CN102140958A - Four-rotor piston engine - Google Patents

Abstract

The invention discloses a four-rotor piston engine, which includes a power shaft, a counter-rotating power shaft and two power cylinder assemblies, and each power cylinder assembly includes an outer end cover, a cylinder body, an inner end cover, rotor II and rotor I, the cylinder block, the outer end cover and the inner end cover are combined to form the cylinder body, and the rotor II and the rotor I are installed in the cylinder body in a staggered shape and rotate in the cylinder body; it also includes a reverse synchronous assembly and two In the differential drive assembly, the one differential drive assembly is connected to a power cylinder assembly to form a set of dual-rotor piston power units, and the reverse synchronous assembly is arranged between the two sets of dual-rotor piston power units. The power shaft of the present invention can do more work per revolution, and eliminates the inherent torsional inertial force caused by the non-uniform rotation of the rotor, so it has the advantages of simple structure, stable transmission, and high mechanical efficiency.

Description

A four-rotor piston engine

technical field

The invention mainly relates to the field of engines, in particular to a four-rotor piston engine applicable to piston internal combustion engines, external combustion engines and other fields.

Background technique

Piston engines mainly include reciprocating piston engines and rotary piston engines. A crank linkage is used for power transmission on most reciprocating piston engines. For more than 100 years, researchers have carried out extensive research on the crank connecting rod mechanism, and at the same time, they are committed to reducing the inertial load and side pressure, overcoming the dead point of motion, and improving the transmission efficiency of the engine by adding some auxiliary mechanisms. Although these studies have improved the power performance of the reciprocating piston engine to a certain extent, they have not fundamentally changed the status quo of the low power density of the engine due to the inherent defects of the power transmission part. The successful development and application of the rotary piston engine is the triangular rotor rotary piston engine invented by German Wankel in 1957. This engine has relatively high power density and promising application prospects, but the manufacturing cost is high due to the complicated shape of the rotor. , and there are difficult problems such as difficult sealing, poor power performance at low speed, poor fuel economy, etc., so that the theoretical superiority of the rotary piston engine has not been fully utilized so far.

The lower power density not only restricts the further improvement of the performance of the piston engine, but also limits the application of the piston engine in many occasions. The above two types of piston engines are limited by the inherent defects of the power transmission part, and the power density is difficult to reach 1 (Kw/Kg). The low power density of power sources has become a bottleneck in the development of some equipment technologies.

In order to improve the characteristics of traditional piston engines, various solutions have been proposed, among which the dual-rotor piston engine is a very popular research direction. Over the years, a large number of researches have been carried out at home and abroad. A breakthrough has been made, but the following three problems are difficult to solve in the existing double-rotor piston engine research.

First, the differential drive assembly constraining the rotor motion is complex. In the literature that has been found, some people use difficult-to-machine parts such as oval gears, transmission gears, non-circular gears, and oval gears to realize differential drive rotors. These solutions are not only high in cost, but also poor in reliability, especially for When the high power density of the engine is required to perform more work per revolution of the power shaft, the shape of these special parts will become very complicated and the processing will be too difficult; others use unconventional parts such as one-way devices, ratchets, and springs. To achieve differential drive rotors, as we all know, these components do not have practical value when used as parts for engine power transmission, and there will be great impact when the rotor rotates at a non-uniform speed, and the running noise is very loud; some people also use gears, Conventional components such as connecting rods drive the rotor at a differential speed, but the mechanism scheme is either too complex, not compact, and difficult to implement, or there are few adjustable parameters, making it difficult to generate a differential speed law that meets the thermodynamic requirements of the engine.

Secondly, it is difficult to realize that the power shaft of the engine can perform work more than 10 times per revolution, which cannot guarantee the high power density of the engine.

Thirdly, all the research at home and abroad did not consider the problem of eliminating the torsional inertial force caused by the non-uniform rotation of the rotor. When the rotor speed is high, this inertial force will bring a greater impact to the engine as a whole, especially the power shaft bearing, so a solution is urgently needed.

Contents of the invention

The technical problem to be solved by the present invention is: aiming at the technical problems existing in the prior art, the present invention provides a simple structure, stable transmission, reliable operation, which can easily ensure that the number of work done by the power shaft of the engine per revolution is within 10 times. The above, and can eliminate the four-rotor piston engine of the inherent torsional inertia force caused by the non-uniform rotation of the rotor.

In order to solve the problems of the technologies described above, the present invention adopts the following technical solutions:

A four-rotor piston engine, comprising a power shaft, a counter-rotating power shaft, and two power cylinder assemblies, each of which includes an outer end cover, a cylinder block, an inner end cover, and rotor II and rotor I, said The cylinder body, the outer end cover and the inner end cover are combined to form the cylinder body. The rotor II and the rotor I are installed in the cylinder body in a staggered shape and rotate in the cylinder body. It is characterized in that it also includes a reverse synchronous assembly and two In the differential drive assembly, the one differential drive assembly is connected to a power cylinder assembly to form a set of dual-rotor piston power units, and the reverse synchronous assembly is arranged between the two sets of dual-rotor piston power units.

As a further improvement of the present invention:

The differential drive assembly includes a ring gear housing, a first crankshaft planetary gear, a second crankshaft planetary gear, a first differential rocker I and a first differential rocker II, and the first differential rocker II and The rotor II is fixedly connected, the first differential rocker I is fixedly connected to the rotor I, and the first crankshaft planetary gear and the second crankshaft planetary gear are meshed with the ring gear housing through the first bracket and can surround the ring gear housing Planetary revolving motion; a first connecting rod is set between the first crankshaft planetary gear and the first differential rocker I, and a second connecting rod is set between the second crankshaft planetary wheel and the first differential rocker II link.

The first bracket is fixedly connected to the power shaft, and the second bracket is fixedly connected to the reverse power shaft.

The first differential rocker II and the rotor II are connected by a key, and the first differential rocker I and the rotor I are connected by a spline shaft and a key.

The cylinder block, the ring gear housing and the inner end cover are fixedly connected in sequence, and seals are provided between the cylinder block and the inner end cover, and between the ring gear housing and the inner end cover.

The reverse synchronization assembly includes a bevel gear frame, a bevel gear, a first bevel gear disc, a second bevel gear disc and a bevel gear shaft, the bevel gear shaft is installed on the bevel gear frame, and the bevel gear is sleeved on On the bevel gear shaft, the first bevel gear disc is fixedly connected to the first differential rocker II, the second bevel gear disc is fixedly connected to the second differential rocker II, the first bevel gear disc, the second The two bevel gear discs are engaged with the bevel gears.

The differential drive assembly is connected with the ring gear housing and forms an installation cavity, and the bevel gear is mounted in the installation cavity.

The power cylinder assembly also includes a large sealing ring, a small sealing ring and a door-shaped sealing ring. The large sealing ring is arranged between the cylinder body and the outer end cover and the inner end cover. The small sealing ring is arranged between the rotor I and the In the annular groove at the root of the blade on the rotor II, the gate-shaped sealing ring is arranged in the gate-shaped groove on the side of the blade on the rotor I and rotor II.

An end cover is also provided on the outer end cover of the power cylinder assembly, and a lip-shaped sealing ring is provided between the end cover and the power shaft.

Compared with the prior art, the present invention has the advantages of:

1. The four-rotor piston engine of the present invention solves the inherent torsional inertia force problem caused by the non-uniform rotation of the rotors by setting a reverse synchronous assembly between the two power units consisting of the power cylinder assembly and the differential drive assembly;

2. The structure of the differential drive assembly of the present invention is simple and reliable, and the differential motion requirements of the rotor can be realized by conventional combination of ordinary components such as gears and connecting rods, and the power shaft of the engine of the present invention rotates once, The total number of times of doing work is 36 times. An obvious advantage brought by the high number of times of work is that, compared with other piston engines, under the same design weight, the power density and liter power are greatly improved. This advantage will have a wide application prospect;

3. The mechanism scheme of the differential drive assembly of the present invention is simple, and there are many adjustable parameters. By adjusting the gear ratio and the size parameters of the four-bar mechanism, the differential law that meets the thermodynamic requirements of the engine can be easily realized, and the number of times the engine works is the number of teeth Therefore, without significantly changing the overall size, weight and manufacturing cost of the engine, the rotor can rotate one revolution, and the number of times of work changes with the square of the gear ratio, so as to adapt to various applications;

4. The average rotational speed of the rotor of the present invention is the same as that of the power shaft of the engine, that is, every time the power shaft rotates one revolution, the rotor also completes a rotary motion, and at the same time, there are 3 working chambers in the power stroke at every moment, and the power frequency is also high Compared with other piston engines, the present invention works more stably in theory, thereby effectively reducing the wear of various mechanical parts and prolonging the service life of the engine;

5. The power output form of the present invention is various. After adopting the reverse synchronous component, the torsional inertial force generated when the single set of rotors perform differential motion can be eliminated, and the power can be combined and then output by the power shaft. The power shaft of the sleeve and the counter-rotating power shaft are respectively output to realize counter-rotating drive, and the counter-rotating output form is especially suitable for occasions that require counter-rotating propeller output, such as large transport aircraft, helicopters, and torpedoes;

6. The present invention adopts a modular design, and separates the power cylinder assembly and the differential drive assembly, which can not only protect the differential drive assembly from complex environments such as high temperature and high pressure, but also facilitate disassembly and maintenance. Conveniently combined into a multi-cylinder working form, suitable for special applications;

7. The structure of the present invention is symmetrically arranged, and the number of parts is small, the working chamber is easy to seal, and there is no complicated gas distribution mechanism.

Description of drawings

Fig. 1 is a schematic diagram of the composition of the two-dimensional structure of the present invention;

Fig. 2 is a schematic diagram of the composition of the three-dimensional structure of the present invention;

Fig. 3 is a schematic diagram of the assembly structure in the specific embodiment of the engine;

Fig. 4 is a schematic cross-sectional structure diagram at A-A in Fig. 3;

Fig. 5 is a schematic diagram of a two-dimensional structure of a power cylinder assembly in a specific embodiment;

Fig. 6 is a schematic diagram of a three-dimensional exploded structure of a power cylinder assembly in a specific embodiment;

Fig. 7 is a schematic diagram of a three-dimensional exploded structure of a differential drive assembly in a specific embodiment;

Fig. 8 is a schematic diagram of the connection mode between the rotor I and the differential rocker I in the specific embodiment;

Fig. 9 is a schematic diagram of the connection mode between the rotor II and the differential rocker II in the specific embodiment;

Fig. 10 is a three-dimensional schematic diagram of the reverse synchronization component in a specific embodiment.

illustration:

100. Power cylinder assembly; 200. Differential drive assembly; 300. Reverse synchronous assembly; 1. Power shaft; 2. Outer end cover; 3. Cylinder block; 4. Inner end cover; 5. Pin; 6. O-type Sealing ring; 7, ring gear housing; 8, breather cap; 9, paper pad; 10, key; 11, bevel gear carrier; 12, bevel gear; 13, crankshaft planetary wheel; 131, first crankshaft planetary wheel; 132 , the second crankshaft planetary wheel; 14, the connecting rod; 141, the first connecting rod; 142, the second connecting rod; 151, the first bracket; 152, the second bracket; 161, the first differential rocker I; 162, Second differential rocker Ⅰ; 171. First differential rocker II; 172. Second differential rocker II; 18. Rotor II; 19. Rotor I; 20. Key; 21. End cover; 22. Lip 23, reverse power shaft; 24, small bearing grinding pad; 25, large bearing grinding pad; 26, spline shaft; 27, key; 281, first bevel gear disc; 282, second bevel gear disc 29, bevel gear shaft; 101, large sealing ring; 102, small sealing ring; 103, door-shaped sealing ring; 301, air inlet; 302, exhaust port; 303, spark plug.

Detailed ways

The present invention will be further described in detail below in conjunction with the accompanying drawings and specific embodiments.

As shown in Figures 1 to 3, the present invention is a high power density four-rotor piston engine without inertial force, comprising a power shaft 1, a reverse power shaft 23 and two power cylinder assemblies 100, each power cylinder assembly 100 Both include outer end cover 2, cylinder block 3, inner end cover 4, rotor II18 and rotor I19, cylinder block 3, outer end cover 2 and inner end cover 4 are combined to form a cylinder block, and rotor II18 and rotor I19 are installed in a staggered shape on Inside the cylinder and rotate within the cylinder. The present invention further includes a reverse synchronous assembly 300 and two differential drive assemblies 200, a differential drive assembly 200 is connected to a power cylinder assembly 100 to form a set of dual-rotor piston power unit, and the reverse synchronous assembly 300 is located on two Set between the double-rotor piston power unit. That is, the engine as a whole is composed of the power cylinder assembly 100 , the differential drive assembly 200 , the reverse synchronous assembly 300 , the differential drive assembly 200 , and the power cylinder assembly 100 in sequence. By arranging a reverse synchronous assembly 300 between the two sets of power units, while achieving high power density output of the engine, it also solves the inherent torsional inertia force problem caused by the non-uniform rotation of the rotor. After using the reverse synchronous assembly 300, it can eliminate the torsional inertial force generated when a single group of rotors perform differential motion, and the power can be combined and then output by the power shaft, or nested power shafts and reverse power shafts can be used Output separately to realize counter-rotating drive, and the counter-rotating output form is especially suitable for occasions that require counter-rotating propeller output, such as large transport aircraft, helicopters, and torpedoes.

As shown in Fig. 5 and Fig. 6, the power cylinder assembly 100 of the four-rotor piston engine of the present invention is basically the same as the dual-rotor piston engine of the prior art, and the power cylinder assembly 100 includes a cylinder block 3, an outer end cover 2, and an inner end cover 4 And the rotor II18 and rotor I19, the cylinder block 3, the outer end cover 2 and the inner end cover 4 are combined to form the cylinder body, and the rotor II18 and the rotor I19 are installed in the cylinder body in a staggered shape (or a cross shape) and can be installed in the cylinder body Rotate in the cylindrical cavity. Among them, rotor II18 and rotor I19 are both six-blade rotors, and two six-blade rotors form 12 working chambers. Three intake ports 301 , three exhaust ports 302 and three spark plugs 303 are evenly distributed on the cylinder of the power cylinder assembly 100 . In this embodiment, the power cylinder assembly 100 also includes a large sealing ring 101, a small sealing ring 102 and a door-shaped sealing ring 103. In the installation groove, the small sealing ring 102 is arranged in the annular groove at the blade root of the rotor II 18 and the rotor I 19 . Among them, there are small sealing rings 102 between the rotor II18 and the rotor I19, between the rotor II18 and the outer end cover 2, and between the rotor I19 and the inner end cover 4, and the door-shaped sealing rings 103 are arranged on the rotor II18 and the rotor I19. The door-shaped groove on the side of the blade ensures the sealing reliability of the power cylinder assembly 100 .

Furthermore, an end cover 21 is provided on the outer end cover 2 of the power cylinder assembly 100, and a lip seal ring 22 is provided between the end cover 21 and the power shaft 1 to further ensure the reliability of the sealing of the entire engine.

Referring to Fig. 3, Fig. 4 and Fig. 7, in this embodiment, the differential drive assembly 200 includes the ring gear housing 7, the first crankshaft planetary gear 131, the second crankshaft planetary gear 132, the first connecting rod 141, the second connecting rod The rod 142 , the first bracket 151 , the first differential rocker I 161 and the first differential rocker II 171 , wherein the ring gear housing 7 is connected to the inner end cover 4 of the power cylinder assembly 100 . As shown in Figure 3, the cylinder block 3, the ring gear housing 7 and the inner end cover 4 are fixedly connected in sequence, and the cylinder block 3 and the inner end cover 4 and the ring gear housing 7 and the inner end cover 4 are provided The seal, the seal is an O-ring 6 , the power shaft 1 is fixedly connected to the first bracket 151 and can rotate with the first bracket 151 . As shown in Figure 3, Figure 8 and Figure 9, the first differential rocker II171 is provided with a boss, and the boss is provided with a keyway, and the mounting part of the rotor II18 is provided with a keyway, the first differential rocker II171 and the rotor II18 Fixedly connected by a flat key, the first differential rocker I161 is provided with a spline groove, the installation part of the rotor I19 is provided with a keyway, the first differential rocker I161 and the rotor I19 are connected by a spline shaft 26, and the spline One end of the shaft 26 has a keyway and is fixedly connected to the rotor I19 through a flat key, and the other end is provided with a spline and is fixedly connected to the first differential rocker I161 through a spline. 132 meshes with the ring gear housing 7 through the first bracket 151 and can perform planetary revolution around the ring gear housing 7. A first connecting rod is arranged between the crankshaft of the first crankshaft planetary gear 131 and the first differential rocker I161 141, the second connecting rod 142 is provided between the second crankshaft planetary gear 132 and the first differential rocker II 171, one end of the first connecting rod 141 is hingedly connected with the first differential rocker I 161, and the other end is connected with the first crankshaft The crankshaft of the planetary gear 131 is hingedly connected, one end of the second connecting rod 142 is hingedly connected to the first differential rocker II 171 , and the other end is hingedly connected to the crankshaft of the second crankshaft planetary gear 132 .

As shown in Figure 3 and Figure 10, in the present embodiment, reverse synchronous assembly 300 comprises bevel gear frame 11, bevel gear 12, first bevel gear disc 281, second bevel gear disc 282 and bevel gear shaft 29, bevel gear The frame 11 is installed in the installation cavity formed by connecting the two differential drive assemblies 200 with the ring gear housing 7 . The bevel gear shaft 29 is fixedly installed on the bevel gear frame 11 along the radial direction of the bevel gear frame 11, the bevel gear 12 is sleeved on the bevel gear shaft 29, the first bevel gear plate 281 is fixedly connected with the first differential rocker II 171, The second bevel gear plate 282 is fixedly connected with the second differential rocker II 172 . Referring to Fig. 8, in this embodiment, the first bevel gear plate 281 and the second bevel gear plate 282 are fixed to the end of the installation part of the first differential rocker II 171 and the second differential rocker II 172 by bolts close to the bevel gear 12 In terms of space utilization, the structure is more compact. Left and right two first bevel gear discs 281 and the second bevel gear disc 282 are all engaged with the bevel gear 12, as shown in FIGS. The central axis of rotation of the power shaft is the central axis of rotation, and the bevel gear 12 is the central axis of rotation on any radial line perpendicular to the central axis of rotation of the engine power shaft on the bevel gear carrier 11. In this embodiment, four bevel gears 12 are evenly distributed on the circumference of the bevel gear carrier 11, thereby ensuring that the force between the first bevel gear disc 281, the second bevel gear disc 282 and the bevel gear 12 is more uniform, The transmission is also smoother.

An engine is a complex machine (consisting of) many mechanisms and systems. In order to complete the energy conversion, realize the working cycle, and ensure the long-term continuous normal operation, some necessary mechanisms and systems must be possessed. Engine of the present invention belongs to piston engine, and basic principle is similar to other piston engines, therefore, except the power transmission part that the present invention emphatically modifies, also must configure fuel supply system, lubricating system, cooling system, starting system etc., these systems The technology can fully refer to the technology of the existing reciprocating piston or triangular rotor rotary piston engine, so it will not be repeated here. In addition, the present invention, as a kind of engine, belongs to volumetric machines, and its mechanism can also be used in the fields of pneumatic motors, compressors, pumps, etc. with slight modifications.

working principle:

When the power shaft 1 of the engine rotates at a constant speed, under the constraints of the differential drive assembly 200 with a degree of freedom of 1, the two rotors rotate at variable speeds at periodically fluctuating angular velocities, so that the volume of the working chamber between the two rotors increases periodically. Big and small. On the contrary, when the fuel explodes in the working chamber, the explosion pressure pushes the two rotors to rotate, and under the constraints of the differential drive assembly 200, the differential rotation of the rotors is transformed into the uniform rotation of the engine power shaft 1 .

The number of working chambers in one cylinder block of the engine used in the present invention is twice the gear ratio of the aforementioned ring gear housing 7 and crankshaft planetary gears (131, 132), and the number of working chambers of each working chamber during one revolution of the rotor The number of times of work is half of the gear ratio, that is, the number of times of work of the engine of the present invention is the square of the gear ratio for one rotation of the rotor. The number of times of work in this embodiment is 36 times, so continuous and high-density output power can be realized. Under the premise of ensuring the same design weight of the engine, compared with other (all) piston engines, the engine of the present invention has a large increase in power density and liter power under the same design weight. This feature has a wide range of applications In the future, the differential motion of the dual rotors is achieved by using ordinary spur gears and connecting rod mechanisms, without the need for special components with complex shapes such as oval gears and non-circular gears. The manufacturing and processing are simple, and there are no wearing parts such as cams, and can be directly The inner ring gear is processed on the cylinder body, so that the layout of the whole structure will be more compact, and it is easier to arrange lubrication, cooling and other systems. More importantly, the mechanism scheme of the differential drive assembly is simple and has many adjustable parameters. By adjusting the gear ratio and the size parameters of the four-bar mechanism, the differential law that meets the thermodynamic requirements of the engine can be easily realized, and the number of times the engine works is equal to the number of teeth. Therefore, without significantly changing the overall size, weight and manufacturing cost of the engine, the rotor can rotate one revolution, and the number of times of work changes with the gear ratio as a square, so as to adapt to various applications.

The above descriptions are only preferred implementations of the present invention, and the protection scope of the present invention is not limited to the above-mentioned embodiments, and all technical solutions under the idea of the present invention belong to the protection scope of the present invention. It should be pointed out that for those skilled in the art, improvements and modifications without departing from the principle of the present invention should also be considered as the protection scope of the present invention.

Claims (9)

1. A four-rotor piston engine comprising a power shaft (1), a reverse power shaft (23) and two power cylinder assemblies (100), each of which includes an outer end cover (2 ), cylinder block (3), inner end cover (4) and rotor II (18) and rotor I (19), the cylinder block (3), outer end cover (2) and inner end cover (4) are composed of The cylinder body, the rotor II (18) and the rotor I (19) are installed in the cylinder body in a staggered shape and rotate in the cylinder body, and it is characterized in that it also includes a reverse synchronous assembly (300) and two differential drives assembly (200), the one differential drive assembly (200) and one power cylinder assembly (100) are connected to form a set of dual-rotor piston power unit, and the reverse synchronization assembly (300) is set on two sets of dual-rotor piston between power units. 2. The four-rotor piston engine according to claim 1, characterized in that: the differential drive assembly (200) comprises a ring gear housing (7), a first crankshaft planetary gear (131), a second crankshaft planetary gear (132), the first differential rocker I (161) and the first differential rocker II (171), the first differential rocker II (171) is fixedly connected to the rotor II (18), the first A differential rocker I (161) is fixedly connected to the rotor I (19), and the first crankshaft planetary gear (131) and the second crankshaft planetary gear (132) are connected to the ring gear housing ( 7) Engage and perform planetary epicyclic motion around the ring gear housing (7); a first connecting rod (141) is provided between the first crankshaft planetary gear (131) and the first differential rocker I (161) , a second connecting rod (142) is provided between the second crankshaft planetary gear (132) and the first differential rocker II (171). 3. The four-rotor piston engine according to claim 2, characterized in that: the first bracket (151) is fixedly connected to the power shaft (1), and the second bracket (152) is connected to the reverse power shaft (23 ) fixed connection. 4. The four-rotor piston engine according to claim 2, characterized in that: the first differential rocker II (171) is connected to the rotor II (18) by a key, and the first differential rocker I (161) is connected with the rotor I (19) through a splined shaft (26) and a key. 5. The four-rotor piston engine according to claim 2, 3 or 4, characterized in that: the cylinder block (3), the ring gear housing (7) and the inner end cover (4) are fixedly connected in sequence, and the Sealing elements are provided between the cylinder block (3) and the inner end cover (4) and between the ring gear housing (7) and the inner end cover (4). 6. The four-rotor piston engine according to claim 2, 3 or 4, characterized in that: the reverse synchronous assembly (300) includes a bevel gear carrier (11), a bevel gear (12), a first bevel gear disc (281), the second bevel gear disc (282) and the bevel gear shaft (29), the bevel gear shaft (29) is installed on the bevel gear frame (11), and the bevel gear (12) is sleeved on the bevel On the gear shaft (29), the first bevel gear disc (281) is fixedly connected with the first differential rocker II (171), and the second bevel gear disc (282) is connected with the second differential rocker II ( 172) Fixed connection, the first bevel gear disc (281), the second bevel gear disc (282) and the bevel gear (12) are connected through meshing. 7. The four-rotor piston engine according to claim 6, characterized in that: the differential drive assembly (200) is connected to the ring gear housing (7) and forms an installation cavity, and the bevel gear carrier (11) Set in the installation cavity. 8. The four-rotor piston engine according to claim 1 or 2 or 3 or 4, characterized in that: the power cylinder assembly (100) also includes a large sealing ring (101), a small sealing ring (102) and a gate The sealing ring (103), the large sealing ring (101) is set between the cylinder block (3) and the outer end cover (2) and the inner end cover (4), and the small sealing ring (102) is set on the rotor I (18) and the annular groove at the root of the blade on the rotor II (19), and the door-shaped sealing ring (103) is set in the door-shaped groove on the side of the blade on the rotor I (18) and rotor II (19). 9. The four-rotor piston engine according to claim 1 or 2 or 3 or 4, characterized in that: the outer end cover (2) of the power cylinder assembly (100) is also provided with an end cover (21), so A lip seal (22) is provided between the end cover (21) and the power shaft (1).

Images