Rotating mechanism, and sealing mechanism and sealing method therefor

Abstract

A sealing mechanism for a rotating mechanism, a rotating mechanism and a sealing method. The rotating mechanism comprises a rotor having a rotary disk (1) and a stator accommodating the rotor. The sealing mechanism comprises a first flow-blocking portion (4), which protrudes and is provided on an end face of the rotary disk (1), wherein a labyrinth seal and a spiral seal are provided in combination at the first flow-blocking portion (4); and a first corresponding flow-blocking portion (5), which is recessed, is provided on an inner surface of the stator and is in clearance fit with the first flow-blocking portion (4). The first flow-blocking portion (4) has a first recessed portion and / or protruding portion (6) on a circumferential surface thereof, the first corresponding flow-blocking portion (5) is flatly constructed or provided, on a circumferential surface thereof, with a first corresponding protruding portion and / or recessed portion (7) which are / is in clearance fit with the first recessed portion and / or protruding portion (6), and the first flow-blocking portion (4) and the first corresponding flow-blocking portion (5) form a labyrinth seal at the corresponding top or bottom section thereof respectively and form a spiral seal at a corresponding side section respectively, which can further suppress fluid leakage, thereby improving the sealing performance.

Description

Rotary mechanism and sealing mechanism and sealing method thereof TECHNICAL FIELD

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

[0002] An internal combustion engine is a power machine that converts heat energy into mechanical energy by burning a mixture of air and fuel, which can be mainly divided into continuous combustion gas turbines and intermittent combustion reciprocating piston internal combustion engines and eccentric shaft rotor internal combustion engines. The gas turbine (including turbojet, turbofan, turbo shaft, etc.) has high speed, large power and high power-to-weight ratio, but continuous combustion leads to very high fuel consumption and high manufacturing cost. The reciprocating piston internal combustion engine realizes the four strokes of intake, compression, expansion and exhaust through the reciprocating motion of the piston in a single cylinder, has the advantages of low fuel consumption and low manufacturing cost, but also has the problems of low power-to-weight ratio, low speed, energy waste of reciprocating motion, etc. Both types of internal combustion engines have been mass-produced. The eccentric shaft rotor internal combustion engine has the advantages of high speed and small size, but also has the disadvantages of high fuel consumption, poor sealing, large friction and wear, poor durability, incomplete combustion, and non-compliance with emission standards. The poor sealing of eccentric shaft or other types of rotor engines has been a century-old problem that hinders the development of rotor engines. SUMMARY

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

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

[0005] a rotor, the rotor having a rotating disc;

[0006] a stator, the stator accommodating the rotor.

[0007] According to the present disclosure, the sealing mechanism comprises: a first flow blocking part arranged on the end face of the rotating disc in a concave and / or convex shape; a first corresponding flow blocking part arranged on the inner surface of the stator in a convex and / or concave shape in a clearance fit with the first flow blocking part; wherein the first flow blocking part is flatly configured on its peripheral face or has a first concave and / or convex part, and the first corresponding flow blocking part is flatly configured on its peripheral face or has a first corresponding convex and / or concave part in a clearance fit with the first concave and / or convex part, wherein the first flow blocking part and the first corresponding flow blocking part respectively form a labyrinth seal on their corresponding top or bottom sections and respectively form a spiral seal on their corresponding one side sections. In a preferred embodiment, the first flow blocking part and the first corresponding flow blocking part respectively form a spiral seal or a labyrinth seal on their corresponding other side sections.

[0008] The flow blocking part is usually much larger than the (labyrinth or other) seal. Through the flow blocking part of the sealing mechanism of the present disclosure, the leakage direction of the working fluid can be greatly changed, and the leakage path of the working fluid can be greatly extended, solving the problem of insufficient sealing space of the conventional rotating mechanism, so that more seals and various different kinds of seals can be deployed on the leakage path to prevent the leakage of the working fluid. The composite structure and the large number of seals used after extending the leakage path can basically solve the working fluid leakage problem of the rotating mechanism.

[0009] In an embodiment according to the first aspect of the present disclosure, a second concave and / or convex part is locally flatly configured or arranged on the end face of the rotating disc, and a corresponding second convex and / or concave part in a clearance fit with the second concave and / or convex part is locally flatly configured or arranged on the inner surface of the stator, forming a labyrinth seal, further improving the sealing performance. A hole groove sealing structure and / or a honeycomb sealing structure and / or a brush sealing structure and / or a sheet sealing structure is arranged on the stator wrapping the rotating disc. Through the hole groove sealing and / or the honeycomb sealing and / or the brush sealing and / or the sheet sealing, the fluid leakage amount can be greatly reduced. In this way, the sealing performance is further improved.

[0010] In an embodiment according to the first aspect of the present disclosure, the first concave and / or convex part and the first corresponding convex and / or concave part and the second concave and / or convex part and the corresponding second convex and / or concave part form a spiral seal and / or a labyrinth seal and / or a clearance seal. Through the spiral seal arranged on the side face of the flow blocking part, the fluid is driven in the direction opposite to the leakage direction of the working fluid. Through the labyrinth seal and / or the hole groove seal and / or the honeycomb seal, pressure drop and vortex are generated, the fluid leakage pressure is reduced, the fluid leakage is further inhibited, and the sealing performance is improved.

[0011] In an embodiment according to the first aspect of the present disclosure, a sealing medium is arranged in the gap between the rotor and the stator in the part or all of the area between the at least two flow blocking parts. The sealing medium can be one or more of a lubricating grease, a lubricating liquid, a cooling liquid, a magnetic fluid, a self-lubricating material. By using a sealing medium in the gap between the rotor and the stator, fluid leakage can be blocked.

[0012] In an embodiment according to the first aspect of the present disclosure, the rotor has a piston connected to the edge of the rotor disc, and the stator surrounds the piston, so that a cavity as a cylinder is formed in the path of the rotation of the piston.

[0013] In an embodiment according to the first aspect of the present disclosure, the rotor disc has a third flow blocking part partially surrounding the piston and the cylinder on the bottom side and / or the side of the piston. With the third flow blocking part, the leakage direction can be greatly changed, the leakage path can be greatly extended, and the working fluid can be prevented from leaking directly towards the central axis area of the rotor disc, thus further improving the sealing performance. In an embodiment of the present disclosure, the third flow blocking part has a third recess and / or protrusion on its peripheral surface, which helps to further improve the sealing performance.

[0014] In an embodiment according to the first aspect of the present disclosure, the piston has a fourth recess on its top side. By means of the special design of the pressure relief groove on the top side of the piston, the leakage gas generates pressure drop and vortex, inhibiting the gas from flowing to the opposite side, thus improving the sealing performance.

[0015] In an 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 connected to the edge of the rotor disc, and the rotating mechanism further comprises an auxiliary concave rotor and an auxiliary stator accommodating the auxiliary concave rotor, the auxiliary concave rotor has an auxiliary rotor disc and an annular extension part surrounding the auxiliary rotor disc on the periphery, the annular extension part has a recessed part cooperating with the piston, and the piston can be accommodated and passed through the recessed part when the piston rotates. In an embodiment according to the first aspect of the present disclosure, the auxiliary rotor disc of the auxiliary concave rotor has a second flow blocking part of a concave and / or convex shape arranged on its end face, and the auxiliary stator has a second corresponding flow blocking part of a convex and / or concave shape arranged on its inner surface and cooperating with the second flow blocking part. 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 of the conventional auxiliary rotating mechanism is solved.

[0016] In an embodiment according to the first aspect of the present disclosure, the auxiliary stator has a circumferential flow collecting groove on its inner side and a flow guiding groove in communication therewith. In an embodiment of the present disclosure, a flow throwing groove is arranged on the rotor disc of the main convex rotor and / or the auxiliary concave rotor. In this way, the sealing performance is improved.

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

[0018] According to a second aspect of the present disclosure, a rotating mechanism is provided, which comprises:

[0019] a main convex rotor having a rotating disc and a piston connected to the edge of the rotating disc; a main stator accommodating the main convex rotor, wherein a cavity as a cylinder is formed inside the main stator on the path of the rotation of the piston.

[0020] In the present disclosure, the rotating mechanism comprises 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 accordingly.

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

[0022] In one embodiment of the second aspect of the present disclosure, the piston is circular or elliptical or circular-rectangular. The circular or elliptical piston makes the gas combustion in the circular or elliptical ring-shaped cylinder of the same shape more sufficient and the combustion efficiency higher, and also makes the thermal stress on the piston more uniform, avoiding thermal deformation of the piston and causing cylinder seizure.

[0023] In one embodiment of the second aspect of the present disclosure, the rotating mechanism further comprises a sealing liquid circulating device for realizing self-circulation work by pressure difference, which has an introduction part and a liquid collecting part opened on the main stator and a guide circuit connecting the introduction part of the liquid low-pressure area blocking part above the main shaft and the liquid collecting part of the gas high-pressure area blocking part below the main shaft. The liquid may, for example, be used for sealing, cooling and lubrication. Thus, the sealing liquid can be used to automatically circulate in a closed loop to prevent gas leakage, improving the sealing performance.

[0024] In one embodiment of the second aspect of the present disclosure, the rotating mechanism further comprises a liquid recovery, storage and replenishment mechanism for cooperating with the sealing liquid circulating device in its shutdown state, which comprises a one-way drive mechanism, a liquid recovery and storage mechanism and a liquid replenishment pipe. Thus, the liquid leaked into the cylinder due to various reasons after shutdown and the liquid lost due to evaporation and other reasons can be recovered in a closed loop.

[0025] In an embodiment according to the second aspect of the present disclosure, the rotating mechanism further comprises a cylinder cutting mechanism which cuts the cylinder to make the cylinder variable in volume with the rotation of the piston. In an embodiment according to the second aspect of the present disclosure, the cylinder cutting mechanism is a secondary concave rotor or a card, the secondary concave rotor having a secondary rotor disc and an annular extension surrounding the secondary rotor disc, the annular extension having a concave recess cooperating with the piston, the cylinder being cut by the annular extension of the secondary concave rotor or the card and variable in volume with the rotation of the piston. In an embodiment according to the second aspect of the present disclosure, the rotating mechanism further comprises a main shaft connecting the main stator and the main convex rotor and a secondary shaft connecting the secondary stator and the secondary concave rotor, a helical portion being provided on the main shaft, the helical portion driving fluid or grease in a direction opposite to leakage when the main shaft rotates in operation.

[0026] In an embodiment according to the second aspect of the present disclosure, the rotating mechanism comprises a main gear connected with the main shaft and a secondary gear connected with the secondary shaft, the transmission ratio of the main gear and the secondary gear being 1:n, wherein n≥1. The larger n is, the smaller the secondary concave rotor is. In this way, the size and weight of the secondary concave rotor can be reduced, and the power to weight ratio of the rotating mechanism can be increased.

[0027] In an embodiment according to the second aspect of the present disclosure, the rotating mechanism comprises a compression ring, the cylinder of which is divided by the piston into an intake chamber and a compression chamber. In an embodiment according to the second aspect of the present disclosure, the compression ring further comprises a valve for adjusting the intake amount of the cylinder. With the valve, the intake amount of the cylinder can be adjusted as needed, and the compression ratio can be flexibly adjusted and the power of the rotating mechanism can be controlled. In an embodiment according to the second aspect of the present disclosure, the rotating mechanism comprises an expansion ring, the cylinder of which is divided by the piston into an expansion chamber and an exhaust chamber. In an embodiment according to the second aspect of the present disclosure, the expansion ring further comprises an exhaust pipe and / or a fuel nozzle and / or a spark plug.

[0028] In an embodiment according to the second aspect of the present disclosure, the rotating mechanism comprises a multifunctional gas chamber provided with a one-way valve between the expansion chamber of the expansion ring and the compression chamber of the compression ring, the multifunctional gas chamber having a fuel nozzle and / or a spark plug, and having the functions of gas storage and / or gas mixing and / or combustion. In this way, various mixing and combustion modes of air and fuel can be flexibly realized. In an embodiment according to the second aspect of the present disclosure, the rotating mechanism injects single or different fuels in the multifunctional gas chamber through an additional fuel injection mechanism and / or in the expansion chamber through the fuel nozzle. In an embodiment according to the second aspect of the present disclosure, the rotating mechanism compresses and ignites the mixture of air and fuel in the multifunctional gas chamber and / or in the expansion chamber. In an embodiment according to the second aspect of the present disclosure, the rotating mechanism can be intermittently operated on demand by misfire, and the temperature of the cylinder of the expansion ring can be controlled, and fuel can be saved.

[0029] In an embodiment according to the second aspect of the present disclosure, the rotating mechanism further comprises a one-way exhaust gas return mechanism connected between the multi-functional air chamber and the exhaust chamber, for allowing the exhaust gas discharged from the exhaust chamber to partially enter the multi-functional air chamber to mix with the compressed air. In this way, the work efficiency and exhaust gas utilization rate can be improved, and the harmful substance NOx emission can be reduced.

[0030] In an 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 the compression ring and / or the expansion ring and the fan, and the air duct for guiding the air flow is formed in the fairing housing. In a preferred embodiment according to the second aspect of the present disclosure, the fan, the expansion ring, the compression ring and the gear are sequentially connected by the shaft. In an embodiment according to the second aspect of the present disclosure, the air duct is formed between the expansion ring and the compression ring. In an embodiment according to the second aspect of the present disclosure, the fan, the expansion ring, the compression ring and the gear are sequentially connected by the shaft. At this time In an embodiment according to the second aspect of the present disclosure, the fan, the expansion ring, the compression ring and the gear are sequentially connected by the shaft. At this time

[0031] ​​​In an embodiment according to the second aspect of the present disclosure, the rotating mechanism further comprises an electromagnetic device comprising an induction coil and a carrier carrying the induction coil, and a magnet disposed on the main gear. The magnet rotates relative to the induction coil to generate electricity. The current size, direction and frequency of the induction coil are controlled to make the magnet drive the gear to rotate, thereby generating power. In an embodiment according to the second aspect of the present disclosure, the rotating mechanism further comprises a piston position holding device comprising 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 comprises a magnet, a pressure relief member, a spring and a casing. In an embodiment according to the second aspect of the present disclosure, the rotating mechanism is a hybrid device, a range extender, an internal combustion engine, an expander, a compressor or a pump.

[0032] According to the third aspect of the present disclosure, a method for sealing a rotating mechanism according to the above is proposed. According to the method of the present disclosure, a sealing mechanism is provided for the rotating mechanism, which comprises: a concave and / or convex first flow blocking part disposed on the end face of the rotating disc; a convex and / or concave first corresponding flow blocking part disposed on the inner surface of the main stator in gap cooperation with the first flow blocking part, wherein the peripheral surface of the first flow blocking part is flatly configured or provided with a first concave and / or convex part, and the peripheral surface of the first corresponding flow blocking part is flatly configured or provided with a first corresponding convex and / or concave part in gap cooperation with the first concave and / or convex part.

[0033] In an embodiment according to the third aspect of the present disclosure, a third flow blocking part is disposed on the edge of the rotating disc to partially surround the bottom side and / or side of the piston and the cylinder. On the inner surface of the auxiliary stator, the leaked gas is guided along the flow guide groove to the circumferential flow groove away from the leakage gap, and is gathered and brought back to the cylinder by the concave part when rotating. In the partial or entire area between the at least two flow blocking parts, a sealing medium is provided in the gap between the rotating disc and the stator to block the leakage of working fluid. The sealing liquid is caused to return from the high-pressure gas area near the cylinder below the main shaft to the low-pressure liquid area near the main shaft above the main shaft by pressure difference.

[0034] In an embodiment according to the third aspect of the present disclosure, a single or different fuels are injected in the multi-functional chamber and / or the expansion chamber and / or combustion of the air-fuel mixture is carried out. In this case, the combustion of the air-fuel mixture is carried out by spark plug ignition or by compression ignition. The location and the combustion mode of the fuel injection and the combustion of the air-fuel mixture can thus be flexibly selected. In an embodiment according to the third aspect of the present disclosure, the fan blows ambient air into the fairing housing to form an air duct guiding the air flow, the air cooling the hot expansion ring, the cold air taking away the thermal energy of the expansion ring to become hot air, which is sucked into the intake by the compression ring to participate in the work, so that the thermal energy lost by the expansion ring is recycled in a closed loop. In another embodiment according to the third aspect of the present disclosure, the exhaust gas discharged from the exhaust pipe of the expansion ring in the tail region of the air duct mixes with the air in the air duct and expands, and is discharged through the tail jet outlet of the rotating mechanism, thereby generating thrust to power the device equipped with the rotating mechanism, further making full use of the energy in the hot exhaust gas, and improving the energy utilization efficiency.

[0035] In an embodiment according to the third aspect of the present disclosure, according to the operating plan under different working conditions, after the i-th combustion cycle of the internal combustion engine is completed, fuel injection is stopped in the subsequent i+j-th misfire cycle, and the exhaust gas partially passes through the multi-functional chamber mixed with compressed air to return to the expansion chamber for expansion work, fuel injection is stopped in the subsequent i+j+p-th misfire cycle, and air compression is not stopped, fuel injection is stopped in the i+j+p+q-th misfire cycle, and air compression is stopped, where i≥1, j, p, q≥0, and at least one of j, p, q is not 0. In this way, the power demand and fuel saving demand under various working conditions can be met by adjusting the values of i, j, p, q.

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

[0037] For better understanding of the above and other objects, features and advantages of the present disclosure, reference should be made to the preferred embodiments thereof illustrated in the accompanying drawings. Identical reference numerals in the drawings refer to the same components. It should be understood by those skilled in the art that the drawings are intended to schematically illustrate the preferred embodiments of the present disclosure, and have no limiting effect on the scope of the present disclosure, and the various components in the drawings are not drawn to scale.

[0038] Fig. 1 is a general top view of a rotating mechanism according to an exemplary embodiment of the present disclosure;

[0039] Fig. 2 is a side view of the rotating mechanism of Fig. 1;

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

[0041] Figure 4 is a perspective view of the housing of the rotary mechanism without the fairing;

[0042] Figure 5 is a front view of the rotary mechanism of Figure 4 without the fan;

[0043] Figure 6 is a front view of the rotary mechanism of Figure 5 without the rotor and the front half of the primary / secondary stator, wherein the secondary stator shows an embodiment of the fling groove;

[0044] Figure 7 is a front view of the rotary mechanism of Figure 4 with the rotor and without the front half of the primary / secondary stator;

[0045] Figure 8 is a front view of the primary male rotor and the secondary female stator of the rotary mechanism;

[0046] Figure 9 shows the circumferential flow collection groove and the flow guide groove on the secondary stator of the rotary mechanism;

[0047] Figure 10 is a partially exploded perspective view of the rotary mechanism;

[0048] Figure 11 is an assembled perspective view of the multi-functional plenum of the rotary mechanism;

[0049] Figure 12 is a top perspective view of the rotary mechanism of Figure 4;

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

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

[0052] Figures 15A-15C are combined perspective views of the primary male rotor and the secondary female stator of the rotary mechanism, showing three embodiments of the third flow blocking portion of the rotor disc, respectively, without the third flow blocking portion, with a middle cup shape, and with a high cup shape;

[0053] Figures 16A-16C show five different design embodiments of the rotor disc and the piston of the primary male rotor of the rotary mechanism;

[0054] Figures 17A-17C show three sets of six different design embodiments of the rotor disc of the primary male rotor of the rotary mechanism;

[0055] Figure 18 is a partially cut-away view of the primary stator and the primary male rotor of the internal combustion engine;

[0056] Figures 19A-19D show four sets of eight different design embodiments of the first flow blocking portion on the rotor disc and the first corresponding flow blocking portion on the primary stator;

[0057] Figure 20 shows an overall design embodiment of the first flow blocking portion on the rotor disc and the first corresponding flow blocking portion on the primary stator;

[0058] Fig. 21 shows the principle of using spiral seal and labyrinth seal to suppress gas leakage through the first choke and the first corresponding choke, the first / second convex part and / or concave part and the first / second corresponding concave part and convex part;

[0059] Fig. 22 is a schematic diagram of the principle of the sealing liquid circulation device of the rotating mechanism and the liquid recovery storage and supply mechanism;

[0060] Fig. 23 shows the design of the top side of the piston of the rotating mechanism;

[0061] Figs. 24A-24E show the gas-pushed side design of the piston;

[0062] Figs. 25A, 25B are different number of matching diagrams of the main convex rotor and the auxiliary concave rotor;

[0063] Fig. 26 is a matching diagram of the main convex rotor and the auxiliary concave rotor saving one auxiliary concave rotor; and

[0064] Figs. 27A-27D show the working principle diagram of the split synchronous four-in-one stroke ring rotating engine of the rotating mechanism. DETAILED DESCRIPTION

[0065] The detailed description of the drawings according to the specific embodiments and examples of the present disclosure. What is described here is only the preferred embodiment according to the present disclosure, and those skilled in the art can think of other ways to achieve the present disclosure on the basis of the preferred embodiment, and other ways also fall within the scope of the present disclosure.

[0066] Referring to FIGS. 1-3, a rotary mechanism 100 according to one example embodiment of the present disclosure is shown. It is noted that the rotary mechanism 100 according to the present disclosure can be, for example, a hybrid device, a range extender, an internal combustion engine, an expander, a compressor, a vacuum machine (pump), or a liquid pump, but is not limited thereto, and can encompass various types of rotary mechanisms. In internal combustion engine, expander, compressor applications, the working fluid is a gas or a mixture of gases. In pump applications, the working fluid can be either a gas or a liquid. The following description of the rotary mechanism 100 according to the present disclosure is mainly based on an internal combustion engine that includes expander and compressor functions. As seen from these figures, the rotary mechanism 100 (e.g., an internal combustion engine in these figures) is mainly composed of a fairing housing 50, a fan 60, an expander ring (expander), a compressor ring (compressor), a multi-functional plenum 80, gears, etc., connected by shafts front and back, and operating in synchronization. In some embodiments, the compressor ring with the compressed air function can be replaced by other types of compressors. The expander ring and the compressor ring have similar structures, and their basic components are main and auxiliary ring structures, including a main male rotor 10 and an auxiliary female rotor 20, and a main stator 30 and an auxiliary stator 34, wherein the main stator 30 and the auxiliary stator 34, as fixed housings, respectively accommodate the main male rotor 10 and the auxiliary female rotor 20 that can rotate around the shaft. Referring to FIGS. 1, 3-4, and 12, the rotary mechanism 100 further includes a main shaft 82 and an auxiliary shaft 83, which are connected to the main male rotor 10 and the main stator 30 through a bearing, and the auxiliary shaft 83 is connected to the auxiliary female rotor 20 and the auxiliary stator 34 through a bearing. The main shaft 82 and the auxiliary shaft 83 are respectively supported in the bearings. The rotary mechanism 100 further includes a main gear 71 connected to the main shaft 82 and an auxiliary gear 72 connected to the auxiliary shaft 83. The main male rotor 10 and the auxiliary female rotor 20 are operated in synchronization through the main / auxiliary gear transmission. Instead of the main gear 71 and the auxiliary gear 72, a belt or other means can be used to achieve the synchronization between the main male rotor 10 and the auxiliary female rotor 20. Thus, the auxiliary female rotor 20 and the main male rotor 10 are rotated in cooperation with each other.

[0067] Figures 15A-15C, 16A-16C, 17A-17C, and 18 show different embodiments of rotors according to the present disclosure. Both the main convex rotor and the secondary concave rotor contain a rotor disc. In some large embodiments, the rotor disc has a thickness greater than 120 mm. In some medium embodiments, the rotor disc has a thickness between 40 and 120 mm. In some small embodiments, the rotor disc has a thickness less than 40 mm. Figures 15B and 15C correspond to two configuration designs in Figure 16B, respectively. Figure 18 is a cross-sectional view of one configuration embodiment in Figure 17B. As can be seen, the main convex rotor 10 has a rotor disc 1 and pistons 2 configured as convex arms, which are connected to the edge of the rotor disc 1. Only one piston and one secondary ring are allowed, but this causes problems of unsymmetrical shaft, continuous impact on the shaft, and is not conducive to long-term operation. In the preferred embodiments of the present disclosure, at least two pistons 2 are provided, which are evenly and symmetrically distributed on the peripheral edge of the rotor disc 1, and the working thrust can achieve force balance; and two secondary rings are evenly and symmetrically distributed on both sides of the main convex rotor. It should be noted 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, etc. 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 the rotating mechanism 100 as an internal combustion engine can easily improve the power-to-weight ratio, i.e., the ratio of power to weight. However, a larger number of pistons will reduce the compression and expansion stroke, which needs to be considered in balance. Inside the main stator 30 as a fixed shell, a cavity as a cylinder 40 is formed in the rotation path of the piston 2 to wrap the piston 2. The cylinder 40 can be used to contain the working fluid and the rotating piston.

[0068] When the auxiliary concave rotors 20 rotate in cooperation with the main convex rotors 10, their rotation directions are opposite, and they do not contact each other but are spaced apart with a small gap to avoid collision, scratching, and even jamming. The number of auxiliary concave rotors 20 is not limited to two as shown in FIGS. 1-7 and FIGS. 15 and 18, and can be three (as shown in FIG. 25A), four (as shown in FIG. 25B), or the like according to the number of pistons 2, and is generally, for example, matched with the number of pistons 2. In the embodiments of the present disclosure, the plurality of auxiliary concave rotors 20 are uniformly and symmetrically distributed around the main convex rotors 10. The auxiliary concave rotors 20 have auxiliary rotor discs 25 and an incomplete closed annular extension 28 surrounding the auxiliary rotor discs 25, and the annular extension 28 has the same cross-sectional shape as the piston cross-section, and functions as an on-off switch for the cylinder and the piston. The annular extension 28 has a concave recess 3 that cooperates with the piston 2, and when the main convex rotors 10 and the auxiliary concave rotors 20 rotate together to a certain angle, the piston 2 can just pass through the concave recess 3 with a small gap, and the remaining operation angle is cut off by the annular extension 28 to block the cylinder, and the cylinder volume is changed by the rotation of the piston. Referring to FIGS. 1, 3-4, 12, 25A, 25B, in 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. For example, a transmission ratio of 1:1, 1:2, 1:3, 1:4, etc. means that for every one revolution of the main gear 71, the auxiliary gear 72 rotates n revolutions, for example, 1 revolution, 2 revolutions, 3 revolutions, 4 revolutions, etc., thereby achieving the rotation cooperation of the auxiliary concave rotors and the concave recesses with the pistons. The number of concave recesses 3 of each auxiliary concave rotor 20 is determined according to the transmission ratio and the number of pistons. For example, in a 1:1:1 auxiliary:main:auxiliary three-ring two-piston structure, each auxiliary concave rotor has two axisymmetric concave recesses, so that one revolution, two axisymmetric pistons pass through two concave recesses respectively. For example, in a 2:1:2 auxiliary:main:auxiliary three-ring two-piston structure, each auxiliary concave rotor has only one concave recess, so that one revolution, two axisymmetric pistons pass through the same concave recess. According to a preferred embodiment, referring to FIG. 26, two main convex rotors 10 and three auxiliary concave rotors 20 cooperating therewith are arranged side by side, one of the auxiliary concave rotors 20 is arranged between the two main convex rotors 10, and the concave recess 3 of this auxiliary concave rotor 20 is shared by the pistons 2 on the two main convex rotors 10 in turn, thereby saving one auxiliary concave rotor and improving the power-to-weight ratio. The method of saving the number of auxiliary concave rotors and improving the power-to-weight ratio by multiplexing auxiliary concave rotors through two or more main convex rotors is not limited to the example of FIG. 26, for example, three main convex rotors can multiplex two auxiliary concave rotors.

[0069] As can be seen from FIGS. 1 to 3, in the exemplary embodiments of the present disclosure, the expansion ring and the compression ring are spaced in parallel and are communicated by conduits or passages and a multifunctional air chamber 80, etc. at appropriate positions. The main convex rotor 10 close to the main gear 71 and the auxiliary concave rotor 20 close to the auxiliary gear 72 are in the same layer, i.e. in the compression ring at the rear end, forming the first layer of main convex rotors 10' and the first layer of auxiliary concave rotors 20'. Correspondingly, the main convex rotor 10 far away from the main gear 71 and the auxiliary concave rotor 20 far away from the auxiliary gear 72 are in the same layer, i.e. in the expansion ring at the front end, forming the second layer of main convex rotors 10" and the second layer of auxiliary concave rotors 20".

[0070] The working principle of the rotary mechanism 100 as an internal combustion engine according to the present disclosure is described below. Referring to FIGS. 3, 12, and 27A-27D, as the main convex rotor 10 and the auxiliary concave rotor 20 rotate in coordination, the cylinder 40 is partitioned by the piston 2 and the auxiliary concave rotor 20 into the intake chamber 41, the compression chamber 42, and the expansion chamber 43 and the exhaust chamber 44, all of which have variable volumes. In some embodiments, instead of the auxiliary concave rotor, a card can be provided to partition the cylinder 40, which is then partitioned into chambers with variable volumes. Both the auxiliary concave rotor and the card are cylinder partitioning mechanisms that cooperate with the piston to form a cylinder with a variable volume. The intake chamber 41 and the compression chamber 42 are formed in the cylinder 40' defined by the first layer (compression ring) of the main convex rotor 10' and the main stator 30', and the expansion chamber 43 and the exhaust chamber 44 are formed in the cylinder 40" defined by the second layer (expansion ring) of the main convex rotor 10" and the main stator 30". In the intake phase, referring to FIG. 27A, in the first layer, air in the channel enters the intake chamber 41 through, for example, two first intake ports 18' of the cylinder 40'. A valve 38 can be provided at the first intake port 18' to regulate the amount of intake air. With the valve 38, the amount of intake air can be adjusted as needed to flexibly control the power of the rotary mechanism. As the piston 2' rotates, the intake chamber 41 gradually increases in size, creating a negative pressure to draw in more air. At the same time, the compression chamber 42 on the other side of the piston 2' gradually decreases in size, and the first one-way valve 22' (or the second one-way valve 22") connected to the first exhaust port 19' of the compression chamber 42 can remain closed at this time, so that the air in the compression chamber 42 (or the multifunctional chamber 80) is compressed, as shown in FIG. 27B. In an alternative embodiment of the present disclosure, the compression ring can be omitted, and an electric compressor can be used alone to achieve intake and compression. When the air in the compression chamber 42 is compressed to a certain extent, for example, when the air pressure exceeds the threshold of the one-way valve, the first one-way valve 22' opens, and the compressed air is transferred from the compression chamber 42 of the first layer (compression ring) to the multifunctional chamber 80 through a conduit or passage and the first one-way valve 22'. The multifunctional chamber 80 has multiple functions such as storing air and / or mixing air and / or combustion. In an embodiment A of the present disclosure, the multifunctional chamber only serves to store air. 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) passes through the recess of the auxiliary concave rotor and the second intake port 18" just before and after. At this time, the second one-way valve 22" is opened to transfer the compressed air from the multifunctional chamber 80 to the expansion chamber 43 of the second layer expansion ring cylinder 40", as shown in FIG. 27C. At this time, in the expansion ring, an appropriate amount of fuel is injected into the expansion chamber 43, for example, using a (high-pressure in-cylinder direct injection) fuel nozzle 21 to form a mixture of compressed air and fuel with the appropriate air-fuel ratio in the expansion chamber 43, and the mixture is ignited by a spark plug 23 of the expansion chamber.In a preferred embodiment B of the present disclosure, instead of igniting the mixture by spark plug 23, direct compression ignition is achieved (all the way or after the spark plug engine) by controlling the temperature, pressure, air-fuel ratio, compression ratio, etc. of the expansion chamber to meet the compression ignition conditions. 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 in the cylinder 40 to do work, so that the expansion chamber 43 increases rapidly, at the same time, the exhaust chamber 44 separated by the second layer (expansion ring) piston 2" decreases, and the gas therein is discharged through the second gas outlet 19", as shown in FIG. 27D. In an embodiment of the present disclosure, the exhaust gas after combustion is discharged to the outside or further processed, for example, through the exhaust pipe 73 connected to the gas outlet of the exhaust chamber 44, for example, through a three-way catalyst and / or a particle trap to treat the exhaust gas and reduce harmful gas emissions. In an embodiment of the present disclosure, the exhaust pipe 73 extends to the outside of the rotating mechanism to discharge the exhaust gas. In a preferred embodiment of the present disclosure, the exhaust pipe 73 extends to the tail region of the air duct, and the discharged exhaust gas mixes with the air in the tail region of the air duct and expands, and is discharged through the tail jet outlet (for example, near the end of the main shaft 82 opposite to the fan 60 in FIG. 1) on the rotating mechanism located on the fairing housing 50, thereby generating thrust to power the device (such as a flying car, a drone, etc. low-altitude aircraft) installed with the rotating mechanism 100, further making full use of the energy in the hot exhaust gas, and improving energy utilization efficiency. Thus, a complete cycle consisting of four strokes of intake, compression, expansion and exhaust is completed. With the continuous rotation of the piston, the next cycle begins, and so on.

[0071] In one embodiment of the present disclosure, various sensors such as Hall sensors, position sensors, oxygen sensors, temperature sensors, concentration sensors, pressure sensors, etc. and pressure relief valves, pressure regulating valves, etc. can be illustratively provided at, for example, the first intake port 18', the second intake port 18", the first exhaust port 19', the second exhaust port 19", the multi-functional gas 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 gear 71 / 72, etc. so as to control the intake flow rate, the exhaust flow rate, the compression ratio, the air-fuel ratio, and the gas pressure, temperature, fuel injection amount, rotational speed, etc. Referring to FIGS. 1, 2, and 11-12, in one preferred embodiment of the present disclosure, the multi-functional gas chamber 80 of the rotating mechanism 100 is in communication with 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 additionally or alternatively (or optionally) be provided on the multi-functional gas chamber 80. Referring to FIG. 11, the first one-way valve 22' and the 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 return mechanism 70, which has different working temperatures and pressures, functions, appearances, and models at different positions, and can be the same or different, and is controlled by electricity (magnetism) and / or mechanically. The first one-way valve 22' between the compression chamber 42 and the multi-functional gas chamber 80 is used to control the intake amount and pressure of the compressed air from the compression chamber 42 into the multi-functional gas chamber 80, and excess air and pressure can be discharged to the air duct as needed. The second one-way valve 22" between the multi-functional gas chamber 80 and the expansion chamber 43 is controlled to open or close the passage from the multi-functional gas 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 return mechanism and the multi-functional gas chamber 80 controls the amount of exhaust gas discharged from the exhaust chamber 44 to the multi-functional gas chamber 80. In the present disclosure, the fuel can include, for example, but is not limited to, hydrogen, gasoline, diesel, heavy oil, methanol, ethanol, ammonia, natural gas, biofuel, etc. In one preferred embodiment of the present disclosure, water vapor can also be injected into the expansion chamber to cool and expand the work.

[0072] In one embodiment of the present disclosure, to save fuel, the fuel injection and ignition can be stopped when the internal combustion engine is at low power demand, which is called misfire. There are two modes of misfire operation, one is to stop the compression of intake air and stop the injection of fuel, and the other is to stop the injection of fuel only without stopping the compression of intake air. A) In the former, the first one-way valve 22' is opened, and the transferred un-compressed air directly enters the expansion chamber 43 through the multi-functional air chamber 80 to form a straight pass; B) In the latter, the internal combustion engine operates as normal but does not inject fuel, and the compression ring continues to compress the air stored in the multi-functional air chamber, and opens the second one-way valve 22" to send the compressed air (or contains the exhaust gas after combustion) into the expansion chamber to expand and do work when the ignition timing comes. Both modes make use of the inertial flywheel energy storage effect to continue to maintain the rotation work. Both modes of misfire operation can cool the cylinder. In one embodiment of the present disclosure, the internal combustion engine and / or the expansion ring and / or the cylinder temperature can be controlled by misfire, and the internal combustion engine can be intermittently operated as needed. When it is detected that the temperature of the expansion ring and / or the cylinder is higher than a threshold value, the internal combustion engine actively enters the misfire mode or the intermittent operation mode to reduce the temperature of the cylinder. Since the main / auxiliary rotor has the inertial flywheel energy storage effect, the fuel saving effect of the misfire operation mode of the internal combustion engine of the present disclosure is much better than that of the traditional reciprocating piston engine and eccentric shaft rotor engine. In one embodiment of the present disclosure, through intermittent operation by misfire, two axisymmetric pistons can achieve 0, 2 or 4 ignitions (combustions) per rotation. Three evenly distributed pistons can achieve 0, 3, 6 or 9 ignitions (combustions) per rotation. Four evenly distributed pistons can achieve 0, 2, 4, 6, 8, 10, 12, 14 or 16 ignitions (combustions) per rotation. Thus, the power can be flexibly output as needed, which can be full power output, or very fuel-efficient during cruising or idling.

[0073] In one preferred embodiment of the present disclosure, the rotating mechanism 100 further comprises a one-way exhaust gas return mechanism 70 connected between the multi-functional air chamber 80 and the exhaust chamber 44, which is configured as a one-way pipeline, for example, to mix part of the exhaust gas discharged from the exhaust chamber 44 with the compressed air through the multi-functional air chamber 80 during the operation of the internal combustion engine, 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 in the high-temperature oxygen-rich combustion process; and make the components that may not be fully combusted in the exhaust gas (such as CO, HC, etc.) continue to burn or oxidize, thereby reducing the harmful substance emissions in the exhaust gas. This working process is EGR exhaust gas recirculation during the operation of the internal combustion engine. In one embodiment of the present disclosure, there can be one or more gas storage chambers or gas tanks or gas / mixing multi-functional air chambers (preferably with a three-way catalyst purification function) that store exhaust gas after purification by the three-way catalyst, mix the exhaust gas with the compressed air in the mixing chamber or the expansion chamber after the exhaust gas is mixed with the compressed air during the misfire operation of the internal combustion engine, and make the cylinder cool down.

[0074] Another embodiment C of the present disclosure, the multi-functional plenum 80 serves as a gas storage and mixing chamber. When the ignition combustion timing arrives, the right amount of fuel is injected into the multi-functional plenum 80 by the additional fuel injection mechanism 16 and mixed with the stored compressed air at the right air-fuel ratio (the temperature and pressure at this time ensure that the mixture will not be compression ignited), the second one-way valve 22" is opened by electric (magnetic) control, so that the mixture is transferred to the expansion chamber 43, ignited and combusted by the spark plug 23 in the expansion chamber, and expanded to do work.

[0075] Another preferred embodiment D of the present disclosure, the multi-functional plenum 80 serves as a gas storage, mixing and combustion chamber. When the multi-functional plenum 80 is ready with compressed air at the right temperature, pressure and compression ratio for compression ignition, the right amount of fuel is injected by the additional fuel injection mechanism 16 directly for compression ignition when the ignition combustion timing arrives. The second one-way valve 22" is opened by electric (magnetic) control or by the heat energy released by the combustion in the multi-functional plenum 80 to generate pressure, so that the combustion gas is transferred to the second layer (expansion ring) of the expansion chamber 43 to continue combustion and expansion to do work. The one-way closure of the first one-way valve 22' makes the high-pressure gas of combustion only pass to the expansion chamber 43 and not to the compression chamber 42.

[0076] Another embodiment E of the present disclosure, the right amount of fuel is injected into the multi-functional plenum 80 by the additional fuel injection mechanism 16 and mixed with the stored compressed air at the right air-fuel ratio (the temperature and pressure at this time ensure that the mixture will not be compression ignited), the mixture is ignited by the additional spark plug 85 when the ignition combustion timing arrives. The second one-way valve 22" is opened by electric (magnetic) control or by the heat energy released by the combustion in the multi-functional plenum 80 to generate pressure, so that the combustion gas is transferred to the second layer (expansion ring) of the expansion chamber 43 to continue combustion and expansion to do work.

[0077] A preferred embodiment F of the present disclosure, supports partitioned mixed combustion of two fuels. A small amount of the first fuel is injected into the multi-functional plenum 80 by the additional fuel injection mechanism 16 and mixed with the stored compressed air for compression ignition, and after being transferred to the expansion chamber through the second one-way valve 22", the right amount of the second fuel is injected by the fuel nozzle 21 in the expansion chamber for compression ignition. Alternatively, the mixture in the multi-functional plenum 80 is not compression ignited, after being transferred to the expansion chamber by opening the second one-way valve 22", the right amount of the second fuel is injected by the fuel nozzle 21 in the expansion chamber, mixed again with the mixture of the first fuel and air, and ignited or compression ignited. Preferably, one of the two fuels can be methanol or methanol-containing fuel, which helps to clean or avoid the generation of carbon deposits during combustion.

[0078] Because the compression chamber of the compression ring and the expansion chamber of the expansion ring are independent of each other and run independently, the timing logic is simple, and the early ignition, deflagration, and knock problems that are difficult to suppress / solve for traditional reciprocating piston engines and eccentric shaft rotor engines (compression ignition) are not problems for the internal combustion engine of the present disclosure. The engine of the present disclosure is different from traditional engines and has similar torque characteristics of an electric motor, i.e., it can have maximum torque when starting at low speed. The internal combustion engine of the present disclosure can achieve any compression ratio within a certain range through the one-way valve control of the variable intake valve and the multi-functional chamber, and can precisely control the working temperature of the expansion chamber through the jump ignition working mode, so it is easy to meet the temperature, pressure, compression ratio, air-fuel ratio, and other compression ignition requirements. Therefore, the (low-temperature) HCCI homogeneous 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 of the present disclosure. Because the intake compression chamber of the compression ring and the expansion exhaust chamber of the expansion ring are independent of each other and run synchronously, the intake is compressed at the same time, and the expansion is exhausted at the same time, so the internal combustion engine of the present disclosure is also called a "split synchronous four-in-one stroke ring rotating engine" or simply a "split synchronous ring rotating engine".

[0079] In an embodiment of the present disclosure, the main convex rotor 10 and the main stator 30 in the first layer (compression ring) formed with the intake chamber 41 and the compression chamber 42 can be made of lightweight high-strength materials such as aluminum alloy, magnesium aluminum alloy, or engineering ceramics or special engineering plastics, etc. to reduce weight and further improve the power-to-weight ratio. In an embodiment of the present disclosure, the main and auxiliary rotors of the expansion ring and the compression ring are the same size and are coaxially connected front and back. In a preferred embodiment of the present disclosure, the expansion ring and the compression ring can be different sizes, for example, the compression ring is larger than the expansion ring, or vice versa, the main convex rotor is coaxially connected front and back, and the auxiliary rotor is coaxially or non-coaxially connected through gears or belts to achieve any adjustment of the compression ratio within a certain range. In an embodiment of the present disclosure, the main convex rotor 10 and the auxiliary concave rotor 20 are hollowed out locally to achieve static and dynamic balance. For example, the annular extension part 28 of the auxiliary concave rotor 20 is a hollow annular extension part 28, so that the auxiliary concave rotor 20 achieves static / dynamic balance.

[0080] As can be seen from FIGS. 1-3, in one exemplary embodiment of the present disclosure, the rotating mechanism 100 further comprises a fairing housing 50, fans 60. The fairing housing has the function of adjusting airflow. The fans 60 are mounted on the main shaft 82 within the fairing housing 50. Additionally, the fans 60 can also be provided on the auxiliary shaft 83, see FIGS. 1, 3-4, three fans 60 in FIG. 12, the number of fans can not be limited to this, the main shaft and / or auxiliary shaft can be mounted with any number of fans, for example, the number is 1, only the main shaft, the number is 2, both on the main shaft or on two auxiliary shafts respectively, the number is 3, on one main shaft and two auxiliary shafts respectively, the number is 4, two on the main shaft and two on the auxiliary shaft, etc. The fairing housing 50 contains the fans, the expansion ring, the compression ring, and the air duct for guiding the airflow is formed inside the fairing housing 50. There is a ​​airflow to the back of the expansion ring, which is not directly blown by the fan, so that the expansion ring can be cooled from both the front and the back. Optionally, the fairing housing 50 can also additionally house the main gear 71 and the 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 connected in sequence by the main shaft 82 and / or the auxiliary shaft 83, or the fan 60, the compression ring, the expansion ring, and the gear set including the main gear 71 and the auxiliary gear 72 are connected in sequence by the main shaft 82 and / or the auxiliary shaft 83, and work cooperatively. Thus, through the air duct formed in the fairing housing 50, the fan 60 continuously blows external air into the fairing housing 50 to cool the hot expansion ring, and the cold air absorbs and carries away the heat emitted by the hot expansion ring, becoming hot air that enters the intake chamber 41 of the compression ring to participate in the next work cycle, thereby recycling the heat energy lost from the cooling of the hot expansion ring in a closed loop, improving thermal efficiency. The heated air helps to increase the temperature of the compressed air, making it easier to achieve compression ignition for fuels with higher ignition points, thereby improving combustion efficiency and thermal efficiency. In an embodiment of the rotary mechanism 100 according to the present disclosure, the exhaust gas discharged from the exhaust pipe 73 of the expansion ring at the tail region of the air duct mixes with the air at the tail of the air duct and expands, and is discharged through the tail jet outlet (for example, near the end of the main shaft 82 opposite the fan 60 in FIG. 1) on the fairing housing 50 of the rotary mechanism 100, thereby generating thrust to power the device (such as a flying car, a drone, or other low-altitude aircraft) equipped with the rotary mechanism 100, further making full use of the energy in the hot exhaust gas, and improving energy utilization efficiency. The number, size, and rotation speed of the fan 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 each be divided into two symmetrical halves, for example, so that the fan 60 and other components, the main convex rotor 10, and the auxiliary concave rotor 20 are respectively accommodated therein when assembled, and then the halves are brought together for assembly, as shown in FIG. 3. In some embodiments, the half main stator 30 and the half auxiliary stator 34 are integrally constructed by, for example, laser welding or casting. Alternatively, the housing 50, the main stator 30 / main convex rotor 10, and the auxiliary stator 34 / auxiliary concave rotor 20 can also be integrally constructed by 3D printing, additive manufacturing, or the like.

[0081] In one exemplary embodiment of the present disclosure, referring to FIG. 13, the rotating mechanism 100 further comprises an electromagnetic device 90, which comprises a fixed inductive coil mechanism near the main gear 71 and a first magnet 95 arranged on the main gear 71. Referring to FIGS. 1-3, 12 and 13, the inductive coil mechanism may, for example, also comprise an inductive coil 96 and a carrier 97 for carrying the inductive coil 96. In a preferred embodiment, the inductive coil 96 is helically drawn on the carrier 97 which is a PCB (printed circuit board). The carrier 97 with the coil 96 is arranged 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 carrier 97, so that the first magnet 95 on the main gear 71 rotates relative to the fixed coil 96, thereby the inductive coil 96 generates electricity, forming a kind of generator. And by controlling the current size, direction and frequency of the inductive coil 96, the electromagnetic device can also be used as a starter and motor to drive the gear and main shaft to rotate, start the internal combustion engine and / or output power. In this way, the motor and generator functions can be realized, so that the internal combustion engine of the present disclosure can become a hybrid power device or a range extender. In another exemplary embodiment of the present disclosure, a piston position holding mechanism 98 is used instead of the electromagnetic device 90, which is arranged on the bottom surface of the housing 50, as shown in FIG. 14, and has a casing 94 and a second magnet 91 and a spring 93 contained in the casing 94, and a pressure relief member 92 is arranged on the casing 94, which may, for example, be configured as a pressure relief hole or a pressure relief valve, etc. The polarity of the second magnet 91 repels or attracts the polarity of the first magnet 95 to achieve the function of keeping the piston at a certain position when it stops rotating. During the operation of the internal combustion engine, the high-pressure air in the fairing housing 50 enters the casing 94 through the pressure relief member 92, and pushes the second magnet 91 to move in the casing 94 against the elastic force of the spring 93, thereby compressing the spring 93. Thus, the position of the second magnet 91 deviates, i.e. does not align with the first magnet 95, so as not to affect the normal operation of the rotating mechanism 100. When the rotating mechanism stops working, the fan 60 no longer blows air into the fairing housing 50, and the high-pressure air in the duct no longer exists. As there is no pressure from the high-pressure gas, the spring 93 resets to push the second magnet 91 back to the original position. At this time, the second magnet 91 on the fixed housing 50 attracts the first magnet 95 on the main gear 71 to the position of alignment, thereby driving the main gear 71 to rotate to a certain position, and further making the main lobe rotor 10 and its piston 2 fixedly connected coaxially with the main gear 71 stop at a predetermined position, such as a position where the spark plug 23 can ignite the fuel. In this position, fuel can be directly injected into the expansion chamber 43 without the starter to ignite the mixture of air and fuel in the expansion chamber 43 by the spark plug 23, thereby realizing the self-starting of the rotating mechanism (without starter).The above are only exemplary embodiments of the piston position maintaining device, and the present disclosure is not limited thereto.

[0082] In the operation of the rotating mechanism, the expansion ring relies on the gas combustion expansion to push the piston 2 to do work. In an embodiment of the present disclosure, the face of the piston 2” of the expansion ring that is pushed by the gas in the expansion chamber, i.e. the back face with reference to the rotation direction, is designed as a flat surface (see FIGS. 24A and 24E), and can also be preferably designed as a concave surface (see FIGS. 24B-24D), which makes the force on the piston 2” of the expansion ring more concentrated (a convex surface will make the force on the piston dispersed), wherein the arrow E represents the rotation direction of the piston 2. The other face of the piston 2” opposite to the force receiving face (the face in the exhaust chamber) can be a flat surface (see FIGS. 24A and 24B), a convex surface (see FIGS. 24D and 24E), or a concave surface (see FIG. 24C) with reference to the rotation direction. In particular, when the front face (the face in the exhaust chamber) of the rotating piston 2” of the expansion ring is convex, the gas is forced to be extruded to 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 to the exhaust chamber. In an embodiment of the present disclosure, the back face (the face in the intake chamber) of the piston 2’ of the compression ring is flat, and can also be preferably designed as a concave surface (see FIGS. 24B-24C), which makes the suction space larger and the negative pressure greater. The front face (the face in the compression chamber) of the piston 2’ of the compression ring is flat (see FIGS. 24A and 24B) or concave (see FIG. 24C), and in particular, when it is concave, it can reduce the gap in which the compressed air is extruded to the periphery of the piston 2’, so as to reduce the leakage of the compressed air, which is beneficial 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 circular (see FIG. 16B), elliptical (see FIG. 16A), rounded rectangular (see FIG. 16C), etc., but the present disclosure is not limited thereto. For example, the compression ring only has two strokes of intake and compression without combustion, and no thermal stress deformation occurs, so the shape of the piston 2' of the compression ring is not necessarily limited to a circle or an ellipse, and can be 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 ring expansion chamber needs to be combusted to expand and push the piston 2" to do work, and relative to a rectangular cylinder, the combustion can be insufficient, and a circular or elliptical ring-shaped cylinder 40 can make the combustion more complete and the combustion efficiency higher, and the piston 2" is preferably circular or elliptical, thereby also making the thermal stress distribution of the piston 2" more uniform and avoiding thermal deformation of the piston 2". Conversely, if the cross section of the piston 2" of the expansion ring is, for example, rectangular, the thermal stress on the corners can cause the piston 2" to deform, thereby increasing the gap between the main stator 30 and the piston 2", causing leakage of gas, reducing the thrust and power, and even possibly causing the piston 2" to be damaged and stuck (stuck cylinder) with the stator 30, causing the rotating mechanism to fail or be scrapped. Therefore, the design of the circular or elliptical piston of the present disclosure not only solves the problem of insufficient combustion of the traditional eccentric shaft rotor engine, but also solves the problem of thermal stress deformation of some rectangular piston rotor engines.

[0084] In order to reduce gas leakage, it is desirable for the gap between the main stator 30 and its contents, i.e., the main convex rotor 10, and the gap between the auxiliary stator 34 and its contents, i.e., the auxiliary concave rotor 20, to be as small as possible. However, in practice, considering the limitations of manufacturing and assembly processes and ensuring the relative rotation of the stator and the rotor, avoiding scratching and even sticking, the gap cannot be infinitely small, and poor design and sealing often result in gas leakage. Gas leakage can cause the compression ratio of the compression ring to decrease, the thrust of the expansion ring piston to decrease, the combustion efficiency to decrease, the output torque and power of the rotating mechanism to decrease, the fuel consumption to increase, the economy to be affected, and the combustion gas to be directly leaked into the atmosphere, even causing air pollution. Traditional eccentric shaft or other rectangular piston rotor engines, especially those without rotating discs, have long had the problem of poor sealing.

[0085] According to one embodiment of the present disclosure, the rotor 1, the piston 2, the main stator 30, the auxiliary stator 34, etc. are specially designed, the direction of the working fluid leakage is changed multiple times and greatly, the path of the working fluid leakage is greatly extended, so that more seals and different types of seals can be deployed on the leakage path to prevent the working fluid from leaking, and the problem of insufficient sealing space of the traditional eccentric shaft or other rotary engine is solved. Referring to FIGS. 1, 2, 6-8, 10, 15, 17, 18, 19A-19D, 20-22, the rotor 1 has a concave and / or convex first flow blocking part 4 arranged on the end face thereof, and the main stator 30 has a convex and / or concave first corresponding flow blocking part 5 arranged on the inner surface thereof, which is in non-contacting, i.e. gap, cooperation with the first flow blocking part 4. The first flow blocking part 4 may, for example, be a concentric circular ring with a generally rectangular cross section, which is usually much larger in size than a single comb tooth of the labyrinth seal, and cooperates with the first corresponding flow blocking part 5 to block the leaked gas, such as escaping through the main shaft 82, like a "block dam", by arranging multiple flow blocking parts, the direction of the working fluid leakage can be changed multiple times and greatly, and the travel path of the fluid leakage is greatly extended. However, the flow blocking part may, for example, also be in various shapes such as semicircular arc, triangle, trapezoid, etc. The number of flow blocking parts can be one or more, preferably two or more, such as 2, 3, 4, 5, 6, etc. In some embodiments, when multiple flow blocking parts are arranged, they can be the same or different in size, shape, spacing, etc., relative to or away from each other, forming an X shape, The purpose and function of the flow blocking part are completely different from those of the labyrinth seal. The size of the flow blocking part is usually much larger than that of a single comb tooth of the labyrinth seal, which is to greatly change the direction of the working fluid leakage and greatly extend the leakage travel path, to solve the problem of insufficient sealing space of the traditional rotary mechanism; the labyrinth seal is to reduce the pressure of the working fluid leakage by throttling the comb tooth gap and expanding the cavity, to generate pressure drop and vortex, to convert kinetic energy into heat energy, to achieve the purpose and effect of reducing the pressure of the working fluid leakage, and does not have the purpose and effect of greatly changing the leakage direction and greatly extending the leakage path. In some embodiments, the flow blocking part extends the leakage path travel by, for example, 50% or 100% or 200% or more, which is not possible for the labyrinth seal. The flow blocking part can support various 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] Referring to Figs. 18, 19A-19D, 20-21, in one embodiment of the present disclosure, the first blocking portion 4 is flatly configured or provided with first recesses and / or protrusions 6 on its peripheral surface, and the first corresponding blocking portion 5 is flatly configured or provided with first corresponding protrusions and / or recesses 7 which are non-contacting, i.e. gap-matched, with the first recesses and / or protrusions 6 on its peripheral surface. Alternatively, it can also be designed reversely, that is, the first corresponding blocking portion 5 is provided with first recesses and / or protrusions 6 on its peripheral surface, and the first blocking portion 4 is flatly configured or provided with first corresponding protrusions and / or recesses 7 which are non-contacting, i.e. gap-matched, with the first recesses and / or protrusions 6 on its peripheral surface. In a preferred embodiment, the first blocking portion 4 and the first corresponding blocking portion 5 respectively form a labyrinth seal on their corresponding top or bottom sections, and respectively form a spiral seal on their corresponding one side sections. The first blocking portion 4 and the first corresponding blocking portion 5 respectively form a spiral seal or a labyrinth seal on their corresponding other side sections. The first recesses and / or protrusions 6 are generally a plurality of, which can be rectangular, semicircular, triangular, trapezoidal, etc. in shape, and can be identical or different in size, shape, spacing, etc. In this way, the sealing performance is further improved.

[0087] In one embodiment of the present disclosure, referring to Figs. 19A-19D, 20-21, the end surface of the rotor 1 is partially flatly configured or provided with second recesses and / or protrusions 8, and the inner surface of the main stator 30 is partially flatly configured or provided with corresponding second protrusions and / or recesses 9 which are non-contacting, i.e. gap-matched, with the second recesses and / or protrusions 8. Similarly, the second recesses and / or protrusions 8 can be one or more, which can be rectangular, semicircular, triangular, trapezoidal, etc. in shape, and can be identical or different in size, shape, spacing, etc. In a preferred embodiment of the present disclosure, the stator wrapped around the rotor is provided with a groove seal and / or a honeycomb seal and / or a brush seal and / or a foil seal. In this way, the sealing performance is further improved.

[0088] In a preferred embodiment of the present disclosure, referring to Figs. 19A-19D, 20-21, the first recesses and / or protrusions 6 and the first corresponding protrusions and / or recesses 7 and the second recesses and / or protrusions 8 and the corresponding second protrusions and / or recesses 9 can form, for example, a spiral seal and / or a labyrinth seal and / or a gap seal, and / or a hole-slot seal structure and / or a honeycomb seal structure can be provided on the stator surrounding the rotor 1. Preferably, on the corresponding one side section of the first flow blocking portion 4 and the first corresponding flow blocking portion 5, the first recesses and / or protrusions 6 form a spiral seal (as shown by "K" in Fig. 20) on a section or component parallel or close to parallel or not perpendicular to the main shaft 82, so that during the rotation of the rotor 1 along with the main shaft 82, the fluid can be driven in the opposite direction of the fluid leakage direction (as shown by the dotted arrow G in Figs. 20 and 21) by setting the spiral driving direction (as shown by the solid arrow H in Figs. 20 and 21), for example, sequentially through the four points D→C, B→A in Fig. 21. The first recesses and / or protrusions 6 have opposite spiral directions on both sides of the rotor 1. A spiral seal or a labyrinth seal can be optionally deployed on the corresponding other side section of the first flow blocking portion 4 and the first corresponding flow blocking portion 5. In some preferred embodiments, the spiral seal can have a composite spiral seal, i.e. a static spiral seal in the opposite direction is provided on the (opposite) stator of the dynamic spiral seal surrounding the rotor, which can further enhance the spiral driving effect. The labyrinth seal, through the comb tooth throttling gap and the expansion cavity structure, generates pressure drop and vortex, converts kinetic energy into heat energy, and gradually reduces the gas leakage pressure, further inhibits gas leakage, and improves the sealing performance. The labyrinth seal can preferably adopt a stepped or staggered comb seal or a curved path seal, etc. In a preferred embodiment of the present disclosure, hole-slot seals and / or honeycomb seals are deployed on the main stator and / or auxiliary stator, which also have the effect of generating pressure drop and vortex.

[0089] Similarly, in a preferred embodiment of the present disclosure, the auxiliary recess rotor 20 has a recessed and / or protruding second flow blocking portion 13 provided on its end face, and the auxiliary stator 34 has a protruding and / or recessed second corresponding flow blocking portion 14 provided on its inner surface in non-contacting or gap cooperation with the second flow blocking portion 13, as shown in Figs. 1, 6-8, 15A-15C. The second flow blocking portion 13 on the auxiliary recess rotor 20 can be identical in number, structure, and working mode to the first flow blocking portion 4 of the main protruding rotor 10, and their functions are also similar.

[0090] Referring to FIG. 15B-15C, 16B, 17A-17C, 18, in a preferred embodiment of the present disclosure, the rotary plate 1 has a third flow barrier 17 partially surrounding the piston 2 and the cylinder 40 at the bottom side and / or the side of the piston 2 and the cylinder 40. Here, the third flow barrier 17 is for example in the shape of a wine glass, and the shape of the main stator 30 is then adapted accordingly to the third flow barrier 17, so as to keep the gap between the main stator 30 and the rotary plate 1 very small. For comparison, FIG. 15A shows a rotary plate 1 without a third flow barrier 17. As can be seen, the third flow barrier 17 forms a first type of third flow barrier 17' in the shape of a wine glass when it is wrapped around the bottom side of the piston 2 and the cylinder (see FIG. 15B, 16B), and the degree of wrapping can be anywhere between FIG. 15A and FIG. 15B. The third flow barrier 17 will greatly change the direction of the working fluid leakage, greatly extend the leakage path, and prevent the working fluid from leaking directly towards the bottom side of the piston 2 (i.e. towards the central axis direction of the rotary plate 1). The third flow barrier 17 forms a second type of third flow barrier 17" in the shape of a high wine glass when it is wrapped around the side of the piston 2 and the cylinder 40 (see FIG. 15C, 16B), which will greatly change the direction of the working fluid leakage, greatly extend the leakage path, and prevent the working fluid from leaking directly towards the side of the piston 2 and the cylinder, so that the leaked fluid can only flow towards the top side of the main stator 30, thereby further improving the sealing performance. The third flow barrier 17 has a third recess and / or protrusion 12 on its peripheral surface, see FIG. 17A-17C. With the third recess and / or protrusion 12, the sealing performance can be further improved.

[0091] Referring to FIG. 23, in a preferred embodiment of the present disclosure, the piston 2 has a fourth recess 11 on its top side. As can be seen from FIG. 23, the fourth recess 11 on the top side of the piston 2 can be for example one or more pressure relief grooves with different depths, such as rectangular, semicircular, triangular, trapezoidal, etc. In this exemplary embodiment, for example, there are three recesses. Among the three recesses, the two small recesses on the left and right sides are for example 0.01-0.2mm deep, and the large recess in the middle is for example 1-2mm deep and 1-2mm wide. Here, the leaked gas is subjected to a sudden pressure drop, and a vortex is generated. In this way, the gas leakage between the two cylinders on both sides of the piston is prevented.

[0092] In a preferred embodiment of the present disclosure, the second flow barrier 13 and the second corresponding flow barrier 14 are flatly configured or have a fifth protrusion and / or recess and a fifth corresponding recess and / or protrusion on their peripheral surfaces (see FIG. 7, 8). Referring to the second recess and / or protrusion of the rotary plate 1 of the main convex rotor 10, similar sixth recess and / or protrusion structures can be provided on the rotary plate of the auxiliary concave rotor 20.

[0093] In a preferred embodiment of the present disclosure, referring to Figs. 3, 6, 9, 10, the auxiliary sub 34 has a circumferential flow collection groove 36 inside the circumferential edge of the annular outer extension 28, and has a plurality of flow guide grooves 35 communicating with the circumferential flow collection groove 36. The width and depth of the circumferential flow collection groove can be, for example, 1-3 mm, and the width and depth of the flow guide groove can be, for example, 0.2-1 mm. The cross sections of the flow guide grooves 35 can be the same or different, and can be trapezoidal, rectangular, semicircular, or the like. The guide direction of the flow guide grooves 35 is at least substantially consistent with the rotation direction of the auxiliary concave rotor 20 (as indicated by the arrow "X" in Fig. 9), so that the gas leaked from the cylinder 40 on the side of the auxiliary concave rotor 20 is guided along the flow guide grooves 35 to the circumferential flow collection groove 36 as the auxiliary concave rotor 20 rotates, thereby moving away from the leakage gap. The gas reaching the circumferential flow collection groove 36 is brought back into the cylinder 40 by the recessed portion 3 as the piston 2 passes through the recessed portion 3, thereby achieving the return of the gas leaked from the cylinder 40 to the auxiliary concave rotor region to the cylinder 40.

[0094] In a preferred embodiment of the present disclosure, the flow throwing groove 37 can also be provided on the main convex rotor 10 and / or the auxiliary concave rotor 20, referring to Figs. 7, 8, and 15A-15C. For the main convex rotor 10, the flow throwing groove 37 is exemplarily shown here with two turns, but the number of turns is not limited thereto, and more turns of flow throwing grooves 37 can also be provided. The flow throwing grooves 37 near the outer circle of the cylinder 40 can be shallow on the outside and deep on the inside, for example, 0.1-2 mm, for throwing the fluid leaked from the cylinder 40 back to the cylinder 40 under the action of centrifugal force. The flow throwing grooves 37 near the inner circle of the main shaft 82 can be shallow on the outside and deep on the inside, for example, 0.2-3 mm, for throwing the sealing liquid or grease away from the center shaft and blocking the gas from leaking at the center shaft under the action of centrifugal force. In this way, fluid leakage is further reduced.

[0095] In one exemplary embodiment of the present disclosure, referring to FIG. 1, FIG. 2, FIG. 20, FIG. 22, a helical portion 81 is provided on the main shaft 82, which drives the fluid in the opposite direction of the fluid leakage when the main shaft 82 rotates in operation, referring to the helical driving direction shown as "H" and the gas leakage direction shown as "G" in FIG. 20. Similarly, a helical portion can also be provided on the auxiliary shaft 83. The helical portion 81 has opposite helical directions on both sides of the rotating disc 1. In one preferred embodiment of the present disclosure, a sealing medium is provided in the gap between the main convex rotor 10 and the main stator 30 and / or the auxiliary concave rotor 20 and the auxiliary stator 34 in at least the part or the whole area between the two flow blocking portions. The sealing medium can include but is not limited to grease, lubricating liquid, cooling liquid, boron nitride, graphite, molybdenum disulfide and other sealing or lubricating media with very small friction coefficient, and liquid forming a magnetic fluid seal. When a magnetic fluid sealing medium is used, a magnetic substance needs to be provided on the stator at the location where the magnetic fluid is deployed so as to attract the magnetic fluid to gather and block the gas leakage. When the main shaft 82 and the auxiliary shaft 83 rotate, the helical portion 81 drives the liquid or grease in the opposite direction of the fluid leakage. In this way, the fluid, i.e. gas or liquid, that can leak during the operation of the rotating mechanism is prevented from leaking outwards through the main shaft 82 and / or the auxiliary shaft 83, thereby improving the sealing performance.

[0096] Referring to Fig. 22, in a preferred embodiment of the present disclosure, the rotating mechanism 100 further comprises a sealed liquid circulating device 15 which can be self-circulated by pressure difference, for making the sealed liquid between the end surface of the rotor 1 and the inner surface of the main stator 30 to be autonomously circulated back and forth, achieving sealing and / or cooling effect, see the direction of the sealed liquid being driven by the spiral seal and centrifugal force shown by the solid arrow "M" in Fig. 22, wherein the dashed arrow "G" represents the direction of gas leakage. Preferably, the device 15 is disposed between two or more flow blocking portions close to the shaft. The sealed liquid can flow in the gap between the main stator 30 and the main convex rotor 10 for sealing, cooling, lubrication, etc. The liquid can include but is not limited to machine oil, lubricating oil, cooling oil, multi-purpose oil, water, magnetic fluid or other liquid with low friction coefficient and low volatility, and composite liquid. The sealed liquid circulating device 15, for example, comprises 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 and the liquid collecting portion 27, and the sealed liquid stored in the liquid collecting portion 27 accounts for a volume ratio of, for example, 30% to 70%, and needs to be replenished when it is less than, for example, 30%. The introduction portion 26 is, for example, configured as a hole located at the liquid low-pressure area flow blocking portion above the main shaft 82. The liquid collecting portion 27 is opened at the gas high-pressure area flow blocking 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 sealed liquid automatically circulate back to the introduction portion 26 of the flow blocking portion above the main shaft 82 along the guide circuit 24 (as shown by the arrow "T" in Fig. 22), from which it enters the gap between the main stator 30 and the main convex rotor 10. Due to the driving of centrifugal force and spiral seal, the sealed liquid follows the rotation of the rotor for several turns from the flow blocking portion above the main shaft to the flow blocking portion opening below the main shaft 82, and is thrown back to the liquid collecting portion 27, and starts to circulate again. The guide circuit 24 can be designed as one or more liquid return pipes or channels, etc. The liquid collecting portion 27 opening is arranged at the intersection area of the sealed liquid and the leaked gas on the flow blocking portion where the pressure of the sealed liquid and the leaked gas is expected to be balanced. The sealed liquid circulating device 15 can be applied on the expansion ring or the compression ring.

[0097] In a preferred embodiment, a liquid recovery, storage and replenishment mechanism is provided for replenishing the seal liquid for the seal liquid circulating device 15 in the stop state of the rotating mechanism 100, as shown in FIG. 22, which includes a one-way driving mechanism such as a pump, a cylinder bottom valve mechanism, a seal liquid recovery and storage mechanism 31 and a replenishment pipe 32, which connects the seal liquid recovery and storage mechanism 31 and the liquid collection portion 27 in one direction. In the stop state, the gas pressure of the cylinder disappears, and the seal liquid that does not return to the liquid collection portion 27 due to various reasons such as equipment tilting reaches the bottom of the cylinder 40 of the rotating mechanism 100 under the action of gravity. Opening the valve at the bottom of the cylinder allows the seal liquid to fall into the liquid recovery and storage mechanism 31 to complete recovery, avoiding the liquid being consumed by combustion the next time the machine is started. When the rotating mechanism detects that the seal liquid storage amount of the liquid collection portion 27 is below a threshold value of, for example, 30%, the seal liquid is pumped from the liquid recovery and storage mechanism 31 to the liquid collection portion 27 along the replenishment pipe 32 using a one-way driving mechanism such as a pump (as shown by the arrow "R" in FIG. 22), thereby replenishing the seal liquid lost due to volatilization and the like, as shown in FIGS. 2 to 6, 10 and 22.

[0098] In a preferred embodiment of the present disclosure, when the rotating mechanism 100 according to the present disclosure is a compressor, only the compression ring, the cylinder 40 only has the intake chamber 41 and the compression chamber 42, and there is no expansion ring and its expansion chamber 43 and exhaust chamber 44. In the rotating mechanism 100 according to the present disclosure, the environment of the vacuum machine (vacuum pump) is basically opposite to that of the compressor, i.e. the intake end of the compressor is open to the environment, and the compressed air is stored or transferred to a closed environment, while the 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, only the expansion ring, the cylinder 40 only has the expansion chamber 43 and the exhaust chamber 44, and there is no compression ring and its 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, only the medium is changed 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 gear and the electromagnetic device cooperate to generate electricity as a generator and output power. Alternatively, the main shaft outputs power to a separate generator to generate electricity and output power. 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 outputs power, and the gear and the electromagnetic device cooperate to generate electricity as a generator or output power as a motor, thereby achieving hybrid power output. It can be seen that the rotating mechanism 100 according to the present disclosure has wide applications.

[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 thereof. Furthermore, 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, which is a rotary mechanism 100 according to the above disclosure of the present disclosure. In the method according to the present disclosure, as a sealing mechanism, a concave and / or convex first flow blocking portion 4 is provided on the end face of the rotor disc 1, a convex and / or concave first corresponding flow blocking portion 5 is provided on the inner surface of the main stator 30, which is in non-contact, i.e. gap cooperation, with the first flow blocking portion 4, wherein a first recess and / or protrusion 6 is provided on the peripheral surface of the first flow blocking portion 4, and the peripheral surface of the first corresponding flow blocking portion 5 is flatly configured or provided with a first corresponding protrusion and / or recess 7 which is in non-contact, i.e. gap cooperation, with the first recess and / or protrusion 6. By this method, the working fluid leakage direction can be greatly changed, and the fluid leakage path can be greatly extended. The above various designs of the rotary mechanism 100 and its sealing mechanism according to the present disclosure also correspondingly apply 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 design of the method according to the present disclosure, a spiral seal and / or a labyrinth seal and / or a gap seal is adopted on the rotor disc 1, and / or a hole groove seal structure and / or a honeycomb seal structure and / or a brush seal structure and / or a lamella seal structure and / or a magnetic fluid seal structure is provided on the stator wrapping the rotor disc to prevent gas leakage. These seals can be realized by using the various mutually cooperating flow blocking portions, recesses and / or protrusions described above.

[0101] In a preferred design of the method according to the present disclosure, on the inner surface of the auxiliary stator 34 accommodating the annular outer extension 28, the fluid leaked from the gas cylinder 40 is guided along the flow guide groove of the auxiliary stator 34 to the circumferential flow groove and brought back to the gas cylinder by the recessed portion when the fluid is rotated, thereby reducing the fluid leakage to the central shaft of the auxiliary stator 34.

[0102] In a preferred design of the method according to the present disclosure, a sealing medium is provided in the gap between the rotor disc 1 and the main stator 30 in the part or all of the area between the at least two flow blocking portions to block the leakage of the working fluid.

[0103] In a preferred design of the method according to the present disclosure, the sealing liquid is caused to return from the gas high pressure area flow blocking portion below the main shaft near the gas cylinder 40 to the liquid low pressure area flow blocking portion above the main shaft near the main shaft by means of a pressure difference.

[0104] In a preferred design of the method according to the present disclosure, the internal combustion engine can be intermittently operated on demand by misfire mode. The internal combustion engine stops injecting fuel and igniting combustion during misfire, but can still continue to operate due to the energy storage and release of the primary and secondary ring inertia flywheels, thus saving fuel, with the effect far superior to reciprocating piston and eccentric shaft rotor engines. In a preferred design of the method according to the present disclosure, the internal combustion engine and / or the expansion ring and / or the cylinder temperature can be precisely controlled by misfire mode. The temperature of the expansion ring and the cylinder 40 of the internal combustion engine will gradually decrease during misfire operation.

[0105] In a preferred design of the method according to the present disclosure, 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. In two working scenarios, A) the internal combustion engine ignites combustion and works normally, for example 10% ~ 30% of the exhaust gas returned from the exhaust gas return mechanism 70 mixes with air in the multifunctional air chamber, the purpose is to reduce NOx emission pollution. B) the internal combustion engine works by misfire, the exhaust gas stored or returned from the exhaust gas return mechanism 70 is returned to the multifunctional air chamber to mix with compressed air and transfer to the expansion chamber 43 to expand and do work, thus improving the work efficiency and saving fuel. In addition, the components that may not be fully combusted in the exhaust gas (such as CO, HC) continue to be combusted or oxidized in both A / B working scenarios, thus reducing harmful substance emissions in the exhaust gas. In another preferred design of the method according to the present disclosure, the exhaust gas discharged from the tail of the exhaust pipe 73 of the expansion ring mixes with air in the air duct tail and expands, and is discharged through the tail jet outlet (for example, near the end of the main shaft 82 opposite to the fan 60 in FIG. 1) on the fairing housing 50 of the rotating mechanism, thus generating thrust to power the device (such as a flying car, a drone, and other low-altitude aircraft) installed with the rotating mechanism 100, further making full use of the energy in the hot exhaust gas, and improving energy utilization efficiency.

[0106] In a preferred design of the method according to the present disclosure, the internal combustion engine can be operated according to an operation schedule. For example, after the internal combustion engine completes the ith (i > 1) combustion cycle according to the schedule, the ignition is scheduled to jump according to the working condition, and in the subsequent ith+j (j > 0) jump-ignition cycle, fuel injection is stopped but air compression continues, so that the exhaust gas stored in the gas storage chamber or gas storage tank (preferably with a three-way catalyst purification function) or gas storage / mixing multifunctional gas chamber partially returns to the expansion chamber 43 through the multifunctional gas chamber mixed compressed air to expand and work, and in the ith+j+p (p > 0) jump-ignition cycle, fuel injection is stopped but air compression continues, and in the ith+j+p+q (q > 0) jump-ignition cycle, fuel injection is stopped and air compression is stopped until the end of the current round of the schedule, the next round of the schedule is started, and the 1~i+j+p+q cycle is started; the following p+q cycles utilize the main and auxiliary ring inertia flywheel effect to release energy and work. The internal combustion engine can be continuously operated according to the i+j+p+q cycle mode, wherein i > 1, j > 0, p > 0, q > 0, and at least one of j, p, and q is not 0. Flexibly adjusting the values of i, j, p, and q can meet the power demand and fuel saving demand under various working conditions.

[0107] In a preferred design of the method according to the present disclosure, fuel injection and / or air-fuel mixture combustion is carried out in the multifunctional gas chamber 80 and / or the expansion chamber 43. Specifically, for example, no fuel can be injected in the multifunctional gas chamber 80, but fuel injection and air-fuel mixture combustion can be carried out in the expansion chamber 43. Alternatively, fuel can be injected in the multifunctional gas chamber 80, but the air-fuel mixture does not burn in the multifunctional gas chamber 80, but burns and expands in the expansion chamber 43. Alternatively, fuel is injected in the multifunctional gas chamber 80 and the air-fuel mixture burns, and the expansion chamber 43 expands.

[0108] In a preferred design of the method according to the present disclosure, the same or different fuels are combusted in the multifunctional gas chamber 80 and the expansion chamber 43 at different times (in different cycles). For example, the first fuel is combusted in the multifunctional gas chamber 80 in the mth (m > 1) cycle, and then the first fuel is combusted in the expansion chamber 43 in the m+nth (n > 1) cycle; the cycles are alternately rotated. Alternatively, the first fuel is combusted in the multifunctional gas chamber 80 in the mth (m > 1) cycle, and then the second fuel is combusted in the expansion chamber 43 in the m+nth (n > 1) cycle; the cycles are alternately rotated. Flexibly adjusting the values of m and n can meet the demand under 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 in the multi-functional plenum 80 and the mixture of compressed air and fuel is combusted, while an appropriate amount of the second fuel is injected in the expansion chamber 43 to continue the combustion, thereby supporting the zoned and / or mixed combustion of the two fuels. Preferably, one of the two fuels can be methanol or a methanol-containing fuel, which helps to clean or avoid the production of carbon deposits during combustion. The zoned stratified combustion can also be achieved if the first and second fuels are the same fuel. The present disclosure is not limited to the above-mentioned ways, and various ways can be flexibly adopted as needed.

[0110] In a preferred design of the method according to the present disclosure, the combustion of the air-fuel mixture is ignited by a spark plug or by compression ignition. The combustion of the air-fuel mixture can be ignited by a spark plug in the multi-functional plenum 80 and / or the expansion chamber 43, or by compression ignition, in particular lean homogeneous compression ignition.

[0111] Some embodiments of the present disclosure have been introduced for the purpose of illustration, but the present disclosure is not limited to these embodiments. Many modifications and variations can also be conceived by those skilled in the art. Therefore, these embodiments are chosen and described in order to better illustrate the principles of the present disclosure, its practical application, and to enable those skilled in the art to understand its content, i.e., all modifications and variations made without departing from the spirit of the present disclosure will fall within the scope of protection of the present disclosure as defined by the appended claims.

Claims

1. A sealing mechanism for a rotary mechanism, the rotary mechanism comprising: a rotor having a rotor disc (1); a stator housing the rotor; wherein the sealing mechanism comprises a convex first flow barrier (4) provided on an end face of the rotor disc (1) and dimensioned to allow a combined deployment of a labyrinth seal and a spiral seal thereon; a concave first counter flow barrier (5) provided on an inner surface of the stator and clearance-fitted to the first flow barrier (4); wherein the first flow barrier (4) has a first recess and / or protrusion (6) on its peripheral face and the first counter flow barrier (5) is flatly configured on its peripheral face or has a first counter recess and / or protrusion (7) clearance-fitted to the first recess and / or protrusion (6), wherein the first flow barrier (4) and the first counter flow barrier (5) each form a labyrinth seal on their respective top or bottom section and each form a spiral seal on their respective one side section.

2. The sealing mechanism of claim 1, wherein, The first flow barrier (4) and the first counter flow barrier (5) each form a spiral seal or a labyrinth seal on their respective other side section.

3. The sealing mechanism of claim 1, wherein, The end face of the rotor disc (1) is provided with a second recess and / or protrusion (8) and the inner surface of the stator is provided with a counter second protrusion and / or recess (9) clearance-fitted to the second recess and / or protrusion (8), the second recess and / or protrusion (8) and the counter second protrusion and / or recess (9) forming a labyrinth seal.

4. The sealing mechanism of claim 1, wherein, A sealing medium is provided in the gap between the rotor disc (1) and the stator (30) in a portion or all of the area between at least two of the first flow barriers (4).

5. The sealing mechanism of claim 4, wherein, The sealing medium is one or more of a lubricating grease, a lubricating liquid, a cooling liquid, a magnetic fluid, a self-lubricating material.

6. The sealing mechanism of claim 5, wherein, The rotary mechanism comprises a sealing liquid circulation device (15) which works by self-circulation using a pressure difference, the sealing liquid circulation device (15) having an introduction portion (26) and a liquid collection portion (27) opened on the main stator (30) and a guide circuit (24) connecting the introduction portion (26) of the liquid low-pressure area barrier above the main shaft and the liquid collection portion (27) of the gas high-pressure area barrier below the main shaft.

7. The sealing mechanism of claim 1, wherein, The stator which wraps the rotor disc (1) is provided with a honeycomb sealing structure and / or a hole groove sealing structure and / or a brush sealing structure and / or a sheet sealing structure.

8. The sealing mechanism of claim 1, wherein, The rotor has a piston (2) connected to the edge of the rotor disc (1), the stator (30) wrapping the piston (2) so that a cavity as a cylinder (40) is formed on the rotation path of the piston (2).

9. The sealing mechanism of claim 8, wherein, The rotor disc (1) has a third flow barrier (17) partially surrounding the piston (2) and the cylinder (40) on the side and / or bottom side of the piston (2) and the cylinder (40).

10. The sealing mechanism of claim 9, wherein, The third flow barrier (17) has a third recess and / or protrusion (12) on its peripheral face.

11. The sealing mechanism of claim 8, wherein, The piston (2) has a fourth recess (11) on its top side.

12. The sealing mechanism of claim 8, wherein, The rotor is a main convex rotor (10), the stator is a main stator (30), the rotating mechanism (100) further comprises an auxiliary concave rotor (20) and an auxiliary stator (34) containing the auxiliary concave rotor (20), the auxiliary concave rotor (20) has an auxiliary rotating disc (25) and an annular outer extension (28) surrounding the auxiliary rotating disc (25), the annular outer extension (28) has a concave recess (3) cooperating with the piston (2), so that the piston (2) can be contained and passed through the concave recess (3) when rotating.

13. The sealing mechanism of claim 12, wherein, The auxiliary rotating disc (25) of the auxiliary concave rotor (20) has a concave and / or convex second flow blocking part (13) arranged on the end face thereof, and the auxiliary stator (34) has a convex and / or concave second corresponding flow blocking part (14) arranged on the inner surface thereof, which is in clearance fit with the second flow blocking part (13).

14. The sealing mechanism of claim 13, wherein, The second flow blocking part (13) and the second corresponding flow blocking part (14) are flatly configured on the peripheral surface thereof or have a fifth convex and / or concave part and a fifth corresponding concave and / or convex part in clearance fit with each other; the end face on the auxiliary rotating disc (25) is partially flatly configured or provided with a sixth convex and / or concave part.

15. The sealing mechanism of claim 12, wherein, The auxiliary stator (34) has a circumferential flow collecting groove (36) and a flow guide groove (35) connected with the circumferential flow collecting groove (36) on the inner surface thereof wrapping the annular outer extension (28).

16. The sealing mechanism of claim 12, wherein, A flow throwing groove (37) is arranged on the rotating disc (1) of the main convex rotor (10) and / or the auxiliary concave rotor (20).

17. The sealing mechanism of any one of claims 1-16, wherein, The rotating mechanism (100) is an internal combustion engine, an expander, a compressor or a pump.

18. A rotating mechanism (100), comprising: a rotor having a rotating disc (1); a stator containing the rotor; wherein the rotating mechanism (100) comprises the sealing mechanism according to any one of the preceding claims.

19. The rotation mechanism (100) according to claim 18, wherein The rotor has a piston (2) connected with the edge of the rotating disc (1), and the stator contains the piston (2), so that a cavity is formed in the rotating path of the piston (2) as a cylinder (40).

20. The swivel mechanism (100) according to claim 18, wherein The rear face of the piston (2) with reference to the rotating direction thereof is a plane or a concave surface, and the front face of the piston (2) with reference to the rotating direction thereof is a convex surface or a concave surface or a plane.

21. The swivel mechanism (100) according to claim 18, wherein The piston (2) has a circular or elliptical or rounded rectangular shape.

22. The swivel mechanism (100) according to claim 18, wherein The rotating mechanism (100) further comprises a liquid recovery, storage and replenishment mechanism for sealing a liquid circulating device (15) in the shutdown state of the rotating mechanism (100), which comprises a one-way driving mechanism, a liquid recovery and storage mechanism (31) and a liquid replenishment pipe (32).

23. The rotation mechanism (100) according to any one of claims 18-21, wherein The rotating mechanism (100) further comprises a cylinder cutting mechanism, which cuts the cylinder (40), so that the volume of the cylinder (40) is variable with the rotation of the piston (2).

24. The rotation mechanism (100) according to claim 23, wherein The cylinder cutting mechanism is a secondary concave rotor (20) or a card, the secondary concave rotor (20) has a secondary rotary disc (25) and an annular extension (28) surrounding the secondary rotary disc (25), the annular extension (28) also has a concave recess (3) matched with the piston (2), the cylinder (40) is cut off by the annular extension (28) of the secondary concave rotor (20) or the card.

25. The rotation mechanism (100) according to claim 24, wherein The stator is a main stator (30), the rotor is a main convex rotor (10), the rotating mechanism (100) further comprises 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), a spiral portion (81) is arranged on the main shaft (82) and the auxiliary shaft (83), when the main shaft (82) and the auxiliary shaft (83) rotate, the spiral portion (81) drives fluid or grease towards a direction opposite to a leakage direction.

26. The rotation mechanism (100) according to claim 25, wherein The rotating mechanism (100) comprises a main gear (71) connected with the main shaft (82) and an auxiliary gear (72) connected with the auxiliary shaft (83), the transmission ratio of the main gear (71) and the auxiliary gear (72) is 1:n, wherein n≥1.

27. The rotation mechanism (100) according to claim 26, wherein The rotating mechanism (100) comprises a compression ring, the cylinder (40) of the compression ring is divided into an intake chamber (41) and a compression chamber (42) by the piston (2).

28. The rotation mechanism (100) according to claim 27, wherein The compression ring comprises a valve (38) for adjusting the intake amount.

29. The rotation mechanism (100) according to claim 27, wherein The rotating mechanism (100) comprises an expansion ring, the cylinder (40) of the expansion ring is divided into an expansion chamber (43) and an exhaust chamber (44) by the piston (2).

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

31. The rotation mechanism (100) according to claim 30, wherein The rotating mechanism (100) further comprises a multifunctional gas chamber (80) connected between the expansion chamber (43) of the expansion ring and the compression chamber (42) of the compression ring through a connecting pipe (84) provided with a one-way valve, the multifunctional gas 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 and / or gas mixing and / or combustion.

32. The rotation mechanism (100) according to claim 31, wherein The rotating mechanism (100) sprays single or different fuels in the multifunctional gas chamber (80) through the additional fuel injection mechanism (16) and / or in the expansion chamber (43) through the fuel nozzle (21).

33. The rotation mechanism (100) according to claim 32, wherein The rotating mechanism (100) compresses or ignites the mixture of air and fuel in the multifunctional gas chamber (80) and / or the expansion chamber (43) by compression ignition or through the spark plug.

34. The rotation mechanism (100) according to claim 33, wherein The rotating mechanism (100) intermittently operates on demand by means of misfire and / or controls the temperature of the expansion ring and the cylinder.

35. The rotation mechanism (100) according to claim 31, wherein The rotating mechanism (100) further comprises a one-way exhaust gas return mechanism (70) connected between the multifunctional gas chamber (80) and the exhaust pipe (73).

36. The swivel mechanism (100) according to claim 30, wherein The rotating mechanism (100) further comprises a fairing housing (50) and a fan (60), the fairing housing (50) at least containing the compression ring and / or the expansion ring and the fan (60), an air duct being formed in the fairing housing (50) to guide air flow.

37. The rotation mechanism (100) according to claim 36, wherein between the expansion ring and the compression ring or between the expansion ring and the main gearwheel (71) and / or the auxiliary gearwheel (72) has a profiled portion or a profiled portion, guiding the air flow to the back and / or front of the expansion ring not directly blown by the fan (60).

38. The rotation mechanism (100) according to claim 37, wherein The The The Or shape.

39. The rotation mechanism (100) according to claim 36, wherein The fan (60), the expansion ring, the compression ring and the gear are connected in sequence by a shaft; or the fan (60), the compression ring, the expansion ring and the gear are connected in sequence by the shaft.

40. The rotation mechanism (100) according to claim 37 or 39, wherein The rotating mechanism (100) has a tail jet outlet.

41. The rotating mechanism (100) according to claim 37 or 39, the exhaust pipe (73) of the expansion ring extending to a tail region of the air duct.

42. The rotation mechanism (100) of claim 40, wherein The exhaust gas discharged by the exhaust pipe (73) of the expansion ring in the tail region of the air duct mixes with air in the air duct and expands, and is discharged through the tail jet outlet, thereby generating thrust.

43. The swivel mechanism (100) according to claim 26, wherein The rotating mechanism (100) further comprises an electromagnetic device (90), the electromagnetic device (90) comprising a fixed induction coil (96) close to the main gear (71), a carrier (97) carrying the induction coil (96), and a first magnet (95) arranged on the main gear (71).

44. The rotation mechanism (100) according to claim 43, wherein The first magnet (95) on the main gear (71) rotates relative to the induction coil (96), thereby generating electric power; the current size, direction and frequency of the induction coil (96) are controlled so that the main gear (71) is driven to rotate by the first magnet (95), thereby generating power.

45. The swivel mechanism (100) according to claim 26, wherein The rotating mechanism (100) further comprises a piston position maintaining device (98), the piston position maintaining device (98) comprising a second magnet (91), a pressure relief member (92), a spring (93) and a shell (94).

46. The rotation mechanism (100) according to any one of claims 18-45, wherein The rotating mechanism (100) is an internal combustion engine, an expander, a compressor or a pump.

47. A method for sealing a rotating mechanism (100) according to any one of claims 18-46, the rotating mechanism (100) comprising: a main convex rotor (10) having a rotor disc (1) and a piston (2) connected with the edge of the rotor disc (1); a secondary concave rotor (20) having a secondary rotor disc (25), an annular outer extension (28) and a concave recess (3) cooperating with the piston (2); a main stator (30) and a secondary stator (34) containing the main convex rotor (10) and the secondary concave rotor (20) respectively, wherein a cavity as a cylinder (40) is formed inside the main stator (30) on the path of the rotation of the piston (2); wherein a sealing mechanism is provided for the rotating mechanism (100), the sealing mechanism comprising a concave and / or convex first flow blocking part (4) arranged on the end surface of the rotor disc (1); a convex and / or concave first corresponding flow blocking part (5) arranged on the inner surface of the main stator (30) in clearance fit with the first flow blocking part (4).

48. The method of claim 47, wherein, A third flow barrier is arranged at the edge of the rotary plate (1) to partially enclose the bottom side and / or the side of the piston and the cylinder.

49. The method of claim 47, wherein, The inner surface of the auxiliary stator (34) is provided with a flow guide groove along the auxiliary stator (34) to guide the leakage gas to converge towards the circumferential flow converging groove away from the leakage gap and to be brought back to the cylinder (40) by the recess part when rotating.

50. The method of claim 47, wherein, A sealing medium is arranged in the gap between the rotary plate (1) and the stator (30) in the area between the at least two first flow barriers (4) to block the leakage of working fluid.

51. The method of claim 50, wherein, The sealing liquid is caused to return from the gas high-pressure area barrier below the main shaft (82) near the cylinder (40) to the liquid low-pressure area barrier above the main shaft (82) near the main shaft (82) by pressure difference.

52. The method of claim 47, wherein, The exhaust gas discharged from the exhaust chamber (44) of the expansion ring of the rotating mechanism (100) is partially mixed with compressed air in the multifunctional gas chamber (80).

53. The method of claim 52, wherein, The fan (60) blows external air into the fairing housing (50) to form an air duct to guide the air flow, and the air cooling reduces the heat of the expansion ring, and the cold air takes away the heat energy of the expansion ring to become hot air, which is sucked into the air inlet of the compression ring of the rotating mechanism (100) to participate in work, so that the heat energy lost by the expansion ring is recycled in a closed loop.

54. The method of claim 53, wherein, The exhaust gas discharged from the exhaust pipe (73) of the expansion ring in the tail area of the air duct is mixed with the air in the air duct and expands, and is discharged through the tail jet outlet of the rotating mechanism (100), thereby generating thrust.

55. The method of claim 52, wherein, Single or different fuels are injected in the multifunctional gas chamber (80) and / or the expansion chamber (43), and / or air and fuel mixture is combusted.

56. The method of claim 55, wherein, The combustion of the air and fuel mixture is carried out by spark plug ignition or by compression ignition.

57. The method of claim 56, wherein, The internal combustion engine is intermittently operated on demand by misfire.

58. The method of claim 57, wherein, The temperature of the expansion ring and / or the cylinder is controlled by misfire.

59. The method of claim 58, wherein, According to the operation plan under the working condition, after the internal combustion engine completes the i-th combustion cycle, fuel injection is stopped in the subsequent i+j-th misfire cycle, and the exhaust gas is partially mixed with compressed air in the multifunctional gas chamber (80) and returned to the expansion chamber (43) to expand and do work, and in the subsequent i+j+p-th misfire cycle, fuel injection is stopped and air compression is not stopped, and in the i+j+p+q-th misfire cycle, fuel injection is stopped and air compression is stopped, where i≥1, j, p, q≥0, and at least one of j, p, q is not 0.

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