Rotating mechanism and sealing mechanism and sealing method thereof

Abstract

The invention relates to a rotating mechanism and a sealing mechanism and a sealing method thereof, and the rotating mechanism comprises a main convex rotor which is provided with a rotating disc and a piston connected with the edge of the rotating disc; the auxiliary concave rotor is provided with a concave notch part matched with the piston; and a main stator and an auxiliary stator accommodating the main convex rotor and the auxiliary concave rotor, respectively, in which a cavity as a cylinder is formed on a path in which the piston rotates inside the main stator. The sealing mechanism comprises a concave and / or convex first choked flow part arranged on the turntable and a first corresponding choked flow part which is arranged on the main stator and is in clearance fit with the first choked flow part, and the first choked flow part is provided with a first concave part and / or a convex part on the peripheral surface of the first choked flow part; the first corresponding flow choking part is provided with a first corresponding convex part and / or concave part on the peripheral surface of the first corresponding flow choking part, wherein the first corresponding convex part and / or concave part is in clearance fit with the first concave part and / or convex part. Fluid leakage prevention of the rotating mechanism is achieved, the piston is even in stress and not prone to deformation, various mixing and combustion modes of air and fuel can be flexibly achieved, and the heat efficiency and the power-to-weight ratio are improved.

Description

Technical Field

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

[0002] An internal combustion engine is a power machine that converts heat energy into mechanical energy by burning a mixture of air and fuel. It can be mainly divided into a gas turbine with continuous combustion, a reciprocating piston internal combustion engine with intermittent combustion, and an eccentric shaft rotor internal combustion engine. Gas turbines (including turbojets, turbofans, turboshafts, etc.) have high speed, high power, and high power-to-weight ratio, but continuous combustion leads to very high fuel consumption and high manufacturing costs. A 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. It has the advantages of low fuel consumption and low manufacturing cost, but it also has problems such as low power-to-weight ratio, low speed, and waste of energy in reciprocating motion. Both types of internal combustion engines are mass-produced. The eccentric shaft rotor internal combustion engine has the advantages of high speed and small size, but it also has the disadvantages of high fuel consumption, poor sealing, high friction and wear, poor durability, incomplete combustion, and substandard emissions, and has basically stopped production. Rotary engines with eccentric shafts or other types (such as rectangular pistons) have long suffered from problems of incomplete combustion and poor sealing, which has become a century-old problem that hinders the development of rotary engines. Summary of the invention

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

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

[0005] A rotor, the rotor having a rotating disk;

[0006] The stator houses the rotor.

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

[0008] The size of the blocking part is usually much larger than the (labyrinth or other) seal. Through the blocking part of the sealing mechanism disclosed in the present invention, the leakage direction of the working fluid can be greatly changed, and the leakage path of the working fluid can be greatly extended, which solves the problem of insufficient sealing space in traditional rotating mechanisms, so that more seals and various types of seals can be deployed on the leakage path to prevent the leakage of the working fluid. The composite structure and the comprehensive use of a large number of multiple seals after extending the leakage path can basically solve the problem of working fluid leakage in the rotating mechanism.

[0009] In one embodiment of the first aspect of the present disclosure, a second concave portion and / or convex portion is locally flatly constructed or arranged on the end surface of the rotating disk, and a corresponding second convex portion and / or concave portion that is clearance-matched with the second concave portion and / or convex portion is locally flatly constructed or arranged on the inner surface of the stator and / or a brush seal structure and / or a thin sheet seal structure is arranged. The fluid leakage can be greatly reduced by the brush seal and / or thin sheet seal. In this way, the sealing performance is further improved.

[0010] In one embodiment according to the first aspect of the present disclosure, the first recess and / or protrusion and the first corresponding protrusion and / or recess and the second recess and / or protrusion and the corresponding second protrusion and / or recess form a spiral seal and / or a labyrinth seal and / or a gap seal and / or a hole-slot seal and / or a honeycomb seal. By means of the spiral seal provided on the flow-blocking portion, the fluid is driven in a direction opposite to the leakage direction of the working fluid. By means of the labyrinth seal and / or the hole-slot seal and / or the honeycomb seal, a pressure drop and a vortex are generated, the fluid leakage pressure is reduced, the fluid leakage is further suppressed, and the sealing performance is improved.

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

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

[0013] In one embodiment of the first aspect of the present disclosure, the rotary disk has a third flow blocking portion located on the bottom side and / or the side of the piston and partially surrounding the piston and the cylinder. The third flow blocking portion can significantly change the leakage direction, significantly extend the leakage path, and prevent the working fluid from leaking directly toward the central axis area of ​​the rotary disk, thereby further improving the sealing performance. In one embodiment of the present disclosure, the third flow blocking portion has a third concave portion and / or convex portion on its peripheral surface, which helps to further improve the sealing performance.

[0014] In one embodiment according to the first aspect of the present disclosure, the piston has a fourth recess on its top side. Through the specially designed pressure relief groove on the top side of the piston, the leaking gas generates a pressure drop and a vortex, which inhibits the gas from flowing to the opposite side, thereby improving the sealing performance.

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

[0016] In one embodiment of the first aspect of the present disclosure, the auxiliary stator has a circumferential flow collecting groove and a flow guide groove connected thereto on its inner side surface. In one embodiment of the present disclosure, a flow slinging groove is provided on the main convex rotor and / or the auxiliary concave rotor rotating disk, thereby improving the sealing performance.

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

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

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

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

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

[0022] In one embodiment according to the second aspect of the present disclosure, the piston is circular or oval or rounded rectangular. The circular or oval piston allows the gas in the circular or oval ring cylinder of the same shape to burn more completely and with higher combustion efficiency, and also makes the thermal stress on the piston more uniform, thus avoiding thermal deformation of the piston and causing cylinder jam.

[0023] In one embodiment according to the second aspect of the present disclosure, the rotating mechanism further includes an autonomously operated sealed liquid circulation device, which has an introduction portion and a liquid collecting portion opened on the main stator, and a guide circuit connecting the introduction portion of the liquid low-pressure area flow resistance portion located above the main shaft and the liquid collecting portion of the gas high-pressure area flow resistance portion located below the main shaft. The liquid can be used for sealing, cooling, and lubrication, for example. In this way, it is possible to use the sealed liquid to prevent gas leakage in a closed-loop automatic circulation, thereby improving the sealing performance.

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

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

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

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

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

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

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

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

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

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

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

[0035] In an implementation according to the third aspect of the present disclosure, according to the operating plan, after the internal combustion engine completes the i-th combustion cycle, in the subsequent i+j-th sparking cycle, the fuel injection is stopped and the exhaust gas is partially mixed with the compressed air through the multifunctional chamber and returned to the expansion chamber to expand and perform work, and in the subsequent i+j+p-th sparking cycle, the fuel injection is stopped without stopping the air compression, and in the i+j+p+q-th sparking cycle, the fuel injection is stopped and the air compression is stopped, wherein i≥1, j, p, q≥0. In this way, the power requirements and fuel saving requirements under various operating 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 thereof according to the present disclosure are also applicable to the method according to the present disclosure. BRIEF DESCRIPTION OF THE DRAWINGS

[0037] In order to better understand the above and other purposes, features, advantages and functions of the present disclosure, reference may be made to the preferred embodiments shown in the accompanying drawings. The same reference numerals in the accompanying drawings refer to the same components. It should be understood by those skilled in the art that the accompanying 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 components in the drawings are not drawn to scale.

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

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

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

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

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

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

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

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

[0046] Fig. 9 The circumferential flow collecting groove and the flow guiding groove on the auxiliary stator of the rotating mechanism are shown;

[0047] Fig.10 is a partially exploded stereoscopic diagram of the rotating mechanism;

[0048] Fig.11 is an assembled stereogram of the multifunctional air chamber of the rotating mechanism;

[0049] Fig.12 yes Figure 4 A top perspective view of a rotating mechanism;

[0050] Fig.13 is a three-dimensional diagram of the electromagnetic device of the rotating mechanism;

[0051] Fig.14 Shows Fig.13 Another magnetic force generating mechanism of the piston position holding device;

[0052] Figures 15A-15C It is a combined stereogram of the main convex rotor and the auxiliary concave rotor of the rotating mechanism, which respectively shows three embodiments of the turntable without the third flow blocking part, with the third flow blocking part in the shape of a medium wine glass, and with the third flow blocking part in the shape of a tall wine glass;

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

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

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

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

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

[0058] Fig.21 The principle of suppressing gas leakage by using a spiral seal and a labyrinth seal through a first flow blocking portion and a first corresponding flow blocking portion, a first / second convex portion and / or concave portion, and a first / second corresponding concave portion and convex portion is shown;

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

[0060] Fig.23 The design of the piston top side of the rotating mechanism is shown;

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

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

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

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

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

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

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

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

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

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

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

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

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

[0074] In another embodiment C of the present disclosure, the multifunctional air chamber 80 plays the role of gas storage and gas mixing. When the ignition and combustion timing comes, an appropriate amount of fuel is injected into the multifunctional air chamber 80 through the additional fuel injection mechanism 16 to mix with the stored compressed air at an appropriate air-fuel ratio (the temperature and pressure at this time ensure that the mixed gas will not be compression ignited), and the second one-way valve 22" is opened through electrical (magnetic) control, so that the mixed gas is transferred to the expansion chamber 43, and ignited and burned through the spark plug 23 of the expansion chamber, and expanded to do work.

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

[0076] In another embodiment E of the present disclosure, a fuel injection mechanism 16 is added to the multifunctional air chamber 80 to inject a proper amount of fuel and mix it with the stored compressed air at a proper air-fuel ratio (the temperature and pressure at this time prevent the mixed gas from being compression-ignited), and the mixed gas is ignited by an additional spark plug 85 when the ignition combustion timing arrives. The second one-way valve 22" is opened by electrical (magnetic) control or by generating pressure through the heat energy released by combustion in the multifunctional air chamber 80 to transfer the combustion gas to the expansion chamber 43 of the second layer (expansion ring) to continue combustion, expansion and work.

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

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

[0079] In one embodiment of the present disclosure, the main convex rotor 10 and the main stator 30 in the first layer (compression ring) formed with the air 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 to reduce weight and further improve the power-to-weight ratio. In one embodiment of the present disclosure, the main and auxiliary rotors of the expansion ring and the compression ring are of 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 of 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 arbitrary adjustment of the compression ratio within a certain range. In one embodiment of the present disclosure, the main convex rotor 10 and the auxiliary concave rotor 20 achieve mass static balance and dynamic balance by hollowing out local materials. For example, the annular extension 28 of the auxiliary concave rotor 20 is a hollow annular extension 28, so that the auxiliary concave rotor 20 achieves static / dynamic balance.

[0080] Depend on Figures 1 to 3 It can be seen that in an exemplary embodiment of the present disclosure, the rotating mechanism 100 further includes a fairing housing 50 and a fan 60. The fairing housing has the function of adjusting the airflow. The fan 60 is installed on the main shaft 82 in the fairing housing 50. In addition, the fan 60 can also be arranged on the auxiliary shaft 83, see Figure 1 , Figure 3 to Figure 4 , Fig.12 The number of fans 60 is not limited to this. The main shaft and / or the auxiliary shaft can be equipped with any number of fans, for example, only the main shaft when the number is 1, both on the main shaft or on the two auxiliary shafts when the number is 2, 1 main shaft and 2 auxiliary shafts when the number is 3, 2 on the main shaft and 2 on the auxiliary shafts when the number is 4, and so on. The fairing housing 50 accommodates the fan, the expansion ring, and the compression ring, and has a The air duct is formed inside the fairing housing 50 to guide the air to flow to the back of the expansion ring which is not directly blown by the fan so that the expansion ring can be cooled both in front and behind. Optionally, the fairing housing 50 can also additionally accommodate 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 through the main shaft 82 and / or the auxiliary shaft 83 to work together. Therefore, through the air duct formed in the fairing housing 50, the fan 60 continuously blows the outside air into the fairing housing 50 to cool the hot expansion ring. The cold air absorbs and takes away the heat emitted by the hot expansion ring, and becomes hot air to enter the air intake chamber 41 of the compression ring to participate in the next power cycle, thereby recovering the heat energy lost from the cooling of the hot expansion ring in a closed loop and improving the thermal efficiency. Heating the air helps to increase the temperature of the compressed air, making it easier for fuel with a higher ignition point to achieve compression ignition, thereby improving the combustion efficiency and thermal efficiency. The number, size and speed of the fans can also be adjusted as needed to further adjust the compression ratio. It should be noted that the fairing housing 50, the main stator 30 and the auxiliary stator 34 can be disassembled into two symmetrical halves, so that the fan 60 and other components, the main convex rotor 10 and the auxiliary concave rotor 20 can be accommodated therein respectively during assembly, and then they can be assembled together, see Figure 3 In some embodiments, the half main stator 30 and the half auxiliary stator 34 are integrally constructed by methods such as 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, etc.

[0081] In an exemplary embodiment of the present disclosure, see Fig.13 The rotating mechanism 100 further includes an electromagnetic device 90, which includes a fixed induction coil mechanism close to the main gear 71 and a first magnet 95 disposed on the main gear 71. Figures 1 to 3 , Fig.12 , Fig.13, the induction coil mechanism may also include, for example, an induction coil 96 and a bearing portion 97 for bearing the induction coil 96. In a preferred embodiment, the induction coil 96 is spirally drawn on the bearing portion 97 which is a PCB printed circuit board. A bearing portion 97 with a coil 96 is provided on one or both sides of the main gear 71, and the main shaft 82 drives the main gear 71 to rotate relative to the fixed bearing portion 97, so that the first magnet 95 on the main gear 71 rotates relative to the fixed coil 96, thereby the induction coil 96 generates electricity to form a generator. By controlling the magnitude, direction and frequency of the current energized to the induction coil 96 by the control circuit, this set of electromagnetic devices can be used as a starter and motor to drive the gears and the main shaft to rotate, start the internal combustion engine and / or output power. In this way, the functions of the motor and the generator 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 maintaining mechanism 98 is used to replace the electromagnetic device 90, for example, it is arranged on the bottom surface of the housing 50, such as Fig.14 As shown, it has a shell 94 and a second magnet 91 and a spring 93 contained in the shell 94. A pressure relief member 92 is provided on the shell 94. The pressure relief member 92 can 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, so that the piston is kept at a specific position when it stops rotating. During the operation of the internal combustion engine, the high-pressure air in the fairing shell 50 enters the shell 94 through the pressure relief member 92, and pushes the second magnet 91 to move in the shell 94 against the elastic force of the spring 93, thereby compressing the spring 93. As a result, the position of the second magnet 91 deviates, that is, it is not aligned with the first magnet 95, 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 shell 50, and the high-pressure air in the duct no longer exists. Since there is no pressure of the high-pressure gas, the spring 93 resets and pushes the second magnet 91 back to the initial position. At this time, the second magnet 91 located on the fixed housing 50 attracts the first magnet 95 of opposite polarity located on the main gear 71 to a position aligned therewith, thereby driving the main gear 71 to rotate to a specific position, and then the main convex rotor 10 and its piston 2 coaxially fixedly connected to the main gear 71 stop at a predetermined position, such as just stopping at a position where the spark plug 23 can ignite and burn. In this position, fuel can be directly injected into the expansion chamber 43 without the drive of the starter, and the mixture of air and fuel in the expansion chamber 43 can be ignited through the spark plug 23, thereby achieving (starter-free) self-starting of the rotating mechanism. The above is only an exemplary embodiment of the piston position holding device, and the present disclosure is not limited to this.

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

[0083] In one embodiment of the present disclosure, as can be seen from FIG. 16 , the cross section of the piston 2 can be, for example, circular (see Fig. 16B ), oval (see Fig.16A ), rounded rectangle (see Fig. 16C) and other shapes, but the present disclosure is not limited to this. For example, the compression ring has only two strokes, intake and compression, and does not require combustion, so there will be no thermal stress deformation. Therefore, the shape of the piston 2' of the compression ring does not have to be limited to a circle or an ellipse. It can be in many shapes here, such as a rectangle or a rounded rectangle, and can have any desired width, thereby achieving any compression ratio within a certain range. The mixed gas in the expansion chamber of the expansion ring needs to burn and expand to push the piston 2" to do work. Compared with a rectangular cylinder, which may not burn fully, a circular or elliptical ring cylinder 40 can make the combustion more complete and the combustion efficiency higher. The piston 2" is preferably circular or elliptical here, which also makes the thermal stress distribution of the piston 2" more uniform, avoiding the deformation of the piston 2" due to heat. On the contrary, if the cross-section of the piston 2" of the expansion ring is, for example, a rectangle, the uneven thermal stress on its corners may cause the piston 2" to deform, thereby increasing the gap between the main stator 30 and the piston 2", causing gas leakage, thrust and power reduction, and long-term operation may even cause the piston 2" and the stator 30 to get stuck (stuck in the cylinder) and damaged, causing the rotating mechanism to fail or be scrapped. Therefore, the design of the circular or elliptical piston disclosed in the present invention not only solves the problem of incomplete combustion in traditional eccentric shaft rotor engines, but also solves the problem of easy thermal stress deformation of some rectangular piston rotor engines.

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

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

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

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

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

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

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

[0091] See also Fig.23 In a preferred embodiment of the present disclosure, the piston 2 has a fourth recess 11 on its top side. Fig.23 It can be seen that the fourth recess 11 on the top side of the piston 2 can be, for example, one or more pressure relief grooves of different depths, such as grooves in the shape of rectangle, semicircle, triangle, trapezoid, etc. In this exemplary embodiment, there are three grooves, for example. Among the three grooves, the two small grooves on the left and right sides are, for example, 0.01-0.2 mm deep, and the large groove in the middle is, for example, 1-2 mm deep and 1-2 mm wide. The leaked gas has a sudden pressure drop here and generates a vortex. This prevents the cylinders on both sides of the piston from leaking gas from each other.

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

[0093] In a preferred embodiment of the present disclosure, see Figure 3 , Figure 6 , Fig. 9 , Fig.10 The auxiliary stator 34 has a circumferential flow collecting groove 36 on the inner side of the circumferential edge of the annular extension 28, and has a plurality of guide grooves 35 connected to the circumferential flow collecting groove 36. The width and depth of the circumferential flow collecting groove can be, for example, 1 to 3 mm, and the width and depth of the guide groove can be, for example, 0.2 to 1 mm. Their cross-sections can be the same or different, and can be trapezoidal, rectangular, semicircular, etc. The guiding direction of the guide groove 35 is consistent with the rotation direction of the auxiliary concave rotor 20 (such as Fig. 9The auxiliary concave rotor 20 has a plurality of grooves 35 and a plurality of grooves 36, and the plurality of grooves 35 are connected to the auxiliary concave rotor 20. The auxiliary concave rotor 20 has a plurality of grooves 35 and a plurality of grooves 36 ...

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

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

[0096] See also Fig. 22 In a preferred embodiment of the present disclosure, the rotating mechanism 100 further includes a sealing liquid circulation device 15 that can work autonomously, for making the sealing liquid between the end surface of the turntable 1 and the inner surface of the main stator 30 circulate autonomously, see Fig. 22 The solid arrow "M" in the figure indicates the direction in which the sealing liquid is driven by the spiral seal and the centrifugal force, and the dotted arrow "G" indicates the direction of gas leakage. Preferably, the device 15 is deployed between two or more flow-blocking parts close to the shaft. The sealing liquid can flow in the gap between the main stator 30 and the main convex rotor 10 for sealing, cooling, lubrication, etc. The liquid may include, but is not limited to, engine oil, lubricating oil, cooling oil, multifunctional oil, water, magnetic fluid or other liquids with low friction coefficient and non-volatile properties, as well as composite liquids. The sealing liquid circulation device 15, for example, includes an introduction part 26 and a liquid collecting part 27 opened on the main stator 30, and a guide circuit 25 connecting the introduction part 26 and the liquid collecting part 27, and a sealing liquid stored in the liquid collecting part 27 with a volume accounting for, for example, 30% to 70%, and when it is lower than, for example, 30%, it needs to be replenished. The introduction part 26 is, for example, configured as a hole, which is located near the liquid low-pressure area flow-blocking part above the main shaft 82. The opening of the liquid collecting portion 27 is located at the gas high pressure area flow resistance portion below the main shaft 82, so that the pressure difference between the high pressure area and the low pressure area can be used to make the stored sealing liquid automatically circulate back along the guide loop 25 to the introduction portion 26 (such as the flow resistance portion above the main shaft 82) of the flow resistance portion. Fig. 22 The guide loop 25 can be designed as one or more return liquid pipes or return liquid channels, etc. The opening of the liquid collecting part 27 is arranged at the intersection area on the flow barrier where the expected pressure of the sealing liquid and the leakage gas is balanced. The sealing liquid circulation device 15 can be applied to both the expansion ring and the compression ring.

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

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

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

[0100] In a preferred design of the method according to the present disclosure, spiral seals and / or labyrinth seals and / or gap seals and / or slot seals and / or honeycomb seals and / or brush seals and / or sheet seals and / or magnetic fluid seals are used on the turntable 1 to prevent gas leakage. These seals can be achieved by using the various flow blocking parts, concave parts and / or convex parts that cooperate with each other as described above.

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

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

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

[0104] In a preferred design of the method according to the present disclosure, the internal combustion engine can be operated intermittently as needed through the spark jump mode. During the spark jump, the internal combustion engine stops injecting fuel and igniting combustion. Since the energy storage of the main and auxiliary ring inertia flywheel is converted into energy release, the internal combustion engine can continue to operate, thereby saving fuel. The effect is far better than that of reciprocating piston and eccentric shaft rotor engines. In a preferred design of the method according to the present disclosure, the temperature of the internal combustion engine and / or the expansion ring and / or the cylinder can be accurately controlled through the spark jump mode. During the spark jump operation, the temperature of the expansion ring and the cylinder 40 of the internal combustion engine will gradually decrease.

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

[0106] In a preferred design of the method disclosed herein, the internal combustion engine can be operated according to the operation plan. For example, after the internal combustion engine completes the i-th (i≥1) combustion cycle as planned, it ignites as planned according to the working conditions, stops injecting fuel but continues to compress air in the subsequent i+j-th (j≥0) ignition cycle, so that the exhaust gas stored in the air storage chamber or air storage tank (preferably with a three-way catalytic converter purification function) or the air storage / mixing multifunctional air chamber is partially returned to the expansion chamber 43 through the multifunctional air chamber to expand and do work by mixing compressed air, and stops injecting fuel but continues to compress air in the i+j+p-th (p≥0) ignition cycle, and stops injecting fuel and stops gas compression in the i+j+p+q-th (q≥0) ignition cycle, until the end of this round of plans, starts the next round of plans, and starts from 1 to i+j+p+q cycles; the following p+q times utilize the inertial flywheel effect of the main and auxiliary rings to release energy and do work. The internal combustion engine can continuously operate in the i+j+p+q cycle mode according to the operation plan, where i≥1, j≥0, p≥0, and q≥0. The values ​​of i, j, p, and q can be flexibly adjusted to meet the power requirements and fuel saving requirements under various working conditions.

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

[0108] In a preferred design of the method according to the present disclosure, the same or different fuels are burned in the multifunctional air chamber 80 and the expansion chamber 43 at different times (in different cycles). For example, the mth (m≥1) cycle first triggers the combustion of the first fuel in the multifunctional air chamber 80, and then the m+nth (n≥1) cycle triggers the combustion of the first fuel in the expansion chamber 43; the cycles are alternating. Alternatively, the mth (m≥1) cycle first triggers the combustion of the first fuel in the multifunctional air chamber 80, and then the m+nth (n≥1) cycle triggers the combustion of the second fuel in the expansion chamber 43; the cycles are alternating. Flexible adjustment of the values ​​of m and n can meet the needs 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 into the multifunctional air chamber 80 to cause the mixture of compressed air and fuel to burn, while an appropriate amount of the second fuel is injected into the expansion chamber 43 to continue burning, thereby supporting the partitioning and / or mixed combustion of the two fuels. Preferably, one of the two fuels can be methanol or a fuel containing methanol, which helps to remove carbon deposits or avoid the formation of carbon deposits during the combustion process. If the first fuel and the second fuel are the same fuel, partitioned and stratified combustion can also be achieved. The present disclosure is not limited to the methods listed above, and various methods can be flexibly adopted as needed.

[0110] In a preferred design of the method according to the present disclosure, the combustion of the air and fuel mixture is carried out by spark plug ignition or by compression ignition. The combustion of the air and fuel mixture can be carried out in the multifunctional air chamber 80 and / or the expansion chamber 43 by spark plug ignition, 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. Those skilled in the art may also think of many modifications and variations. Therefore, these embodiments are selected and described in order to better illustrate the principles and practical applications of the present disclosure and to enable those skilled in the art to understand the contents thereof, that is, without departing from the spirit of the present disclosure, all modifications and variations made will fall within the scope of protection of the present disclosure as defined by the appended claims.

Claims

1. A sealing mechanism for a rotating mechanism, the rotating mechanism comprising: A rotor having a rotating disk (1); a stator accommodating the rotor; The sealing mechanism comprises: a concave and / or convex first flow-blocking portion (4) arranged on the end surface of the rotating disk (1); and a convex and / or concave first corresponding flow-blocking portion (5) arranged on the inner surface of the stator and loosely matched with the first flow-blocking portion (4); wherein the first flow-blocking portion (4) is flatly constructed on its peripheral surface or has a first concave portion and / or convex portion (6), and the first corresponding flow-blocking portion (5) is flatly constructed on its peripheral surface or has a first corresponding convex portion and / or concave portion (7) loosely matched with the first concave portion and / or convex portion (6).

2. The sealing mechanism according to claim 1, wherein: The end surface of the turntable (1) is locally flat or provided with a second recess and / or protrusion (8), and the inner surface of the stator is locally flat or provided with a corresponding second protrusion and / or recess (9) that is clearance-matched with the second recess and / or protrusion (8) and / or provided with a brush seal structure and / or a thin-film seal structure.

3. The sealing mechanism according to claim 2, wherein: The first recess and / or projection (6) and the first corresponding projection and / or recess (7) as well as the second recess and / or projection (8) and the corresponding second projection and / or recess (9) constitute any one of the following sealing methods: spiral seal and / or labyrinth seal and / or gap seal and / or honeycomb seal and / or hole groove seal.

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

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

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

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

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

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

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

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

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

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

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

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

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

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

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

19. The rotating mechanism (100) according to any one of claims 16 to 18, wherein: The rotating mechanism (100) also includes an autonomously operating sealed liquid circulation device (15), the sealed liquid circulation device (15) having an introduction portion (26) and a liquid collecting portion (27) opened on the main stator (30), and a guide circuit (25) connecting the introduction portion (26) of the liquid low-pressure zone resistance portion located above the main shaft and the liquid collecting portion (27) of the gas high-pressure zone resistance portion located below the main shaft.

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

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

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

23. The rotating mechanism (100) according to claim 22, wherein: The rotating mechanism (100) further 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), wherein a spiral portion (81) is provided on the main shaft (82) and the auxiliary shaft (83), and when the main shaft (82) and the auxiliary shaft (83) rotate, the spiral portion (81) drives the fluid or grease in a direction opposite to the leakage direction.

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

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

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

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

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

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

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

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

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

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

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

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

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

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

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

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

40. A method for sealing a rotating mechanism (100) according to any one of claims 16 to 39, the rotating mechanism (100) comprising: A main convex rotor (10), the main convex rotor (10) having a rotating disk (1) and a piston (2), the piston (2) being connected to the edge of the rotating disk (1); An auxiliary concave rotor (20), the auxiliary concave rotor (20) comprising an auxiliary rotating disk (25), an annular extension (28) and a concave portion (3) cooperating with the piston (2); a main stator (30) and an auxiliary stator (34), wherein the main stator (30) and the auxiliary stator (34) respectively accommodate the main convex rotor (10) and the auxiliary concave rotor (20), wherein a cavity serving as a cylinder (40) is formed inside the main stator (30) on a rotation path of the piston (2); A sealing mechanism is provided for the rotating mechanism (100), and the sealing mechanism comprises: a concave and / or convex first flow blocking portion (4) provided on the end surface of the turntable (1); and a convex and / or concave first corresponding flow blocking portion (5) provided on the inner surface of the main stator (30) and loosely matched with the first flow blocking portion (4); wherein a first concave portion and / or convex portion (6) is evenly constructed or provided on the peripheral surface of the first flow blocking portion (4), and a first corresponding convex portion and / or concave portion (7) is evenly constructed or provided on the peripheral surface of the first corresponding flow blocking portion (5) and loosely matched with the first concave portion and / or convex portion (6).

41. The method of claim 40, wherein: A third flow-blocking portion is arranged on the edge of the rotating disk (1) and partially surrounds the bottom side and / or the side side of the piston and the cylinder.

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

43. The method of claim 40, wherein: In a part or all of the area between at least two of the blocking parts, a sealing medium is arranged in the gap between the rotating disk (1) and the stator (30) to prevent leakage of the working fluid.

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

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

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

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

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

49. The method of claim 48, wherein: The internal combustion engine can be operated intermittently as needed by sparking.

50. The method of claim 49, wherein: The expansion ring and / or cylinder temperature can be controlled by means of sparking.

51. The method of claim 49, wherein: According to the operating plan, after the internal combustion engine completes the i-th combustion cycle, in the subsequent i+j-th sparking cycle, the fuel injection is stopped and the exhaust gas is partially mixed with the compressed air through the multifunctional air chamber (80) and returned to the expansion chamber (43) to expand and perform work, and in the subsequent i+j+p-th sparking cycle, the fuel injection is stopped and the air compression is not stopped, and in the i+j+p+q-th sparking cycle, the fuel injection is stopped and the air compression is stopped, wherein i≥1, j, p, q≥0.

52. The method according to any one of claims 40 to 51, wherein: The rotating mechanism (100) is an internal combustion engine, an expander, a compressor, or a pump.

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