CN114856803B

CN114856803B - Alternate relay type double-piston disc annular multi-cylinder crankless internal combustion engine

Info

Publication number: CN114856803B
Application number: CN202210374077.XA
Authority: CN
Inventors: 黄华
Original assignee: Individual
Current assignee: Individual
Priority date: 2022-04-11
Filing date: 2022-04-11
Publication date: 2023-07-14
Anticipated expiration: 2042-04-11
Also published as: CN114856803A

Abstract

The invention discloses a relay type double-piston disc annular multi-cylinder crankless internal combustion engine, which comprises two shells which are in mirror image relationship with each other and serve as cylinders, two piston discs which are mirror images with a plurality of piston blades are used as pistons, the two piston discs alternately do circular motion in the cylinders along the same circumferential direction all the time, the two piston discs are respectively connected with a flywheel through an output shaft, the two flywheels drive a flywheel box, and intermittent circular mechanical motions of the two piston discs are integrated and directly output to do work. The invention does not need heavy design such as a crank case and the like, directly outputs the rotary mechanical energy, effectively reduces the whole weight of the internal combustion engine and reduces the volume of the internal combustion engine; the waste gas generated by doing work is completely separated from the fuel newly entering the cylinder, so that the fuel combustion efficiency is not affected, and the work efficiency of the internal combustion engine can be improved; the oxyhydrogen binary fuel can be directly used.

Description

Alternate relay type double-piston disc annular multi-cylinder crankless internal combustion engine

Technical Field

The invention relates to the field of internal combustion engines, in particular to a rotation relay type double-piston disc annular multi-cylinder crankless internal combustion engine.

Background

An internal combustion engine, which is a power machine, is a heat engine that directly converts heat energy emitted from fuel burned in the machine into power; of these, reciprocating piston internal combustion engines are most common. The working principle of the piston type internal combustion engine is that fuel and air are mixed and combusted in a cylinder, and the released heat energy enables the cylinder to generate high-temperature and high-pressure fuel gas; the gas expands to push the piston to apply work, and then the crank-link mechanism or other mechanisms output mechanical work to drive the driven machinery to work.

The internal combustion engine is required to be subjected to four processes of air suction, compression, acting and exhaust after completing one working cycle, and the traditional internal combustion engine is mainly divided into a two-stroke internal combustion engine and a four-stroke internal combustion engine: four strokes are needed for the four-stroke internal combustion engine to complete one working cycle, the crankshaft needs to rotate for two weeks, the four strokes are independent, only one does work, the work efficiency is low, and the energy conversion rate is limited. The two-stroke internal combustion engine only needs two strokes for completing one working cycle, and the crankshaft rotates for one circle; therefore, when the rotation speed of the crankshaft is the same, the number of times of work done by the two-stroke internal combustion engine in unit time is twice that of the four-stroke internal combustion engine, and theoretically, the power of the two-stroke internal combustion engine is twice that of the four-stroke internal combustion engine; however, the four processes of air suction, compression, acting and exhaust of the two-stroke internal combustion engine are crossed, and the waste gas generated after acting can be mixed with the fuel newly entering the cylinder, so that the fuel combustion efficiency is seriously affected.

In the traditional internal combustion engine working process, the piston makes reciprocating rectilinear motion in the cylinder, devices such as a crank case and the like are needed to convert the reciprocating rectilinear motion of the piston into rotary motion of the output shaft, so that the machine is complex in structure and heavy in weight, energy is lost in motion conversion, and repair, maintenance and maintenance costs are high in the use process.

Disclosure of Invention

In order to solve the defects and shortcomings of the technical problems, the annular multi-cylinder crankless internal combustion engine with the alternate relay type double piston discs adopts two piston discs which are mirror images and provided with a plurality of piston blades as pistons, the two piston discs alternately do circular motion along the same circumferential direction all the time, the piston discs are respectively fixed on respective output shafts, the output shafts are directly connected with a flywheel, and the intermittent circular mechanical motion of the two pistons can be directly output to do work without precise crankshaft balance; the invention has no fuel compression process, integrates the air inlet, acting and exhaust processes in the traditional internal combustion engine, and has higher acting efficiency and smaller energy loss.

The utility model provides a relay formula double piston dish annular multicylinder does not have bent axle internal-combustion engine, includes cylinder, two piston dishes, output shaft, the cylinder includes the shell that two symmetries set up, the piston dish can rotate around the cylinder axis, every piston dish lateral wall evenly distributed at least one piston leaf, the piston leaf is fan-shaped, terminal surface and lateral surface closely laminate with the cylinder, piston dish, piston leaf divide into a plurality of cavitys with the cylinder, exhaust hole and inlet port have evenly been seted up along circumference to at least one side shell terminal surface, and the quantity of exhaust hole, inlet port is unanimous with the piston leaf quantity on the piston dish, the thickness of piston leaf is less than the distance between adjacent exhaust hole and the inlet port, and the terminal surface can fully shelter from exhaust hole or inlet port, two piston dishes are connected with the output shaft respectively, and the output shaft passes the cylinder terminal surface, with cylinder swing joint.

Further, the center of the inner side of the shell is provided with a control ring, the periphery of the control ring is provided with a check valve stress layer and a check valve stress layer in a layering manner, the check valve stress layer is uniformly provided with check valves along the circumferential direction, the check valve stress layer is uniformly provided with check valves and a controller along the circumferential direction, one end of the controller is in sliding connection with the check valves, the other end of the controller points to the center of the control ring, and the controller can only do reciprocating motion along the radial direction of the control disc; the check valve and the check valve are connected with the control ring shaft, the check valve and the check valve can rotate around the shaft, and a spring piece is arranged at the shaft connection part of the check valve, so that the check valve is always in the centrifugal movement trend; the number of the check valves, the check valves and the controllers is consistent with that of the piston blades on the piston disc, and the check valves, the check valves and the controllers are uniformly distributed around the axis of the control ring;

further, a track cavity is formed in one side, close to the shell, of the piston disc, a track disc is arranged in the center of the track cavity, and the track disc is formed by sequentially superposing a first lower track disc, a second lower track disc, a middle disc, a second upper track disc and a first upper track disc;

the top of the first lower track disc and the bottom of the first upper track disc are provided with first track channels which are vertically symmetrical and have gaps; the side surfaces of the second lower track disc and the second upper track disc are provided with second track channels which are vertically symmetrical;

The first track corresponds to the second track in position and has a gap, the second track is a continuous track from a low-order position to a high-order position, the first track is a medium-order track, and the distance from any position on the medium-order position to the center of the track disc is unchanged; the number of the first track ways and the second track ways is consistent with the number of the piston blades on the piston disc, and the first track ways and the second track ways are uniformly distributed around the axis of the track disc.

Further, the inner side wall of the track cavity is provided with a backstop track and a backstop track in a layering manner, the number of the backstop tracks and the backstop tracks is consistent with that of the piston blades on the piston disc, the backstop tracks are respectively and uniformly distributed around the axis of the piston disc, the backstop tracks are provided with backstop protrusions, the backstop protrusions and the backstop protrusions are opposite in direction, the backstop tracks and the backstop tracks correspond to a backstop valve stress layer and a backstop valve stress layer on the control ring respectively, the backstop tracks are the action tracks of the backstop valves, the action anchor points of the backstop valves are the backstop protrusions, the action tracks of the backstop valves are the action anchor points of the backstop valves, and the backstop protrusions are the action anchor points of the backstop valves.

Furthermore, the backstop track is an arc-shaped step which gradually rises in the centripetal direction of the inner side wall of the track cavity, and is suddenly interrupted at the tail point of the track.

Further, the controller comprises a core part and a shell part, wherein the core part is provided with a core part anchor rod, the core part anchor rod is in contact with a track way of a track disc, the shell part is provided with a shell part anchor rod, the shell part anchor rod is connected with a stop valve in a sliding manner, the core part anchor rod is sleeved with the shell part anchor rod, the core part anchor rod and the shell part anchor rod are provided with a first spring, the shell part is connected with a stress layer of the stop valve through a second spring, and the core part anchor rod and the shell part anchor rod are both T-shaped anchor rods.

Further, at any moment, the first spring and the second spring are always in a compressed state, and the elastic force of the first spring is always larger than that of the second spring, so that the core anchor rod and the shell part always have a centripetal movement trend.

Further, the air mixing valve is arranged at the air inlet and comprises two air inlets, a spark plug and an air mixing chamber, the outer ends of the air inlets are provided with electric control air inlet valves, the inner ends of the air inlets are connected with the air mixing chamber through pressure valves, and the ignition ends of the spark plug are positioned in the air mixing chamber.

Further, the outside of the cylinder is provided with an electronic inductor near the exhaust hole, the electronic inductor is in signal connection with the electric control air inlet valve, when the electronic inductor senses that a piston blade passes through the exhaust hole, the electric control air inlet valve is closed, and if the piston blade does not sense, the electric control air inlet valve is opened.

Further, the output shaft comprises a first output shaft and a second output shaft which are coaxially connected, the first output shaft and the second output shaft move independently, the first output shaft is connected with a piston disc on one side and penetrates through the end face of the shell on the same side to be fixedly connected with a flywheel, and the second output shaft is connected with the piston disc on the other side and penetrates through the end face of the shell on the same side to be fixedly connected with another flywheel.

The invention has the beneficial effects that:

1. the internal combustion engine directly uses oxyhydrogen as fuel, has wide energy source and zero pollution, and completely meets the environmental protection requirement;

2. the internal combustion engine adopts the oxyhydrogen binary fuel as direct fuel, so that no residue exists on the cylinder wall, the piston blade and the like, and the cylinder and the piston blade are more durable;

3. the internal combustion engine has simple working cycle, and reduces the energy consumption of the mechanical structure in the working process;

4. the internal combustion engine has simple mechanical structure, does not have devices such as a crankshaft, an air pressurizing filter, a carburetor and the like, effectively reduces the overall weight of the internal combustion engine, reduces the volume of the internal combustion engine and improves the repair and maintenance convenience;

5. in the aspect of work output, compared with a traditional four-stroke internal combustion engine, the internal combustion engine based on the design scheme of the invention has the advantages that only 1/4 of time is needed to work in each piston work cycle (the rest time is the air inlet, compression and exhaust processes), and the work time of the internal combustion engine in the scheme of the invention is about 2/3 of the work cycle, and only about 1/3 of the alternation force is the non-work energy consumption stage; in addition, compared with the ratio of the number of times of work done per unit time to the rotation speed of a crankshaft of the traditional four-stroke internal combustion engine, if the number of cylinders of the internal combustion engine is n, the flywheel box rotates for 1/n rotation every time, and the internal combustion engine can provide larger output torque;

6. Compared with the traditional two-stroke internal combustion engine, the internal combustion engine has the advantages that the exhaust gas generated by acting is completely separated from the fuel newly entering the cylinder, the fuel combustion efficiency is not affected, and the efficiency of converting the internal energy into mechanical energy is improved;

7. the internal combustion engine has wider application range, does not need oxygen in the air to support combustion because of using oxyhydrogen fuel, can be used in a closed space or an air-free area, and does not worry about the discharge of toxic waste gas.

Drawings

In order to more clearly illustrate the technical solutions of the embodiments of the present application, the drawings that are needed in the embodiments will be briefly described below, it being understood that the following drawings only illustrate some embodiments of the present application and therefore should not be considered limiting the scope, and that other related drawings may be obtained according to these drawings without inventive effort for a person skilled in the art.

FIG. 1 is an exploded view of the overall structure of the present invention;

FIG. 2 is an exploded view of the housing structure;

FIG. 3 is a schematic diagram of the structure of a piston disc;

FIG. 4 is a schematic diagram of the layered structure of a track pad;

FIG. 5 is an exploded schematic view of a controller structure;

FIG. 6 is a schematic diagram of the assembly relationship of a control ring;

FIG. 7 is a schematic cross-sectional view of a gas mixing valve;

fig. 8 is a schematic diagram showing the change of the relationship between the positions of the check valve, the check valve and the controller of the piston disc B and the piston blades of the piston disc B and the piston disc a in the state a 1;

fig. 9 is a schematic diagram showing the change of the relationship between the positions of the check valve, the check valve and the controller of the piston disc B and the piston blades of the piston disc B and the piston disc a in the state a 2;

fig. 10 is a schematic diagram showing the change of the relationship between the positions of the check valve, the check valve and the controller of the piston disc B and the piston vanes of the piston disc B and the piston disc a in the state a 3;

fig. 11 is a schematic diagram showing the change of the relationship between the check valve, and the position of the controller of the piston disc B and the piston vanes of the piston disc B and the piston disc a in the state a 4;

fig. 12 is a schematic diagram showing the change of the relationship between the positions of the check valve, and the controller of the piston disc B and the piston blades of the piston disc B and the piston disc a in the state a 5;

fig. 13 is a schematic diagram showing the change of the relationship between the check valve, and the position of the controller of the piston disc B and the piston vanes of the piston disc B and the piston disc a in the state a 6;

in the figure: the device comprises a shell, a 2-check valve stress layer, a 3-piston disc, a 4-check valve stress layer, a 5-piston blade, a 6-exhaust hole, a 7-air inlet hole, an 8-check track, a 9-check track, a 10-check valve, an 11-check valve, a 12-controller, a 13-track disc, a 14-first lower track disc, a 15-second lower track disc, a 16-middle disc, a 17-second upper track disc, a 18-first upper track disc, a 19-first track way, a 20-second track way, a 21-check protrusion, a 22-check protrusion, a 23-core part, a 24-shell part, a 25-core part, a 26-shell part anchor rod, a 27-first spring, a 28-second spring, a 29-air mixing valve, a 30-air inlet channel, a 31-spark plug, a 32-air mixing chamber, a 33-pressure valve, a 34-first output shaft and a 35-second output shaft.

Detailed Description

For the purposes of making the objects, technical solutions and advantages of the embodiments of the present application more clear, the technical solutions of the embodiments of the present application will be clearly and completely described below with reference to the drawings in the embodiments of the present application, and it is apparent that the described embodiments are some embodiments of the present application, but not all embodiments. The components of the embodiments of the present application, which are generally described and illustrated in the figures herein, may be arranged and designed in a wide variety of different configurations.

In the description of the embodiments of the present application, it should be noted that, the indicated orientation or positional relationship is based on the orientation or positional relationship shown in the drawings, or the orientation or positional relationship that is conventionally put when the product of the application is used, or the orientation or positional relationship that is conventionally understood by those skilled in the art, or the orientation or positional relationship that is conventionally put when the product of the application is used, which is merely for convenience of describing the application and simplifying the description, and is not indicative or implying that the device or element to be referred to must have a specific orientation, be configured and operated in a specific orientation, and therefore should not be construed as limiting the application. Furthermore, the terms "first," "second," "third," and the like are used merely to distinguish between descriptions and should not be construed as indicating or implying relative importance.

In the description of the embodiments of the present application, it should also be noted that, unless explicitly specified and limited otherwise, the terms "disposed," "mounted," and "connected" are to be construed broadly, and may be, for example, fixedly connected, detachably connected, or integrally connected; may be directly connected or indirectly connected through an intermediate medium. The specific meaning of the terms in this application will be understood by those of ordinary skill in the art in a specific context.

As shown in the figure, the alternate relay type double-piston disc annular multi-cylinder crankless internal combustion engine provided by the invention comprises a cylinder, two piston discs 3 and an output shaft.

The cylinder comprises two symmetrically arranged shells 1, and the two shells 1 are connected to form a cylindrical cylinder. A control ring is arranged in the center of the inner side of the shell 1, a check valve stress layer 2 and a check valve stress layer 4 are layered on the outer periphery of the control ring, check valves 10 are uniformly arranged on the check valve stress layer 2 along the circumferential direction, check valves 11 and a controller 12 are uniformly arranged on the check valve stress layer 4 along the circumferential direction, one end of the controller 12 is slidably connected with the check valves 11, the other end of the controller 12 points to the center of the control ring, the controller 12 can only make reciprocating motion along the radial direction of the control ring, and the number of the check valves 10, the check valves 11 and the controller 12 is consistent with the number of the piston leaves 5 on a single piston disc 3 and are uniformly distributed around the axis of the control ring; the check valve 10 and the check valve 11 are connected with the control ring through a shaft, the check valve 10 and the check valve 11 can rotate around the shaft, and a spring piece is arranged at the shaft connection part of the check valve 10, so that the check valve 10 is always in the centrifugal movement trend.

The two piston discs 3 are coaxially and oppositely arranged in the cylinder, and the piston discs 3 and the shell 1 are tightly attached. The piston discs 3 are rotatable about the cylinder axis, and each piston disc 3 is provided with at least one piston vane 5 uniformly on its side wall. The piston blade 5 is fan-shaped, the end face and the outer side face are closely attached to the cylinder, and the piston disc 3 and the piston blade 5 divide the cylinder into a plurality of cavities.

A track cavity is formed in one side, close to the shell 1, of the piston disc 3, a track disc 13 is arranged in the center of the track cavity, and the track disc 13 is formed by sequentially superposing a first lower track disc 14, a second lower track disc 15, a middle disc 16, a second upper track disc 17 and a first upper track disc 18;

the top of the first lower track disc 14 and the bottom of the first upper track disc 18 are provided with first track channels 19 which are symmetrical up and down and have gaps; the side surfaces of the second lower track disc 15 and the second upper track disc 17 are provided with second track channels 20 which are vertically symmetrical;

the first track 19 corresponds to the second track 20 in position and has a gap, the second track 20 is a continuous track from a low-order position to a high-order position, the first track 19 is a medium-order track, and the distance from any position on the medium-order position to the center of the track disc 13 is unchanged; the number of the first track way 19 and the second track way 20 is identical to the number of the piston leaves 5 of the single piston disc 3, and the first track way and the second track way are respectively uniformly distributed around the axis of the track disc.

The inner side wall of the track cavity is provided with a retaining track 8 and a retaining track 9 in a layered mode, the number of the retaining track 8 and the retaining track 9 is identical to that of the piston blades 5 on the single piston disc 3, the retaining track 8 is provided with retaining protrusions 21 which are uniformly distributed around the axis of the shell 1, the retaining track 9 is provided with retaining protrusions 22, the retaining protrusions 21 and the retaining protrusions 22 are opposite in direction, the retaining track 8 and the retaining track 9 correspond to the retaining valve stress layer 2 and the retaining valve stress layer 4 on the control ring respectively, the retaining track 8 is the action track of the retaining valve 10, the retaining protrusions 21 are the action anchor point of the retaining valve 10, the retaining track 9 is the action track of the retaining valve 11, and the retaining protrusions 22 are the action anchor point of the retaining valve 11.

The backstop track 8 is an arc-shaped step which gradually rises in the centripetal direction of the inner side wall of the track cavity, and is suddenly interrupted at the tail point of the track. The check valve 10 can be gradually lifted along the check track 8, and can be suddenly reset at the tail point of the track, and the check protrusion 21 can prop against the check valve 10 to prevent the piston disc 3 from backing. The stop valve 11 moves along the stop trajectory 9 and the stop protrusion 22 blocks the forward trend of the piston disc 3.

The controller comprises a core 23 and a shell 24, wherein the core 23 is provided with a core anchor rod 25, the core anchor rod 25 is in contact with a track way of the track disc 13, the shell 24 is provided with a shell anchor rod 26, the shell anchor rod 26 is in sliding connection with the check valve 11, the state of the check valve 11 is directly influenced by the position change of the shell 24, the core anchor rod 25 is sleeved with the shell anchor rod 26, the core anchor rod 25 and the shell anchor rod 26 are provided with a first spring 27, and the shell 24 and the check valve stress layer 4 are connected through a second spring 28. Neither the core anchor 25 nor the shell anchor 26 are T-shaped anchors.

The first spring 27 and the second spring 28 are always in a compressed state at any time, and the elastic force of the first spring 27 is always larger than that of the second spring 28, so that the core anchor rod 25 and the shell 23 always have a centripetal movement trend. The T-bar of the core anchor 25 moves along the tracks and the T-bar can pass through the gap between the first tracks 19.

Under the combined action of the first spring 27 and the second spring 28, the core anchor rod 25 is always pressed on the track disc 13 to slide, and the track disc 13 moves in the radial direction through the track step adjusting controllers 12 with different heights of middle, low and high, so as to indirectly control the state of the check valve 11. The stop valve 10 and the stop valve 11 are set to be in a centrifugal direction to be in a closed state and in a centrifugal direction to be in an open state. The stop valve 10 always has a tendency of closing under the action of a spring piece, the stop valve 10 slides and lifts on the stop track 8 to increase the elastic potential energy of the spring piece, and the stop valve can quickly reset to a closing state after being separated from the stop track 8 and enter the lowest point of the next stop track 8, so that the piston disc 3 always keeps circular motion in the working direction.

When the core anchor 25 slides gradually from the low-order position to the high-order position on the second track 20, the first spring 27 and the second spring 28 of the controller 12 are gradually compressed, and the controller 12 makes centrifugal movement, so that the stop valve 11 linked with the shell anchor 26 gradually approaches the stop track 9.

The end face of the shell 1 on at least one side is uniformly provided with an exhaust hole 6 and an air inlet hole 7 along the circumferential direction, the number of the exhaust holes 6 and the air inlet holes 7 on one side is consistent with that of the piston blades 5 of the single piston disc 3, and the exhaust holes 6 and the air inlet holes 7 are uniformly distributed around the axis of the shell 1. Since the end surfaces of the piston blades 5 of the piston disc 3 are completely fitted to both side planes of the cylinder and the exhaust holes 6 can be completely shielded, one-side intake and exhaust or two-side intake and exhaust can be performed. The thickness of the piston blade 5 is smaller than the distance between the adjacent exhaust hole 6 and the air inlet hole 7, the two piston discs are respectively connected with an output shaft, and the output shaft penetrates through the end face of the air cylinder and is movably connected with the air cylinder.

The output shaft comprises a first output shaft 34 and a second output shaft 35 which are coaxially connected, the first output shaft 34 and the second output shaft 35 move independently of each other, the first output shaft 34 is fixedly connected with one side of the piston disc 3 and penetrates through the end face of the same side shell 1 to be fixedly connected with one flywheel, and the second output shaft 35 is fixedly connected with the other side of the piston disc 3 and penetrates through the end face of the same side shell 1 to be fixedly connected with the other flywheel. The two flywheels are connected with the same flywheel box, and the two flywheels drive one flywheel box to rotate to do work.

The air mixing valve 29 is arranged at the air inlet 7, the air mixing valve 29 comprises two air inlets 30, a spark plug 31 and an air mixing chamber 32, the outer ends of the air inlets 30 are provided with electric control air inlet valves, the inner ends of the air inlets are connected with the air mixing chamber 32 through pressure valves 33, and the ignition ends of the spark plug 31 are positioned in the air mixing chamber 32. The ignition time of the spark plug 31 is synchronous with the switch of the electric control air inlet valve, if the ignition time is close to the ignition time, more fuel enters the cylinder, and the output power is increased; if the ignition is advanced, on the contrary, less fuel enters the cylinder and the output power is lower.

And an electronic inductor is arranged at the outer side of the cylinder and close to the exhaust hole 6, and the electronic inductor is in signal connection with the electric control air inlet valve. The electric control air inlet valve is an active control air valve and is controlled by the electronic sensor to adjust the fuel input quantity. When the electronic sensor senses that the piston blade 5 passes through the exhaust hole 6, the electric control air inlet valve is closed, and if the electronic sensor does not sense that the piston blade 5 passes through the exhaust hole 6, the electric control air inlet valve is opened.

The pressure valve 33 is a passive valve, the switch state of the pressure valve is directly controlled by the air pressure at two sides of the pressure valve 33, and if the air cylinder side pressure is higher than the pipeline side, the pressure valve 33 is closed; if the cylinder side pressure is lower than the pipe side, the pressure valve 33 is opened, allowing fuel to enter the cylinder. Meanwhile, the pressure valve 33 has a protection function, when the pressure in the cylinder suddenly rises due to certain abnormal conditions (for example, fuel entering the cylinder is ignited in advance) and exceeds the air inlet side pressure of the pressure valve 33, but the electric control air inlet valve is not closed at the moment, the pressure valve 33 can be closed passively at the moment, the mixed fuel in the cylinder is prevented from flowing back into the air inlet channel 30, and meanwhile, mechanical devices are protected.

Examples

The design scheme of the invention is not limited to the specific number of the piston blades 5, and the number of the piston blades 5 can be set to be different according to different requirements, so that the number of the piston cylinders can be changed, and the description is given below by taking an alternative relay type double-piston disc annular four-cylinder crankless internal combustion engine with four piston blades 5 on a single piston disc 3 as an example, and the drawing is a schematic drawing drawn on the basis of the embodiment. The two piston discs 3 are used for doing work in a rotation manner as a working cycle, and the working cycle is divided into four processes, wherein the first process is similar to the third process, the second process is similar to the fourth process, and the working exhaust process is similar to the fourth process, so that the first process and the second process are mainly described in detail, and the third process and the fourth process are not repeated. The piston cylinder takes the clockwise direction as the working advancing direction, the travel description of the piston in the working period is recorded according to the angle travel, and the position of the piston cylinder is illustrated according to the angle. According to whether the air cylinders are closed or not, the air cylinders are divided into an open air cylinder and a closed air cylinder, and the open air cylinder and the closed air cylinder are distributed at intervals. As shown, each piston vane 5 has a top and bottom portion, the cylinder bottom of the closed cylinder is provided by the bottom surface of the stationary piston vane 5 during the work, the cylinder top is provided by the top surface of the work piston vane 5, and so on. As shown in the figure, the working advancing direction of each piston blade 5 is a bottom surface, the opposite surface is a top surface, the fan-shaped included angle of the piston blade 5 is 15 degrees, the fan-shaped included angle of the exhaust hole 6 is 5 degrees, and the center line included angle between the exhaust hole 6 and the nearest air inlet hole 7 is 40 degrees. For convenience of description, the symmetrical feature of the present invention is described as being divided into two symmetrical parts, namely, a piston disc a and a piston disc B, a housing a and a housing B, and various movable parts, such as a controller 12, a check valve 10, a check valve 11, etc., described below, all move in the corresponding piston disc 3 and housing 1.

The first process is a relay process, the angular travel of which is 0-25, and is described by six stage states of a1, a2, a3, a4, a5 and a6, and in this process, the two piston disks 3 move synchronously:

at the beginning of a new working cycle, the bottom surface of the piston blade 5 of the piston disc B coincides with the edge of the exhaust hole 6, the top surface is 5 degrees away from the tail end edge of the exhaust hole 6, as shown in a state a1 of fig. 8, the bottom surface of the piston blade 5 of the piston disc B just contacts the top surface of the piston blade 5 of the piston disc a, the volume of an open cylinder is 0 at the moment, the closed cylinder reaches the maximum volume, the high-pressure gas in the cylinder after the last working combustion can not release pressure by pushing the piston disc B, the momentum of the piston disc B in the forward motion can not be completely transferred to the piston disc a to enable the piston disc B to be stationary, and the two piston discs 3 can only be driven to advance together under the kinetic energy obtained by the piston disc B at the moment. At this moment, the electronic sensor at the exhaust hole 6 actively closes the electrically controlled air inlet valve due to sensing the piston blade 5, and meanwhile, the cylinder side pressure of the pressure valve 33 is still larger than the pipeline side pressure, so that the electronic sensor is passively closed.

The angular travel is between 0 and 5 degrees: at this time, the exhaust hole 6 is always completely blocked by the piston vane 5, the high-pressure gas in the closed cylinder still does not escape, the in-cylinder pressure is continuously higher than the intake side pressure, the pressure valve 33 is always in a closed state, and the fuel cannot enter the cylinder. During this time the track anchor point of the core anchor 23 of the control 12 in the housing B is in the higher order position of the second track way 20 of its own track disk 13 and both springs in the control 12 are in the maximally compressed state, so that the non-return valve 11 associated with the housing anchor 26 is in the closed state. Correspondingly, the track anchor point of the core anchor rod 25 of the controller 12 in the shell a is located at the low-order position of the second track way 20 of the track disc 13 of the controller, and slides along with the rotation of the piston disc a, at this time, both springs in the controller 12 are in the minimum compression state, and the check valve 11 linked with the shell anchor rod 26 is in the open state.

When the angular travel reaches 5 °, the piston She Dingmian of the piston disc B reaches the end edge of the exhaust hole, and the closed cylinder is at the critical point of closing and opening, and fig. 9 shows a state a2. The track anchor point of the shell anchor 26 of the controller 12 in the housing B is still in the higher order position of the corresponding second track way 20, and the check valve 11 is still in the closed state. At this time, the track anchor point of the shell anchor rod 26 of the controller 12 in the shell a is located at the lower-order position of the corresponding second track 20, the check valve 11 is in an open state, the check valve 10 still slides on the check track 8, and is 15 ° away from the end point of the check track 8, and the check valve 10 is in a closed state.

During the angular travel of 5-15 degrees, the piston disc A and the piston disc B continuously and synchronously advance in a clinging manner, the closed cylinder is converted into an open cylinder, the open clearance is gradually increased along with the advance of the two piston discs 3, the high-pressure gas escape speed is increased, the in-cylinder pressure is rapidly reduced, and the advance resistance of the two piston discs 3 is reduced. During this time, the electronic sensor continues to maintain the closed state because it senses that the piston 5 does not pass through the exhaust gap, but the pressure valve 33 gradually opens as the in-cylinder pressure decreases, but as the piston plate a advances, the piston 5 of the piston plate a gradually shields the intake hole 7, so no fuel still enters the cylinder. During this time, the locus anchor point of the core anchor rod 25 of the controller 12 in the housing B continues to slide on the high-order position of the corresponding second locus path 20, the check valve 11 is in the closed state, the housing B stops the slide of the check valve 10 on the corresponding check locus 8, and the check valve 10 maintains the closed state. The track anchor point of the core anchor 25 of the controller 12 in the housing a still slides on the lower-order position of the corresponding second track way 20, and the check valve 11 remains in an open state and is passing through the check protrusion 22 of the piston disc a.

Fig. 10 shows a state a3, when two piston discs 3 advance to 15 ° synchronously, the exhaust hole 6 is completely opened, the piston blade 5 passes through the exhaust hole 6 completely, the electronic sensor does not sense the piston blade 5, the electronically controlled air inlet valve is actively opened, but at this moment the air inlet hole 7 is completely blocked by the piston blade 5 of the piston disc a, and no fuel enters the cylinder. At this point the check valve 10 of the housing B is 5 ° from the corresponding end point of the check track 8 and the core anchor 26 of the controller 12 is 5 ° from the corresponding end point of the higher order track 20. At the same time, the check valve 10 of the housing a begins to slide on the corresponding check track 8 and gradually lifts, and the track anchor point of the core anchor 26 of the controller 12 continues to slide on the second track 20 of the corresponding track disk 13.

When the piston disc a and the piston disc B continue to advance synchronously for 20 °, as shown in a state a4 of fig. 11, the track anchor point of the core anchor rod 26 of the controller 12 in the piston disc B just breaks away from the high-order end point of the second track 20, falls onto the middle-order position of the first track 19 under the action of the first spring 27, and the stop valve 11 is still in the closed state because the position state of the shell portion 24 of the controller 12 of the housing B is unchanged. The track anchor point of the core anchor rod 26 of the controller 12 in the shell a continues to slide from the low-order position to the high-order position on the second track way 20, the two springs are gradually compressed, the whole controller 12 is pushed to centrifugally move, the check valve 11 gradually tends to be in a closed state, the shell a stops the sliding and lifting of the check valve 10 on the check track 8, and the elastic potential energy of the spring piece of the check valve 10 is gradually increased. At this time, the casing B stops the back valve 10 from just separating from the back track 8, and is driven by the spring leaf of the casing B to quickly reset to the next back track 8 and tends to be in a closed state.

As shown in fig. 11, in the state a4, when the two piston discs 3 continue to advance synchronously for 25 °, the track anchor point of the core anchor rod 26 of the controller 12 in the housing B advances for 5 ° on the middle position of the first track 19, the state of the controller 12 is unchanged, and the stop valve 11 is still in the closed state, but at this moment, the stop protrusion 22 contacts the stop valve 11 to stop the advance of the piston disc B, and the stop valve 10 has reached the closed state under the urging of the spring piece. During this time, housing a ceases to slide up valve 10 and controller 12 on their respective trajectories and reserves their respective springs for elastic potential energy, and piston disc a receives kinetic energy of piston disc B, and will continue to advance, since housing a ceases to advance valve 11 has passed completely stop 22. At this moment, the contact surfaces of the two piston disks 3 reach the positions of the air inlet holes 7, the electric control air inlet valve is in an active opening state, the cylinder side pressure of the pressure valve 33 is smaller than the pipeline side pressure and is in a passive opening state, fuel starts to enter between the two piston blades 5, the temperature of the entering fuel is obviously lower than the temperature of the cylinder wall and the temperature of the piston blades 5, the fuel absorbs the temperature of the cylinder wall and the temperature of the piston blades 5 to expand, and the expanded fuel pushes the piston disk B to retreat while pushing the piston disk A to do work. A new closed cylinder is started between the two piston leaves 5 which are gradually separated, and the process ends as soon as it is now.

In the first process, the two piston discs 3 always keep fit and synchronously advance, and in the advancing process, part of kinetic energy of the piston disc B is transferred to the piston disc A, so that the impact of the piston disc B on the shell B stopping the inlet valve 11 is reduced, the stopping inlet valve 11 is protected, and meanwhile, the output power is improved through kinetic energy transfer. At the same time, the housing a stops the advance opening of the inlet valve 11, releasing the advance restriction of the piston disc a in advance. Under the cooperative control of the two sets of controllers 12, the two piston plates 3 finish work and static alternate force, and the work process is ensured to be continuous and orderly.

The second process is a working process, and starts from the moment when fuel enters the sealed cylinder and the piston disc A starts working:

the second process comprises two working parts, expansion working and combustion working, and the two parts are bounded by ignition of the spark plug 31. In the early stage, expansion work is done, low-temperature fuel rapidly enters the cylinder through the open electric control air inlet valve and the pressure valve 33, and heat energy left by work done on the cylinder wall and the piston blade 5 is rapidly absorbed while the fuel quantity is increased, so that the pressure in the closed cylinder is rapidly expanded and increased. The expanded fuel pushes the piston disc A to do work while pushing the piston disc B to retreat, when the top surface of the piston disc B retreats to 20 degrees, the track anchor point of the core anchor rod 26 of the controller 12 in the shell B is separated from the middle level corresponding to the first track way 19, the expanded fuel falls onto the lower level of the second track way 20 under the action of the second spring 28, and the check valve 11 linked with the controller 12 is in an open state at the moment, so that the check valve 11 can be smoothly passed through by the check protrusion 22 after the third process is started, and the piston disc B can keep advancing. When the housing B stops moving back the valve 10 to the next stopping track 8, and is not contacted with the stopping protrusion 21, the piston disc B continues moving back by 5 degrees, when the piston disc B moves back to 15 degrees, the housing B stops moving back the valve 10 to the stopping protrusion 21, the piston disc B stops moving back to be kept static under the common constraint of the stopping valve 10 and the pressure in the sealed cylinder, the top surface of the piston blade 5 of the piston disc B is overlapped with the starting edge of the exhaust hole 6, and the static state of the piston disc B is kept to the end of the second process.

In the second process, the piston disc A continues to advance under the action of the expansion work of the fuel, the controller 12 in the shell A continues to slide and lift on the second track 20 and gradually closes the check valve 11, the check valve 10 slides and lifts on the check rail 8 of the piston disc A and stores the elastic potential energy of a spring leaf, and the sliding of the controller 12 and the check valve 10 maintains the second whole process. When the ignition plug 31 is ignited under control, the electronically controlled intake valve is actively closed, the fuel in the cylinder is ignited to rapidly raise the in-cylinder pressure, the in-cylinder pressure of the pressure valve 33 is significantly higher than the intake side pressure, the pressure valve 33 is passively closed, and the fuel stops entering the closed cylinder. The ignited fuel makes the in-cylinder pressure of the closed cylinder rise sharply, the piston disc B maintains a static state, the pressure can be released only by pushing the piston disc A forward, the rotating piston disc A drives the first output shaft 34 to rotate, and the flywheel box connected with the first output shaft 34 rotates to output continuous mechanical energy outwards. The piston disc A continuously advances under the pushing of the in-cylinder pressure, when the bottom surface of a piston blade 5 of the piston disc A is contacted with the top surface of a piston blade 5 of an adjacent piston disc B, the closed cylinder volume is maximum, the open cylinder volume is zero, and the process II is finished. At this point, the process returns to the first starting position, and the piston plate A and the piston plate B are replaced.

In the second process, the electronically controlled intake valve can actively control the on-off state according to the output requirement, and the pressure valve 33 passively controls the on-off state by the pressure difference between the two sides. In this process, the respective springs or spring pieces of the controller 12 and the check valve 10 in the housing a store energy continuously, and the check valve 11 linked with the controller 12 is forced to be closed gradually due to the elevation of the controller 12, so that the check valve 11 is in a completely closed state before the second process is finished, and the smooth rotation of the two piston discs 3 in the third process is ensured. After the piston disc B retreats to the rest position in the second process, the rest state is maintained all the time, and the open state of the check valve 11 and the closed state of the check valve 10 in the corresponding housing B are not changed.

As can be seen from the combination of the first and second processes, when the closed cylinder is converted into the open cylinder, the exhaust gas generated by acting starts to be discharged, and the exhaust gas is further discharged along with the advance of the piston disc a until the second process is finished, the volume of the open cylinder is zero, and the exhaust gas is exhausted. The exhaust process is not an independent process but proceeds simultaneously as the working piston disc advances. Meanwhile, the closed cylinder and the open cylinder are separated by the piston blade 5 of the acting piston disc, so that different cylinders at the positions of fuel and waste gas are not interfered with each other, and the acting efficiency is not influenced.

Since the third and fourth processes are similar to the first and second processes, respectively, the description thereof will not be repeated.

In conclusion, the invention has strong expansibility, the rotation angle of the piston 5 for doing work is designed according to the number of the piston 5 of the piston disc 3, and the specific numbers and the specific sizes of the piston 5, the exhaust hole 6, the air inlet hole 7, the track disc 13 and the like are all calculated and then are arranged, but the working principle of the internal combustion engine is the same, and the working process is the same. Each complete working cycle comprises four processes, two alternate relay processes and two working exhaust processes, the two piston discs 3 do work alternately once, the two piston discs 3 respectively complete the alternate relay of static and working in the first process and the third process, and fuel enters the cylinder twice and is ignited twice. The waste gas of the piston disc B doing work is discharged when the piston disc A does work, namely the waste gas of the piston disc A doing work is discharged when the piston disc B does work, namely the work is done twice in each period, the air is discharged twice simultaneously, the air discharge and the work are done simultaneously, and each controller completes one control cycle.

At present, most of the mainstream internal combustion engines in the field use fossil energy (gasoline, diesel oil, natural gas and the like) as fuel, the fossil energy has limited reserves and is not renewable, a large amount of greenhouse gas or even toxic gas can be generated in the combustion work process, the atmospheric environment is seriously harmed, the ecological balance is damaged, and the total reserve is limited and cannot be used as long-term energy supply for sustainable development. Environmental protection and development and the world are the main consciousness, and the oxyhydrogen energy is widely considered to be the main energy in the future, so that the requirements of environmental protection and sustainable development are completely met. Along with the continuous breakthrough of hydrogen production and storage technology, oxyhydrogen is used as a main energy source to continuously tamp the foundation.

The internal combustion engine can directly use oxyhydrogen as fuel, has wide energy source and zero pollution, and completely meets the environmental protection requirement. And because the oxyhydrogen binary fuel is adopted as direct fuel, no residue exists on the cylinder wall, the piston blade and the like, so that the cylinder and the piston blade are more durable. The application range is wider, and because oxyhydrogen fuel is used, oxygen in the air is not needed for supporting combustion, the internal combustion engine can be used in a closed space or an air-free area, and toxic waste gas is not worried about discharging.

The invention has simple working cycle and reduces the energy consumption of the mechanical structure in the working process; the mechanical structure is simple, devices such as a crankshaft, an air pressurizing filter and a carburetor are not needed, the whole weight of the internal combustion engine is effectively reduced, the volume of the internal combustion engine is reduced, and the repair and maintenance convenience is improved.

In the aspect of acting output, compared with a traditional four-stroke internal combustion engine, the internal combustion engine based on the design scheme of the invention has the advantages that each piston acting period of the traditional four-stroke internal combustion engine only has 1/4 time to act, the rest time is the air inlet, compression and exhaust processes, the acting time of the internal combustion engine of the scheme of the invention occupies about 2/3 acting period, and only has the alternation force of about 1/3 as the non-acting energy consumption stage. Compared with the traditional two-stroke internal combustion engine, the two-stroke internal combustion engine has the advantages that the waste gas generated by acting is completely separated from the fuel newly entering the cylinder, the fuel combustion efficiency is not affected, and meanwhile, the efficiency of converting the internal energy into mechanical energy is improved.

Of course, the present invention is capable of other various embodiments and its several details are capable of modification and variation in light of the present invention by one skilled in the art without departing from the spirit and scope of the invention as defined in the appended claims.

Claims

1. The utility model provides a relay formula double piston dish annular multi-cylinder does not have bent axle internal-combustion engine which characterized in that: the air cylinder comprises an air cylinder, two piston discs (3) and an output shaft, wherein the air cylinder comprises two symmetrically arranged shells (1), the piston discs (3) can rotate around the axis of the air cylinder, at least one piston blade (5) is uniformly distributed on the side wall of each piston disc (3), the end face of each piston blade (5) is fan-shaped, the end face and the outer side face of each piston blade are tightly attached to the air cylinder, and the air cylinder is divided into a plurality of cavities by the piston discs (3) and the piston blades (5); the end face of the shell (1) at least on one side is uniformly provided with an exhaust hole (6) and an air inlet hole (7) along the circumferential direction, the number of the exhaust hole (6) and the air inlet hole (7) is consistent with the number of the piston blades (5) on the piston disc (3), the thickness of each piston blade (5) is smaller than the distance between the adjacent exhaust hole (6) and the adjacent air inlet hole (7), the end face can completely shield the exhaust hole (6) or the air inlet hole (7), the two piston discs (3) are respectively connected with an output shaft, and the output shafts penetrate through the end faces of the cylinders and are movably connected with the cylinders;

The inner side center of the shell (1) is provided with a control ring, the outer periphery of the control ring is provided with a check valve stress layer (2) and a check valve stress layer (4) in a layering manner, the check valve stress layer (2) is uniformly provided with check valves (10) along the circumferential direction, the check valve stress layer (4) is uniformly provided with check valves (11) and a controller (12) along the circumferential direction, one end of the controller (12) is slidably connected with the check valves (11), the other end points to the center of the control ring, the controller (12) can only do reciprocating motion along the radial direction of the control ring, the check valve (10) and the check valve (11) are connected with the control ring through a shaft, the check valve (10) and the check valve (11) can rotate around the shaft, and a spring piece is arranged at the shaft connection part of the check valve (10) so that the check valve (10) is always in the centrifugal movement trend; the number of the non-return valves (10), the non-inlet valves (11) and the controller (12) is consistent with the number of the piston blades (5) on the piston disc (3);

a track cavity is formed in one side, close to the shell (1), of the piston disc (3), a track disc (13) is arranged in the center of the track cavity, and the track disc (13) is formed by sequentially superposing a first lower track disc (14), a second lower track disc (15), a middle disc (16), a second upper track disc (17) and a first upper track disc (18);

The top of the first lower track disc (14) and the bottom of the first upper track disc (18) are provided with first track channels (19) which are vertically symmetrical and have gaps; the side surfaces of the second lower track disc (15) and the second upper track disc (17) are provided with second track channels (20) which are vertically symmetrical;

the first track (19) corresponds to the second track (20) in position and has a gap, the second track (20) is a continuous track from a low-order position to a high-order position, the first track (19) is a medium-order track, and the distance from any position on the medium-order position to the circle center of the track disc (13) is unchanged; the number of the first track ways (19) and the second track ways (20) is consistent with the number of the piston blades (5) on the piston disc (3), and the first track ways and the second track ways are uniformly distributed around the axis of the track disc (13);

the inner side wall of the track cavity is provided with a backstop track (8) and a backstop track (9) in a layered manner, the number of the backstop tracks (8) and the backstop tracks (9) is consistent with the number of the piston blades (5) on the piston disc (3), and the backstop tracks are uniformly distributed around the axis of the piston disc (3); the anti-return track (8) is provided with an anti-return protrusion (21), the anti-return track (9) is provided with an anti-return protrusion (22), the anti-return protrusion (21) and the anti-return protrusion (22) are opposite in direction, the anti-return track (8) and the anti-return track (9) respectively correspond to the anti-return valve stress layer (2) and the anti-return valve stress layer (4) on the control ring, the anti-return track (8) is an action track of the anti-return valve (10), the anti-return protrusion (21) is an action anchor point of the anti-return valve (10), the anti-return track (9) is an action track of the anti-return valve (11), and the anti-return protrusion (22) is an action anchor point of the anti-return valve (11);

The backstop track (8) is an arc-shaped step which gradually rises in the centripetal direction of the inner side wall of the track cavity, and is suddenly interrupted at the tail point of the track.

2. The alternating relay type double-piston disc annular multi-cylinder crankless internal combustion engine according to claim 1, characterized in that: the controller (12) comprises a core (23) and a shell (24), wherein the core (23) is provided with a core anchor rod (25), the core anchor rod (25) is in contact with a track way of a track disc (13), the shell (24) is provided with a shell anchor rod (26), the shell anchor rod (26) is connected with a stop valve (11) in a sliding mode, the core anchor rod (25) is sleeved with the shell anchor rod (26), a first spring (27) is arranged between the core anchor rod (25) and the shell anchor rod (26), the core anchor rod (24) is connected with a stop valve stress layer (4) through a second spring (28), and the core anchor rod (25) and the shell anchor rod (26) are T-shaped anchor rods.

3. The alternating relay type double-piston disc annular multi-cylinder crankless internal combustion engine according to claim 2, characterized in that: the first spring (27) and the second spring (28) are always in a compressed state at any time, and the elastic force of the first spring (27) is always larger than that of the second spring (28), so that the core anchor rod (25) and the shell (24) always have a centripetal movement trend.

4. The alternating relay type double-piston disc annular multi-cylinder crankless internal combustion engine according to claim 1, characterized in that: the air mixing valve (29) is arranged at the air inlet hole (7), the air mixing valve (29) comprises two air inlet channels (30), a spark plug (31) and an air mixing chamber (32), the outer end of each air inlet channel (30) is provided with an electric control air inlet valve, the inner end of each air inlet channel is connected with the air mixing chamber (32) through a pressure valve (33), and the ignition end of each spark plug (31) is positioned in the air mixing chamber (32).

5. The alternating relay type double-piston disc annular multi-cylinder crankless internal combustion engine according to claim 4, characterized in that: the electronic inductor is arranged at the outer side of the cylinder and close to the air inlet hole (7), the electronic inductor is in signal connection with the electric control air inlet valve, when the electronic inductor senses that the piston blade (5) passes through the air outlet hole (6), the electric control air inlet valve is closed, and if the piston blade is not sensed, the electric control air inlet valve is opened.

6. The alternating relay type double-piston disc annular multi-cylinder crankless internal combustion engine according to claim 1, characterized in that: the output shaft comprises a first output shaft (34) and a second output shaft (35) which are coaxially connected, the first output shaft (34) and the second output shaft (35) move independently, the first output shaft (34) is connected with one side of the piston disc (3) and penetrates through the end face of the same side shell (1) to be fixedly connected with one flywheel, and the second output shaft (35) is connected with the other side of the piston disc (3) and penetrates through the end face of the same side shell (1) to be fixedly connected with the other flywheel.