechanism (100) according to claim 27, wherein: The expansion ring has an exhaust pipe (73) and / or a fuel nozzle (21) and / or a spark plug (23).

29. The rotating mechanism (100) according to claim 28, wherein: The rotating mechanism (100) further comprises a multifunctional air chamber (80) connected between the expansion chamber (43) of the expansion ring and the compression chamber (42) of the compression ring via a connecting pipe (84) provided with a one-way valve. The multifunctional air chamber (80) has an additional fuel injection mechanism (16) and / or an additional spark plug (85), and has one or more functions of gas storage, gas mixing, and / or combustion.

30. The rotating mechanism (100) according to claim 29, wherein: The rotating mechanism (100) injects a single or different fuels in the multifunctional air chamber (80) through the additional fuel injection mechanism (16) and / or in the expansion chamber (43) through the fuel nozzle (21).

31. The rotating mechanism (100) according to claim 30, wherein: The rotating mechanism (100) performs compression ignition in the multifunctional air chamber (80) and / or the expansion chamber (43) or ignites a mixture of air and fuel through the spark plug.

32. The rotating mechanism (100) according to claim 31, wherein: The rotating mechanism (100) operates intermittently as required by sparking, and / or controls the temperature of the expansion ring and the cylinder.

33. The rotating mechanism (100) according to claim 29, wherein: The rotating mechanism (100) further comprises a one-way exhaust gas return mechanism (70) connected between the multifunctional air chamber (80) and the exhaust pipe (73).

34. The rotating mechanism (100) according to claim 27, wherein: The rotating mechanism (100) further comprises a fairing housing (50) and a fan (60), wherein the fairing housing (50) at least accommodates the compression ring and / or the expansion ring and the fan (60), and a fan (60) is provided between the expansion ring and the compression ring. The profile portion is formed so that an air duct for guiding air flow is formed in the fairing shell (50).

35. The rotating mechanism (100) according to claim 34, wherein: The fan (60), the expansion ring, the compression ring and the gear are connected in sequence through the main shaft (82).

36. The rotating mechanism (100) according to claim 24, wherein: The rotating mechanism (100) further includes an electromagnetic device (90), wherein the electromagnetic device (90) includes a fixed induction coil (96) close to the main gear (71), a bearing portion (97) bearing the induction coil (96), and a first magnet (95) arranged on the main gear (71).

37. The rotating mechanism (100) according to claim 36, wherein: The first magnet (95) on the main gear (71) rotates relative to the induction coil (96), thereby generating electricity; and the current magnitude, direction and frequency of the induction coil (96) are controlled so that the main gear (71) is driven to rotate through the first magnet (95), thereby generating power.

38. The rotating mechanism (100) according to claim 24, wherein: The rotating mechanism (100) further comprises a piston position maintaining device (98), wherein the piston position maintaining device (98) comprises a second magnet (91), a pressure relief member (92), a spring (93) and a casing (94).

39. The rotating mechanism (100) according to any one of claims 16 to 18, wherein: The rotating mechanism (100) is an internal combustion engine, an expander, a compressor or a pump.

40. A method for sealing a rotating mechanism (100) according to any one of claims 16 to 39, the rotating mechanism (100) comprising: A main convex rotor (10), the main convex rotor (10) having a rotating disk (1) and a piston (2), the piston (2) being connected to the edge of the rotating disk (1); An auxiliary concave rotor (20), the auxiliary concave rotor (20) comprising an auxiliary rotating disk (25), an annular extension (28), and a concave portion (3) cooperating with the piston (2); a main stator (30) and an auxiliary stator (34), the main stator (30) and the auxiliary stator (34) respectively accommodating the main convex rotor (10) and the auxiliary concave rotor (20), wherein a cavity serving as a cylinder (40) is formed inside the main stator (30) on a path along which the piston (2) rotates; A sealing mechanism is provided for the rotating mechanism (100), the sealing mechanism comprising: a concave and / or convex first flow-blocking portion (4) provided on the end surface of the turntable (1); and a convex and / or concave first corresponding flow-blocking portion (5) provided on the inner surface of the main stator (30) and having a clearance fit with the first flow-blocking portion (4).

41. The method according to claim 40, wherein A third flow blocking portion is provided on the edge of the rotary disk (1) and partially surrounds the bottom side and / or side of the piston and the cylinder.

42. The method of claim 40, wherein: On the inner surface of the auxiliary stator (34), the leaked gas is guided along the guide groove of the auxiliary stator (34) to converge toward the circumferential confluence groove away from the leakage gap, and is brought back to the cylinder (40) by the concave portion during rotation.

43. The method of claim 40, wherein: In a partial or entire region between at least two of the first flow blocking parts (4), a sealing medium is provided in the gap between the rotating disk (1) and the stator (30) to prevent leakage of the working fluid.

44. The method according to claim 43, wherein The sealing liquid is made to autonomously return from the gas high-pressure zone resistance portion below the main shaft (82) close to the cylinder (40) to the liquid low-pressure zone resistance portion above the main shaft (82) close to the main shaft (82) by utilizing the pressure difference.

45. The method of claim 40, wherein The exhaust gas discharged from the exhaust chamber (44) of the expansion ring of the rotating mechanism (100) partially enters the multifunctional air chamber (80) and is mixed with the compressed air.

46. ​​The method of claim 40, wherein The fan blows outside air into the fairing shell (50) to form an air duct for guiding the air flow, and the air cools the hot expansion ring. The cold air takes away the heat energy of the expansion ring and turns into hot air, which is sucked into the compression ring of the rotating mechanism (100) for air intake compression and participates in work, so that the heat energy lost by cooling the expansion ring is recovered in a closed loop.

47. The method of claim 40, wherein The combustion of the injected single or different fuels and / or air and fuel mixture is carried out in the multifunctional air chamber (80) and / or the expansion chamber (43).

48. The method of claim 47, wherein Combustion of the air and fuel mixture occurs by spark ignition or by compression ignition.

49. The method according to claim 48, wherein The internal combustion engine is operated intermittently as needed by sparking.

50. The method of claim 49, wherein The expansion ring and / or cylinder temperature is controlled by sparking.

51. The method of claim 49, wherein According to the operating plan, after the internal combustion engine completes the i-th combustion cycle, the fuel injection is stopped in the subsequent i+j-th sparking cycle and the exhaust gas is partially mixed with the compressed air through the multifunctional air chamber (80) and returned to the expansion chamber (43) to expand and perform work, and the fuel injection is stopped in the subsequent i+j+p-th sparking cycle without stopping the air compression, and the fuel injection is stopped and the air compression is stopped in the i+j+p+q-th sparking cycle, wherein i≥1, j, p, q>0.

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