CN108825374B - Swing arm type two-stroke straight shaft internal combustion engine - Google Patents

Abstract

The swinging arm type two-stroke straight shaft internal combustion engine has improved power by 4-6 times compared with crankshaft internal combustion engine with same volume, and its principle is that when the fuel oil is burst, the angle of crank of crankshaft internal combustion engine is 0 deg. and 45 deg. compared with that of crank of crankshaft internal combustion engine, its arm of force is lengthened, the output conversion rate of useful work done by fuel oil explosive force is up to 90%, and the rotation angle of maximum output power stage in the initial stage of fuel oil burst is increased compared with crankshaft internal combustion engine, and it is implemented by using swinging arm and side arm slide block and duckbill wheel and comma-shaped cam on the straight shaft which are alternatively connected together, and said straight shaft of internal combustion engine can be rotated by one turn to drive two V-type cylinders or three triangular type cylinders to burst once respectively, and compared with crankshaft internal combustion engine whose engine body structure and manufacturing process are greatly simplified, and its engine body weight is reduced by 4-6 times, the production cost is reduced by 4-6 times, and the method is an improved system project of the internal combustion engine.

Description

Swing arm type two-stroke straight shaft internal combustion engine

Technical Field

The invention relates to a swing arm type two-stroke straight shaft internal combustion engine, which is a device for converting the linear reciprocating motion of a piston into the circular motion of a straight shaft by using a piston connecting rod to push a swing arm and a side wall slide block to be in rotary fit with a duckbill wheel and a comma cam on the straight shaft, and is suitable for the improvement and the upgrade of crankshaft internal combustion in the prior art.

Background

The internal combustion engine in the prior art also adopts a crankshaft type internal combustion engine invented by Otto and Diesel more than a hundred years ago, and the internal combustion engine has the defects that the output efficiency is too low, the fuel oil waste is too large, and the output efficiency cannot be improved due to a circular orbit rotating mode fixed by a crank of the internal combustion engine. The main reasons for the low output efficiency of the crankshaft internal combustion engine are: at the moment of fuel explosion and in the initial operation stage, the highest pressure of the gas temperature in the cylinder is the largest, but the crank rotates at the top end of the radius of the circular track, the piston connecting rod and the crank operate on a curve with a small bending angle compared with a vertical line, and when the explosion pressure of the fuel in the cylinder is transmitted to the crank through the piston connecting rod, a very large useless component force (normal force) pointing to the circle center along the radius of the crank is generated, see N in the attached figure 1, so that the output proportion of the useful component force (tangential force) is very small, see T in the attached figure 1. The high-temperature high-pressure gas generated during fuel oil explosion can not do useful work under the resistance of useless component force of the crank and output, a large amount of high-temperature heat energy is transferred to a cooling system through the cylinder wall, a large part of high-temperature gas is discharged along with waste gas without doing work, and the fuel oil explosion generates huge explosion force instantly, and most of the high-temperature high-pressure gas is lost due to the fact that the crank rotates around the zero-degree angle to twelve-degree angle of the top dead center. The pressure in the cylinder after the explosive force disappears, a large part of the pressure generates useless component force pointing to the axle center through the connecting rod crank, the force generates friction force to do resistance work except for a small part, most of the force does not do work and increases with the rotating angle of the crank, the steep force of an inverse proportion curve is reduced when the volume of the cylinder increases, the useful component force output only accounts for a part of the useful power output, although the useful component force output proportion rapidly increases with the rotating angle of the crank, the friction force of the piston to the side wall of the cylinder is increased due to the increase of the vertical running angle of the connecting rod relative to the piston, the work output of the useful component force is still lost, and the crankshaft outputs little power outwards at the stage when the energy released at the initial stage of fuel explosion is the largest. After 76.4 degrees, because the operation angle of the connecting rod relative to the crank is less than 90 degrees, the useless component force is increased rapidly, and as can be seen from the useful component force conversion rate in the seventh row of the list of fig. 31, the output efficiency is reduced rapidly, and the useless component force of the crankshaft internal combustion engine loses the energy for doing work in the whole operation stage, so the output efficiency of the crankshaft internal combustion engine is very low.

Taking the prior art cited by the applicant as an example, a 4 horsepower diesel engine produced by a Changzhou Tiancheng diesel engine plant, the piston stroke is 60 mm, and the cylinder diameter is 70 mm. When the piston is in cylinder fuel explosion at the top dead center, the piston is descended by 10 mm from the top dead center when the crank rotates from 0 degree to 42.6 degree from the top dead center, which is one sixth distance of the piston stroke, the output of useful component (tangential force) is increased from 0 to about 81 percent of that of 42.6 degree, at this moment, the pressure in the cylinder is roughly seen from the pressure output curve 30-5 in figure 30, the pressure is descended by more than fifty percent from the highest peak, and after 76.4 degree, the output efficiency is rapidly reduced from the 7 th row in the table in figure 31.

The crankshaft internal combustion engine has low output efficiency, great fuel oil waste and serious emission pollution, is in a limited and gradually cancelled state, and has come with diversification of new energy automobile development, the Chinese development is the most fierce pure electric automobile, although the pure electric automobile has long charging time, short endurance mileage, high price and unsuitability for high-power delivery tools, and the popularization needs to build a large number of short plates such as charging stations, and the pure electric automobile is not a real clean energy source, but the crankshaft internal combustion engine has low content of vehicle manufacturing technology, and is particularly recommended to use electricity to be cheaper than the crankshaft internal combustion engine oil. Although natural gas is used as a clean energy source, the degree of emission pollution can be greatly reduced, the problems of low output efficiency and large energy waste of the natural gas used on a crankshaft type internal combustion engine are still not solved, a certain degree of air pollution still exists due to the large gas consumption, the price advantage of the natural gas is not obvious along with the rising of the price of the natural gas, and the natural gas is in a state of being cooled down because the supply of the natural gas in China is in a shortage stage at present. However, the advantages of the traditional automobile are still obvious, the only defects are that the output efficiency is too low, the fuel oil waste amount is too large, the emission pollution is serious, if the output efficiency of the internal combustion engine can be greatly improved on the basis of a crankshaft internal combustion engine, and the methanol gasoline fuel is reused, so that the energy is greatly saved, the petroleum energy pressure is relieved, and the exhaust emission is reduced to the negligible degree. For example, if a pure electric car consumes 15 kilowatts in hundred kilometers, an internal combustion engine car consumes 2 liters in hundred kilometers in oil, and the exhaust emission of 2 liters of fuel oil is far lower than the exhaust emission of coal-fired fuel oil with 15 kilowatts of electricity generation, if the engine adds more than half of methanol into the fuel oil, the gasoline consumption is reduced to negligible degree, the condition of petroleum energy shortage is thoroughly relieved, the price of consumed fuel is cheaper than the price of electricity consumed by the pure electric car, the pure electric car has no advantages, powerful support is provided for the internal combustion engine to finally use clean hydrogen fuel, and huge investment and large amount of manpower and material resources in all countries in the world are avoided to research various new energy cars.

The traditional internal combustion engine can completely improve the efficiency greatly because of the potential huge space for improving the efficiency, the acting mode of the internal combustion engine is that fuel oil explosive force is added with pressure to act, a pure electric vehicle is equivalent to fuel combustion acting, and the explosive force power of fuel is more than ten thousand times of the combustion power. The re-edition of the mathematical and chemical self-study series physics in 1977, page 324, describes a rotary piston engine which has a very high useful work output efficiency, and experimental data have shown that compared to a crankshaft engine of the same capacity, a rotary piston engine outputs 3.6 times its horsepower and one third of its fuel consumption, and although this engine is not ultimately on the market, experimental data show that it is more likely that its power is increased than a crankshaft engine.

The applicant has performed two experiments, the first one being to place a spring, which is longer than the plastic tube by a certain length, in a plastic tube, where one end of the spring is provided with a valve stem, and to stop the valve stem at one end of the plastic tube by a wood plate, and to compress the spring at the other end by a wood plate, so that the spring and the plastic tube are equal in length, see 4-1 in fig. 4, and then to release the wood plate provided with the valve stem at the end, and the valve stem is ejected by a certain distance under the thrust of the spring. Then the spring with valve stem is placed in the plastic tube, so that the part of the spring is exposed at one end of the plastic tube, then a long wood plate is used to quickly hit the part of the spring, see 4-2 in figure 4, as a result, the spring pushes the valve stem to pop out for a distance which is more than 8 times of the above pop-out distance under the hitting force of the wood plate, because the spring is limited by the length of the plastic tube, the compression amount of the spring is equal in two experiments, the pop-out distance of the valve stem in the latter experiment is far longer than that in the former experiment, firstly, because the valve stem is not subjected to any blocking force from the spring force to the pop-out, the hitting force is all used for doing work, secondly, the spring is quickly compressed by the hitting force of the long wood plate, as a result of the explosion force acting on the valve stem, the hitting force of the long wood plate is equivalent to the explosion force of the oil in the cylinder of the internal combustion engine, and the explosion expansion speed of the fuel oil of the internal combustion engine is much faster than that of the long wood plate, therefore, the piston is impacted by huge explosive force generated in the cylinder during the instant of fuel explosion, and very large kinetic energy can be given to the inertia wheel on the output shaft, so that the output efficiency of the internal combustion engine is greatly improved, and most of the explosive force is wasted due to the blocking effect of the crank angle during the instant of crankshaft internal combustion engine explosion. The above experiment leads to the conclusion that: the pressure plus the explosive force generating the pressure work is far greater than the pressure work, and the explosive force work accounts for the main part.

The second experiment, the experiment was performed on the 125 pedal motorcycle engine of the new century, the other connecting pieces on the engine were removed, only the cylinder piston connecting rod crankshaft was left, the piston ring and the oil ring on the piston were also removed, the rotating friction of the crankshaft was minimized, the magneto flywheel on the crankshaft was removed, a 5.5 kg flywheel was mounted, the piston in the cylinder was rotated to the 0 degree position of the top dead center, a wooden stick was gripped with both hands, the piston in the cylinder was briefly pushed by the force of the whole body, as a result, the piston was found to be not rotated, then the crank was sequentially placed at the clockwise, 10 °, 20 °, 30 °, 45 °, 60 ° degrees, the piston at each angle position was repeatedly pushed by the same force, respectively, as a result, the number of revolutions of the crankshaft was found to be 2, 4, 6.5, 8, 9, respectively, the selected number of revolutions was at each angle position, the number of the crank shaft rotation turns which are most probable after the piston is pushed repeatedly is reduced from 30 to 45 degrees, the crank shaft rotation turns in 45 to 60 degrees are found to be reduced compared with the number of the crank shaft rotation turns in 30 to 45 degrees, the crank shaft rotation turns clockwise after 60 degrees to increase the crank shaft angle, the piston is pushed by the same force, the number of the crank shaft rotation turns is not increased, and the crank shaft rotation turns do not increase, which also accords with the formula of the tangential force doing T of the crank internal combustion engine which is described later, namely P sin (a + beta), and the test has the conclusion that: after the fuel oil of the internal combustion engine explodes, the explosive force and the pressure are acted by small useless resistance and are several times more than the work acted by large useless resistance.

The crank of the crankshaft internal combustion engine generates useless component force, so that a large part of useful work output is wasted by huge explosive force, the useful component force output conversion rate of the crank in the explosive force stage is increased from 0 degree to 12 degrees from the top dead center by about 27 percent, and is about 13.5 percent averagely, the explosive force of the internal combustion engine in the stage is 90 percent useful work output, and later, the work of the engine in the stage is improved by about 4.1 times compared with the horsepower of the crankshaft internal combustion engine. The other main working mode of the crankshaft internal combustion engine is pressure working, namely pressure working after the 12-degree fuel explosive force after the top dead center disappears, and the pressure working output efficiency of the crankshaft internal combustion engine is also very low due to useless component force.

From explosive power acting to pressure acting, this application straight axle internal-combustion engine output efficiency compares the bent axle internal-combustion engine and has all promoted by a wide margin, still introduces this application internal-combustion engine later and compares bent axle internal-combustion engine structure simpler, the performance is more excellent. Therefore, on the basis of the traditional internal combustion engine, only a part of modification is needed, the new generation high-efficiency internal combustion engine with simple structure, excellent performance and lower manufacturing cost can be manufactured, is obviously the most excellent option in the improvement of various types of automobiles at present, and is a smart measure with one stone, more birds, one property, three actions and half effort. If we give up using the advanced high-efficiency explosion working mode for more than one hundred years, the low-efficiency working mode of pursuing equivalent combustion is not promising.

The applicant does not search similar models for comparison, and the invention is compared with a frame tooth type direct-shaft internal combustion engine, application number 201410116958.7, applied by the applicant on 12, month and 8 in 2014, and the patent is granted at present. The frame-tooth type straight shaft internal combustion engine has the advantages that when fuel in a cylinder explodes, the explosive force can reach nearly 90% to output useful work, but compared with the internal combustion engine of the application, the rotating angle of the internal combustion engine at the initial stage of fuel explosion is shortened, the force arm is not lengthened, the biggest defect of the frame-tooth type straight shaft internal combustion engine is that the rotating direction of the connecting rod pushing a gear frame to move downwards at the moment of fuel explosion is opposite to the direction of the gear frame pushing a special-shaped tooth to move upwards at the moment of fuel explosion, once the instant contact point of fuel explosion generates resistance such as friction and clamping stagnation, the influence on the output efficiency is great, particularly under the condition of high-speed rotation of the engine, once the condition occurs, the normal work of the engine can be seriously influenced, even the engine cannot operate, the precision of machine parts and the stability of the whole machine can be avoided, but the condition is always a fatal hidden trouble of the engine. This application internal-combustion engine piston connecting rod promotes the swing arm when down, and swing arm lower extreme circular arc contact point promotes duckbilled wheel downstream is with the direction, has overcome above-mentioned shortcoming, and the arm of force has carried out the extension, and the rotatory route of fuel explosion initial stage is compared the bent axle internal-combustion engine and has been increased in addition, and output efficiency has improved by a wide margin. And the frame tooth type straight shaft internal-combustion engine still rotates two weeks and explodes once, there are five intermittent points in rotatory a week, the structure is more complicated, this application model when a cooperation unit (namely a duckbilled wheel comma-shaped cam complex on the straight shaft rotates in a week and promotes one to three side arm slider formula swing arms and be a unit), there are three intermittent points in single cylinder unit model operation a week, the fuel oil explodes once a week, the inner structure has also simplified a large amount, it is more steady to operate, manufacturing cost is lower.

Disclosure of Invention

Aiming at the defects of low output efficiency and large exhaust emission pollution of a crankshaft type internal combustion engine in the prior art, the invention provides a swing arm type two-stroke straight shaft internal combustion engine. The invention part of the single-cylinder one-unit internal combustion engine is introduced firstly: a side arm sliding block type swing arm is shown as 7-5 in fig. 5 and 7, a duckbill wheel comma-shaped cam combination straight shaft with an air inlet cam and an oil supply cam is arranged on a straight shaft, 7-9 in fig. 7, a side wall exhaust hole type cylinder, 7-4 and a stabilizing spring, 7-2 and a swing piece and an air inlet valve rocker arm connected through a push rod, 8-5, 8-3 and 8-2 in fig. 8, an exhaust rocker arm and exhaust cam system and an oil injection cam, a swing block and an oil injection pump of a two-stroke oil supply system are eliminated, 8-10, 8-7 and 8-6 in fig. 8, an inertia wheel is enlarged, 7-7 in fig. 7, a case and the like. The invention of the one-unit two-cylinder and one-unit three-cylinder, two-unit four-cylinder and two-unit six-cylinder type is described later. Other parts of the internal combustion engine of the application still adopt the prior art in the crankshaft type internal combustion engine.

The technical problem solved by the invention is as follows: the combination body of the duckbilled wheel and the comma-shaped cam on the straight shaft is respectively contacted with the side arm sliding block type swing arm alternately in the rotation process, so that the straight shaft can be in stable contact operation at three intermittent points passing through in one rotation, when the piston is exploded at the top dead center, the arc vertex of the duckbilled wheel is positioned at the position of about 45 degrees at the right side of the straight shaft, see 6-5 in figure 6 and 7-6 in figure 7, the moment arm from the arc vertex of the duckbilled wheel to the axis of the straight shaft is lengthened, the useful work output of the fuel oil explosion force reaches 90 percent, compared with the useful work output of the explosion force at the top dead center of a crankshaft internal combustion engine, the crankshaft rotation angle of the 4 horsepower diesel engine is 42.6 degrees when the machine and the comparative 4 horsepower diesel engine piston descend by 10 millimeters from the top dead center, the crankshaft rotation angle of the 4 diesel engine is 43.6 degrees, and the crankshaft rotates to 63 degrees from 10 millimeters when the piston descends to 20 millimeters, the straight shaft rotates from an angle of 43.6 degrees to an angle of 74.6 degrees, so when the pistons of the two engines both descend by 20 millimeters in the initial stage of fuel explosion, the rotation angle of the straight shaft is greatly increased compared with that of the crankshaft. The pressure work power is increased by 1.39 times compared with that of a crankshaft internal combustion engine, so that the power of the engine is increased by 4-6 times, and the pollution emission of waste gas is greatly reduced. The engine only changes a part of parts on the basis of a crankshaft type internal combustion engine, greatly simplifies the structure and the manufacturing process of the engine body, lightens the engine body by 4-6 times, and reduces the production cost by 4-6 times.

The swing arm type two-stroke straight shaft internal combustion engine provided by the application is composed of a series of types and used as a power output device, is suitable for various delivery vehicles and equipment needing power, and can be divided into a single-cylinder type according to the installation position of a cylinder on a case, namely a V-shaped type shown in figure 7, a V-shaped type shown in figure 14 and a triangular type, wherein the triangular type is horizontally arranged and vertically arranged, and the triangular type shown in figure 28 is a horizontally arranged two-unit triangular type. The V-shaped internal combustion engine is characterized in that each duckbilled wheel position of a straight shaft is taken as a radial plane, 2 cylinders in the plane form an arrangement unit, three cylinders in the radial plane of each duckbilled wheel position of the straight shaft of the triangular internal combustion engine are taken as an arrangement unit, and the multi-cylinder internal combustion engine can be divided into multi-unit arrangement according to the arrangement quantity of the comma-shaped cam complexes of the duckbilled wheels on the straight shaft. The V-shaped machine body is designed on the basis of an equilateral triangle, the base is arranged on the bottom edge of the triangle, two cylinders are respectively arranged on two oblique edges, see fig. 14, the triangular machine body is also designed on the basis of the equilateral triangle, one cylinder is respectively arranged on three edges, the triangular machine body is vertically and horizontally arranged, see fig. 22 and 28, a swing arm corresponds to the lower surface of each cylinder of the V-shaped machine body and the triangular machine body, and the number of cylinders marked on the figure is that the number of corresponding swing arms is smaller.

The single cylinder type and the V type have the advantages that the cylinder on the engine body can be vertically upwards or upwards arranged at an angle of 60 degrees, the single cylinder is shown in figure 7, the form of the V type is similar to that of the V type of the cylinder of the crankshaft type internal combustion engine, the V type is a unit type, and the single cylinder is shown in figure 14, when the combination of the duckbill wheel and the comma-shaped cam on the straight shaft rotates for one circle, two cylinders on one unit of the V type respectively explode for one time, and compared with the crankshaft type four-stroke single cylinder internal combustion engine which explodes for two weeks, the single cylinder explodes for 4 times. Three cylinders on one unit of the triangular engine explode once respectively, and compared with the four-stroke crankshaft internal combustion engine which explodes once in two revolutions, the engine explodes six times in total, and the efficiency improved by the engine is increased, so that the output power is very strong, and a wide space is provided for realizing miniaturization and light weight of a high-power engine. The machine can be designed into other machine bodies, but compared with a V-shaped machine body and a triangular machine body, the two machine bodies have the most advantages in structural layout, so that the two machine bodies are preferably selected.

The following describes in detail the parts and operational performance of the present invention based on the single cylinder one unit model in the present application, in the order of explosion, exhaust, blow, compression, in conjunction with the drawings of the specification, compared to a 4 horsepower diesel engine produced by a Changzhou Tiancheng diesel engine plant. Then, the operation process of a unit type with 2 cylinders in a V-shaped layout and a unit type with 3 cylinders in a triangular layout is introduced, and finally, a unit type is introduced.

First, a cylinder-unit model will be described, see figure 7,

an explosion stage: the piston is connected with a connecting hole at the front end of the swing arm through a connecting rod at the top dead center, at the time, the arc vertex of the duckbill wheel is positioned at the right 45-degree angle position of the vertical central line of the straight shaft, see 76 in figure 7, the left side and the right side are based on a certain point on the figure, the left side and the right side are respectively the left side and the right side of the figure, the left side is viewed from the left side of the figure, the right side is viewed from the left side of the figure, and the description refers to the left side and the right side of the figure.

The lower arc point of the front end of the swing arm is in contact with the position of a few millimeters left side of the arc vertex of the duckbilled wheel, see 9-1 in fig. 9, the slide way at the top of the duckbilled wheel is divided into a left sliding section and a right sliding section by the arc vertex, see 6-1 and 6-6 in fig. 6, the arc top outgoing line of the arc sliding section of the left half part and the left horizontal line form a 25-degree included angle, see 25-degree lead in fig. 6, the rotating angle of a straight shaft is greatly increased when the piston descends in the initial stage of fuel explosion, the moment arm from the arc vertex of the duckbilled wheel to the central point of the straight shaft is 1.45 times longer than the radius of a crank of a 4-horsepower diesel engine, and as can also be seen from 5-5 marks in fig. 5, the center distance of a dotted line from the center of the upper connecting hole at the front end of the swing arm to the connecting hole of the solid line part at the rear end of the swing arm is longer than the intersection point of the arc point perpendicular to the dotted line under the swing arm, that is the power arm, that is about 1.2 times longer than the resistance arm. When the lower arc point of the front end of the swing arm runs downwards, the angle of the difference value is changed at the same time, so that the multiple ratio is not changed greatly. After fuel oil explodes, the piston pushes the connecting rod and the swing arm, so that the arc point at the lower part of the front end of the swing arm pushes the duckbill wheel to rotate to the right lower side along the left arc sliding section, and the arc point at the lower part of the swing arm slides to the left relative to the duckbill wheel left arc sliding section. When the piston descends 10 mm from the top dead center position during explosion, the lower arc point of the swing arm pushes the duckbill wheel to enable the straight shaft to rotate by about 43.6 degrees, and the angle is slightly lengthened compared with the angle of about 42.6 degrees when the piston descends 10 mm in a 4-horsepower diesel engine, and at the moment, the lower arc point of the swing arm is 38 mm away from the center point of the duckbill wheel, which is shown as 9-2 in fig. 9. The piston continues to move downwards under the push of explosion pressure, when the piston descends to 20 mm from the top dead center, the lower arc point of the swing arm is pushed to reach the top point of the left arc section of the duckbilled wheel, the straight shaft rotates by 73.6 degrees, see 10-1 in fig. 10, the straight shaft rotates from 43.6 degrees to 74.6 degrees and rotates by 31 degrees, when the 4-horsepower diesel engine descends to 20 mm, the crank rotates to 63 degrees and rotates from 42.6 degrees to 63 degrees, the crankshaft rotates by 20.4 degrees, the straight shaft is 1.52 times of the rotation angle of the crankshaft, and the process that the rotation angle of the straight shaft is increased compared with the rotation angle of the crankshaft internal combustion engine at the initial stage of fuel explosion is achieved. At the moment, the arc point of the lower part of the swing arm is 33 mm away from the center of the straight shaft, as shown in 10-1 in figure 10, which is 1.1 times of the crank length of the 4-horsepower diesel engine. Then the duck bill wheel moves downwards, and the lower arc point of the swing arm pushes the peak of the left arc-shaped section of the duck bill wheel, which belongs to a direct pushing state. However, as can be seen from 10-1 in fig. 10, the center of the upper connecting hole at the front end of the swing arm is closer to the right than the lower arc point of the swing arm, that is, the power arm is longer than the resistance arm, and the output efficiency is further improved compared with that of a crankshaft internal combustion engine. When the piston descends to 50 millimeters from top dead center, the internal tooth at swing arm front end middle part begins to cut into duckbilled department of duckbilled wheel, see 10-2 in figure 10, because the duckbilled wheel is close contact all the time to left circular arc sliding segment top and the lower circular arc point of swing arm when moving down, so the internal tooth of swing arm when the duckbilled contact with the duckbilled wheel, there is a stable contact curve, make the internal tooth of swing arm and the duckbilled of duckbilled wheel be close last mutual contact gradually with asymptote form, their contact process is similar to two meshed rotary gear, both sides joggle tooth is close the principle of last stationary contact with the same direction with speed syntropy during the rotation, thereby collision and the noise that produce when swing arm and duckbilled wheel duckbilled are approached fast and contact have been successfully eliminated. When the piston drops below 50 mm, the cylinder enters an exhaust stage, and when the piston drops to 50 mm from the top dead center in the whole explosion stroke, the straight shaft rotates by about 122 degrees.

And (3) exhausting and blowing stages: the piston in the explosion stroke pushes the swing arm to move downwards, when the piston descends to 50 mm from the top dead center, the upper piston ring of the piston is positioned at the upper edge of the exhaust hole on the side wall of the lower part of the cylinder, see 12-1 in figure 12, the exhaust gas in the cylinder begins to be discharged outwards through the exhaust hole on the side wall of the cylinder, the exhaust hole is divided into a left side surface, a right side surface, a left side surface and a right side surface, the exhaust hole is completely consistent with 27-2 and 27-5 in a V-shaped two-unit model figure 27, when the piston descends to half of the position of the exhaust hole, the air inlet cam on the straight shaft pushes the swinging piece, the air inlet valve is opened through the push rod and the upper rocker arm, the air inlet cam is shown as 8-9 in figure 8, the swinging piece and the push rod are shown as 8-5 and 8-3 in figure 8, compressed air blown out by the high-pressure fan enters the air cylinder through an air inlet channel on the air cylinder cover, 8-1 in figure 8 and is ventilated outwards through two exhaust holes on the lower side of the air cylinder. The exhaust and air blowing of the engine are completed within about 120 degrees, so the exhaust and air exchange process is much shorter than that of a crankshaft internal combustion engine, compressed air is blown in the engine, the air exchange speed is much higher, certain air pressure exists in the cylinder when an exhaust valve is closed, in order to increase the exhaust and air exchange speed, the number of exhaust holes can be increased from two to 4, and the left side and the right side of the exhaust holes are respectively arranged side by side, so that the fresh air can be filled in the cylinder after air exchange. The supercharging mode of the traditional internal combustion engine fan is multiple, the traditional mechanical supercharging mode of the turbo fan is adopted, the supercharging fan is installed at the top of the engine and is connected with a belt pulley on a crankshaft through a belt, the crankshaft outputs power to drive a fan rotor to rotate, and a left exhaust hole and a right exhaust hole on the outer wall of a case are respectively connected with exhaust pipes on two sides.

The cylinder enters an exhaust stage and then drives the straight shaft to continue rotating through the inertia wheel, the duckbill wheel continues rotating under the driving of the inertia wheel, a transition arc sliding section is arranged between an arc section at the duckbill position of the duckbill wheel and a circular sliding way of the duckbill wheel, 6-3 in figure 6, along with the rotation of the duckbill wheel, the inner teeth of the swing arm cut into the sliding section at the duckbill position of the duckbill wheel, 6-2 in figure 6, the sliding section moves onto the circular sliding section of the duckbill wheel through the transition arc sliding section, the circular sliding section is shown as 6-4 in figure 6, the piston stops at a bottom dead point, shown as 11-1 in figure 11, meanwhile, a side arm arc sliding block on the swing arm is also about to contact with the arc sliding section of the comma cam through a gap of 0.2 mm, shown as 11-2 in figure 11, and a basis is laid for the contact side arm arc sliding block of the comma cam without collision and noise. Swing arm internal tooth has a process that reduces the velocity of motion gradually from contacting the duckbilled wheel duckbilled to moving to the circular smooth section of duckbilled wheel, has avoided swing arm high-speed drop to the striking and the noise that cause of stopping suddenly when lower dead center. And then the straight shaft rotates by 60 degrees on the circular sliding section, the inner teeth of the swing arm always run on the circular track of the duckbilled wheel, the piston is stabilized at a bottom dead center, the exhaust valve is always in an open state, and air intake and air exchange are continuously carried out until the piston starts to run upwards. At the moment, the arc part of the comma cam starts to contact the arc slide way of the side arm of the swing arm, the swing arm starts to rise, the contact gap between the arc slide block of the side arm on the swing arm and the arc slide section of the comma cam is only 0.2 mm, and the contact between the arc slide block of the side arm on the swing arm and the arc slide section of the comma cam is gradually close to the final contact, so the collision and noise generated during the contact are eliminated, see 13-1 in fig. 13, when a lower piston ring on a piston rises to the upper side of an exhaust hole on the side wall of the cylinder, an air inlet cam on a straight shaft releases a swing sheet push rod and an upper rocker arm, so that an inlet valve in an open state is closed, and the cylinder enters a compression stroke. The straight shaft rotates through an angle of about 120 degrees in the whole exhaust and ventilation process.

A compression stage: the arc slide block on the side wall of the swing arm is pushed by the arc slide way of the comma-shaped cam to continuously rise, when the arc slide block is 12 mm away from the top dead center, the arc point at the lower end of the swing arm rises to be in contact with the vertex at the right end of the right half arc slide section of the duckbill wheel which rotates, the contact gap between the arc point and the right half arc slide section of the duckbill wheel is 0.2-0.5 mm at the moment, see 13-2 in fig. 13, the arc slide way of the comma-shaped cam controls the rising speed of the swing arm, so that the contact process of the arc point at the lower end of the swing arm and the right half arc section of the duckbill wheel is gradually close to and stably contacted, and the impact and noise during the contact are avoided. The rest arc-shaped sliding section is an ignition advance angle sliding section, at the moment, an oil injection cam on a straight shaft pushes an oil injection valve through a swing block, oil is pressed to an oil injection nozzle through an oil pipe, and gasified fuel oil is injected into a cylinder, as shown in 8-10, 8-7 and 8-6 in figure 8, and meanwhile, a duckbill wheel drives a lower arc point of a swing arm to drive a piston to rise to an upper stop point under the drive of an inertia wheel. After the piston of the internal combustion engine runs to the top dead center, the conversion from the top dead center to the bottom dead center is not provided with the forced linkage conversion mechanism of the crank control connecting rod of the crankshaft internal combustion engine, the conversion from the top dead center to the bottom dead center is realized, the adopted measure is similar to the mode that the camshaft of the internal combustion engine pushes the valve rod rocker arm to run up and down, and because the valve rod rocker arm is pushed by the strong force of the valve rod spring, the valve rod rocker arm is always in close contact with the contact surface of the cam, and the contact surface can not be separated in the high-speed rotation of the camshaft. The local is two strokes, and the piston all is in the highest compression stage when rising to the top dead center at every turn, and the powerful compressive force of gas is enough to guarantee in the cylinder that the piston moves to the top dead center and converts the downward movement in-process into again, and the arc point converts the left circular arc section into through the circular arc summit from duckbilled wheel right circular arc section under the swing arm, and the arc point is in close contact with all the time on duckbilled wheel circular arc top under the swing arm. When the circular arc vertex of the duckbilled wheel rotates to pass through the upper dead point, the lower circular arc point of the swing arm is located at the position where fuel oil of the left circular arc section of the circular arc vertex of the duckbilled wheel explodes, so that the single-cylinder single-unit internal combustion engine completes the whole process of two strokes in one circle of rotation, and the straight shaft of the whole compression process rotates by about 120 degrees.

Two-cylinder one-unit V-shape type: the straight shaft rotates for a circle, the duckbilled wheel and the comma-shaped cam are respectively in contact fit with the two swing arms and the side wall slide block successively, through six intermittent contact points, two cylinders on a case explode once respectively, and the duckbill wheel and the comma-shaped cam explode 4 times compared with a crankshaft internal combustion engine which explodes for 1 time in two circles of four strokes, the two cylinders and a unit V-shaped machine type is shown in a figure 14, the air inlet valve is opened and closed by pushing swing pieces on two sets of swing frames through the air inlet cam on the straight shaft, and then the air inlet valve is pushed through the push rod and the upper rocker arm, shown in a figure 15, and each air inlet valve works once when the straight shaft rotates for a circle. Because the exhaust port at the lower side of the cylinder is directly communicated with the outside through the exhaust pipe of the case, the exhaust pipe is raised up after being connected with the case, see 15-4 in fig. 15, so as to prevent lubricating oil in the case from leaking outwards through the exhaust pipe, and the two exhaust holes at the two sides of the two cylinders on the case are connected together through the exhaust pipe to send waste gas outwards. The oil supply system also pushes the swing block on the swing frame to push the oil injection valve through the oil injection cam on the straight shaft, the oil pipe supplies oil to the oil injection nozzle on the cylinder cover, see fig. 16, the booster fan is arranged at the top of the machine box, the installation position is shown as 29-3 in fig. 29, and simultaneously supplies air to the two air inlet valves, and the working process of one rotation of the V-shaped machine is described on the basis of the working process of the single-cylinder machine.

The piston in the cylinder 1 is at the top dead center, make swing arm 1 front end lower part circular arc point contact at duckbilled wheel circular arc apex through the connecting rod, see fig. 14, the piston rises 20 millimeters position departments in bottom dead center cylinder lateral wall exhaust hole downside in the cylinder 2, the middle part sliding segment of swing arm 2 lateral wall slider left side afterbody contact at the direct axis comma cam this moment, when the piston rises 10 millimeters from the bottom dead center in the cylinder 2, namely when the piston is 50 millimeters from the top dead center, the epaxial inlet cam release pendulum piece that admits air, make the inlet valve on the cylinder 2 close through push rod and rocking arm, the cylinder 2 gets into compression state. The air intake and exhaust system is shown in figure 15. The explosive force and the pressure after the fuel oil in the cylinder 1 explodes push the duckbill wheel to rotate clockwise, when the piston in the cylinder 1 descends by 20 mm, the lower arc point of the swing arm 1 is contacted with the top point of the left arc section of the duckbill wheel, 17-1 in figure 17, the middle sliding section of the comma-shaped cam on the straight shaft is contacted with the top point of the right side of the arc sliding section of the side arm of the swing arm 2, and 17-2 in figure 17 pushes the swing arm 2 to ascend, and the piston in the cylinder 2 ascends to a position 20 mm away from the top dead point through the connecting rod, so that the gas in the cylinder 2 is further compressed. The straight shaft continues to rotate, the top point of the right end of the right circular arc section of the duckbilled wheel starts to be close to the lower circular arc point of the swing arm 2 and gradually contacts the right circular arc section surface of the duckbilled wheel under the control of the rear half section of the comma cam, when the lower circular arc point of the swing arm 2 contacts the right circular arc section surface of the duckbilled wheel, the remaining sliding section is a small sliding section from the sliding section to the circular arc top point, the straight shaft oil injection cam pushes the oil injection valve to enable the oil injection nozzle to inject oil into the cylinder 2, an oil supply system is shown in figure 16, meanwhile, the duckbilled wheel right circular arc section pushes the lower circular arc point of the swing arm 2 to enable the piston to rise to the upper stop point, and is shown in figure 17-4 in figure 17. At this time, the piston in the cylinder 1 descends to a position 50 mm away from the top dead center, the piston runs to the exhaust hole position of the cylinder 1, the exhaust gas in the cylinder 1 begins to be discharged outwards, when the piston descends to a position 54 mm away from the top dead center, the air inlet cam on the straight shaft pushes the swing sheet, the air inlet valve on the cylinder cover 1 is opened through the push rod and the rocker arm, the cylinder 1 enters the exhaust and ventilation stage, the high-pressure air sent by the high-pressure fan blows into the cylinder and exhausts to the exhaust pipe outside the case through the exhaust hole on the side wall of the cylinder, the exhaust holes of the cylinder 1 and the cylinder 2 are divided into the left side and the right side, the two exhaust holes on the two sides are respectively connected in series through the exhaust pipe, the right side exhaust system is shown as 15-4 in fig. 15, the left side exhaust system is completely symmetrical to the right side, and the exhaust holes on the two sides of the cylinder are completely identical to the exhaust holes 27-2 and 27-5 in fig. 27. At this point the internal teeth in the middle of the front end of the swing arm 1 cut a small distance into the duckbill top arc segment, 17-3 in figure 17.

When the piston 2 descends to about 10 mm from the top dead center, see 18-2 in fig. 18, the piston in the cylinder 1 descends to the bottom dead center under the thrust of a steady spring and the downward thrust of the piston running downwards, and the left side of a comma-shaped cam circular slideway on the straight shaft starts to contact an arc slideway on the side wall of the swing arm 1, see 18-1 in fig. 18. When the piston in the cylinder 2 descends to 50 mm from the top dead center, the piston moves to the exhaust hole position of the cylinder 2, waste gas in the cylinder 2 begins to be discharged outwards, at the moment, the internal teeth in the middle of the front end of the swing arm 2 cut into the duckbill part of the duckbill wheel, see 19-2 in fig. 19, when the piston 2 descends to 54 mm from the top dead center, the air inlet cam on the straight shaft begins to push the air inlet system to open the air inlet valve on the cylinder cover of the cylinder 2 for ventilation, the piston in the cylinder 1 ascends to 40 mm from the top dead center, and the sliding section in the middle of the comma-shaped cam contacts with the left tail part of the side wall sliding block of the swing arm 1, and 19-1 in fig. 19. At this time, the inertia wheel drives the straight shaft to continue rotating, the circular sliding section of the comma-shaped cam is contacted with the middle part of the arc-shaped sliding section of the side wall of the swing arm 2, 19-4 in the figure 19, and the piston in the cylinder 2 descends to the bottom dead center. At this time, the middle sliding section of the comma-shaped cam is contacted with the position which is deviated from the left position in the middle of the arc-shaped sliding section of the side wall of the swing arm 1, 19-3 in fig. 19 pushes the piston 1 to ascend to compress the gas in the cylinder 1, and the piston 1 ascends to the position 28 mm away from the top dead center. The comma-shaped cam on the straight shaft is driven by the inertia wheel to continuously push the swing arm 1 to ascend, when the swing arm is 12 mm away from the top dead center, the arc point under the swing arm starts to contact with the right end vertex of the right semicircular arc slideway of the duckbilled wheel, the arc point under the swing arm is controlled by the comma-shaped cam to be stably contacted with the duckbilled wheel, the oil injection cam on the straight shaft after the contact starts to push the oil injection valve to inject the gasified fuel oil into the cylinder through the swing block, meanwhile, the right arc section of the duckbilled wheel pushes the swing arm 1 to enable the piston to ascend to the top dead center, and the V-shaped straight shaft runs for a circle, and the pistons in the two cylinders respectively explode once.

Triangular three-cylinder one-unit model: the operation sequence of the vertical arrangement of the cylinders will be described in the following from the positions of fig. 20 to fig. 25, and the operation sequence of the horizontal arrangement of the cylinders is completely the same as the vertical arrangement. The speed regulating system is basically consistent with the V-shaped speed regulating system when vertically placed, the speed regulator is arranged on an outer straight shaft on the right side of a machine box, a hole is drilled on the side wall of the machine box, the oil supply amount of an oil injection pump is controlled through a link rod, when a triangle-shaped one-unit type cylinder is vertically placed, an oil injection part is shown in figure 20, an air inlet system is shown in figure 21, a structure diagram of a triangle-shaped machine body is shown in figure 28 when horizontally placed, a bottom-layer one unit in the figure and a 28-3 air inlet cam system in the figure 28 form a triangle-shaped horizontal one-unit type, a base part of the machine box of the triangle-shaped machine type is totally closed to prevent oil leakage, and the speed regulating and oil supplying system adopts a high-pressure common rail mode when the cylinder is horizontally placed.

The output shaft of the triangle 3-cylinder one-unit type engine rotates for 3 times of fuel oil outbreaks in one circle, and the fuel oil outbreaks for 6 times compared with a crankshaft internal combustion engine with 1 outbreak in two circles of four strokes, the triangle type engine is designed on the basis of an entity equilateral triangle, one cylinder is respectively arranged on three edges, the lower surface of each cylinder is connected with a side arm slider type swing arm through a piston, as shown in figure 22, a duckbill wheel and comma-shaped cam combination is arranged at a central point vertical to a triangle plane, the straight shaft rotates for one circle, the duckbill wheel and the comma-shaped cam are respectively contacted and matched with the three swing arms one time after one cycle, and the 3 cylinders on the case explode one time after nine intermittent contact points. The air inlet cam on the main shaft respectively pushes three sets of rocker arm systems which form an angle of 120 degrees with each other to open and close the air inlet valve, in the figure 21, each air inlet valve works once when the straight shaft rotates for a circle, the vertically placed type exhaust system is the same as the single-cylinder V-shaped type, the horizontally placed type exhaust system is different from the single-cylinder V-shaped type, an exhaust hole channel and the straight shaft form an angle of 90 degrees, in the figure 28, the oil supply system also respectively pushes three swing blocks and oil injection valves which form an angle of 120 degrees with each other through the oil injection cam on the straight shaft, oil is respectively supplied to an oil injection nozzle on a cylinder cover through an oil pipe, in the figure 20, each oil injection valve works once when the straight shaft rotates for a circle, and the horizontally placed type oil supply system adopts a high-pressure common rail oil supply mode in the prior art. The centrifugal fan supplies air for three admission valves simultaneously, outwards exhausts through the exhaust hole on the quick-witted case, and 3 every cylinder both sides of cylinder respectively have an exhaust hole on the quick-witted case, and 3 antithetical couplets are together outwards sent waste gas for every survey in 6 exhaust holes.

The working process of rotating a triangle-shaped unit vertical machine type straight shaft for one circle is described below, a piston in a cylinder 1 is at the top dead center, the piston in a cylinder 2 is at the position 20 mm above the bottom dead center, internal teeth in the middle of the front end of a swing arm 3 connected below the piston of the cylinder 3 start to cut into a duckbilled part of a duckbilled wheel, see fig. 22, a lower arc point of the swing arm 3 is contacted with the top of the left end of a left arc sliding section of the duckbilled wheel, see 22-1 in fig. 22, a piston ring on the piston at the moment of the swing arm 3 descends to the upper side of an exhaust hole on the side wall of the cylinder 3, and waste gas in the cylinder 3 starts to be discharged outwards, see 22-3 in fig. 22. The explosive force and the pressure promote the piston to make duckbilled wheel clockwise rotation after the fuel in the cylinder 1 explodes, and piston 3 has descended to 54 millimeters from the top dead center this moment, and the cam that admits air on the straight axis promotes the pendulum piece, makes the (air) intake valve on the cylinder 3 open through push rod and rocking arm, and the compressed air that high pressure positive blower sent blows in the cylinder to exhaust to the blast pipe of quick-witted case outside through the cylinder lateral wall exhaust vent. The straight shaft continues to rotate, the internal teeth in the middle of the swing arm 3 below the cylinder 3 cut into the duckbilled sliding section of the duckbilled wheel and move to the circular slide way through the middle transition sliding section, the swing arm 3 reaches the lower dead point, and the exhaust ventilation in the cylinder 3 is continuously performed. At this time, the piston in the cylinder 1 descends to about 10 mm from the top dead center, the piston in the cylinder 2 ascends to about 25 mm from the top dead center,

when the piston in the cylinder 1 descends by 20 mm, the lower arc point of the swing arm 1 is contacted with the top of the left end of the left arc sliding section of the duckbill wheel, see 23-1 in fig. 23, the middle sliding section of the comma-shaped cam on the straight shaft is contacted with the top point of the right side of the arc sliding section of the side arm of the swing arm 2, see 23-2 in fig. 23, at this time, the comma-shaped cam at the position of the swing arm 3 runs through the sliding section on the circular track, and the rear arc sliding section starts to gradually contact the side wall sliding block of the swing arm 3 and pushes the swing arm 3 to ascend, see 23-3 in fig. 23. When the piston 3 rises to the upper side of the exhaust hole on the side wall of the cylinder 3, namely, 50 mm away from the top dead center, the tail part of the slide block on the side wall of the swing arm 3 contacts the middle slide section of the comma cam, see 23-6 in fig. 23, the swing piece on the air inlet system 3 is released by the air inlet cam on the straight shaft, the air inlet door on the cylinder cover of the cylinder 3 is closed through the rocker arm on the connecting rod, the cylinder 3 enters a compression stroke, at the moment, the internal tooth in the middle of the front end of the swing arm 1 connected below the piston of the cylinder 1 starts to cut into the circular arc at the duckbilled part of the duckbilled wheel, see 23-4 in fig. 23, and the circular arc point below the swing arm 2 connected below the piston of the cylinder 2 is about to reach the circular arc vertex of the duckbilled wheel, see 23-5 in fig. 23. Then the piston in the cylinder 2 reaches the top dead center, the fuel in the cylinder 2 explodes to push the duckbill wheel to continue rotating, and at the moment, the comma-shaped cam pushes the side wall slide block of the swing arm 3 to lift the swing arm 3, as shown in 23-6 in fig. 23.

When the straight shaft rotates to the position, below the swing arm 3, of the arc point, the contact with the right end of the rotary duckbill wheel right arc section is required, at the moment, the distance between the right end of the duckbill wheel and the lower arc point of the swing arm 3 is still 0.2-0.5 mm, the duckbill wheel continuously rotates, the lower arc point of the swing arm 3 is controlled by the comma-shaped cam and the swing arm side wall sliding block, the lower arc point is gradually close to and is in contact with the right arc section of the duckbill wheel, collision and noise during contact are avoided, when the lower arc point of the swing arm 3 is in contact with the right arc section of the duckbill wheel, the remaining small section sliding section to the arc vertex is a sliding section, and the straight shaft fuel injection cam pushes the fuel injection valve on the cylinder cover to inject fuel into the cylinder. At the moment, the middle sliding section of the comma-shaped cam corresponding to the swing arm 1 below the cylinder 1 contacts the tail part of the left side of the side wall sliding block of the swing arm 1, see 24-1 in figure 24, and the middle internal tooth of the front end of the swing arm 2 connected below the piston of the cylinder 2 starts to cut into the duckbilled part of the duckbilled wheel, see 24-2 in figure 24. Then the inertia wheel drives the duckbilled wheel right circular arc section on the straight axis and promotes 3 lower circular arc points of swing arm and reach duckbilled wheel circular arc summits, and the fuel in the cylinder 3 begins the explosion, and explosive force adds pressure promotion duckbilled wheel clockwise and continues the rotation. When the piston in the cylinder 3 descends to the top dead center by 20 mm, and the lower arc point of the swing arm 3 runs to the top point of the left end of the left arc section of the duckbill wheel, 25-1 in fig. 25, the top point of the right end of the arc section of the side wall slide block of the swing arm 1 contacts with the middle slide section of the comma cam, shown as 25-2 in fig. 25, and simultaneously the comma cam starts to push the side wall slide block of the swing arm 2 to lift the swing arm 2, shown as 25-3 in fig. 25. The straight shaft continues to rotate, when the internal teeth at the middle part of the front end of the swing arm 3 start to cut into the circular arc section at the duckbilled part of the duckbilled wheel, 25-4 in fig. 25, the circular arc point under the swing arm 1 runs to the oil injection section of the right circular arc section surface of the duckbilled wheel, 25-5 in fig. 25, the top point at the left end of the circular arc section of the side wall slide block of the swing arm 2 is contacted with the sliding section in the middle part of the comma cam, 25-6 in fig. 25, then the straight shaft drives the duckbilled wheel to push the circular arc point under the swing arm 1 to enable the piston 1 to ascend to the top dead point, and the straight shaft of the triangle machine type runs for a circle until the straight shaft of the triangle machine type drives 3 cylinders on the case to explode once.

Four-cylinder two-unit V-type: see fig. 26 and fig. 27, a unit is added on the basis of a two-cylinder one-unit, 4 cylinders are provided in total, the engine is equivalent to an eight-cylinder four-stroke crankshaft internal combustion engine, two sets of duckbill wheel comma-shaped cams on a straight shaft replace 8 cranks on a crankshaft, 4 swing arms and side wall sliders of a two-unit V-shaped engine are respectively arranged on two sides of the straight shaft in a case in a group, see fig. 26-4 and 26-9 in fig. 26, because the two duckbill wheel mounting positions are close to two side walls of the case, the stress capability of the straight shaft is enhanced, the arc vertex of the duckbill wheel is at an angle of 45 degrees when fuel oil explodes, the normal force transmitted to the straight shaft by the explosive force is far smaller than the stress of the crankshaft, so that no reinforcing measure is needed in the middle of the straight shaft, and the manufacturing process is reduced. The bottom seat of the swing sheet frame is arranged at the middle position of the case, see 26-2 in figure 26, the cam on the straight shaft pushes 4 push rods on two swing sheets to respectively push 4 upper rocker arms on two cylinder covers to work through a middle through hole of two cylinders and a middle through hole of the cylinder covers, see 26-7 and 26-5 in figure 26 and 27-8 in figure 27, the improvement enables one cam of the engine to replace 8 cams of a crankshaft internal combustion engine, saves a large number of processes for manufacturing and installing a cam system, and is miniaturized. 27-1, 27-6 in FIG. 27 are the positions of the intake ports, the left cylinder head structure and the right cylinder head structure in FIG. 27 are identical, 26-6 in FIG. 26 are the steady spring baffles, and the dotted lines in the middle of the baffles are the inner spring rods.

The exhaust part exhausts from 6 exhaust ports on 4 cylinders, 4 exhaust ports are arranged on two side walls of the case, see 27-2 and 27-5 in fig. 27, 2 exhaust ports in the middle are respectively exhausted from exhaust ports close to the middle parts of the two cylinders to one exhaust port on the case, see 26-1 and 26-10 in fig. 26 and 27-3 and 27-7 in fig. 27, the oil supply mode adopts a high-pressure common rail mode in the prior internal combustion engine technology, and the rotation matching sequence of the swing arm and the duckbill wheel is completely the same as the working sequence of one unit of the two cylinders in one rotation of the straight shaft of the two units.

Triangle 6 cylinder two-unit model: the rotary matching relation of a duckbilled wheel and a swing arm of the three-cylinder three-unit air cylinder is completely consistent with that of a triangular 3-cylinder one-unit air cylinder, the triangular two-unit air cylinder is also vertically placed and horizontally placed, only one unit is added on the basis of a graph 22 when the three-unit air cylinder is vertically placed, an air inlet cam and a swing sheet system are installed in the middle of a case, and the other parts of the three-cylinder three-unit air cylinder are completely consistent with that of a triangular 3-cylinder one-unit air cylinder. When the 6-cylinder two-unit type is horizontally placed, because the exhaust ports in the cylinder are directly communicated with the outside of the case, the exhaust ports are changed from a vertically placed type into the type which is on the same horizontal plane with the swing arm, as shown in the positions 28-1 and 28-2 in fig. 28, the triangular base part of the case is totally closed to prevent oil leakage, and the structural schematic diagram is shown in fig. 28. The engine has the common characteristics that a 6-cylinder two-unit triangle type engine is additionally provided with a unit on the basis of a 3-cylinder one-unit, the engine has 6 cylinders, and is equivalent to a 12-cylinder four-stroke crankshaft internal combustion engine, 12 cranks on a crankshaft are replaced by two sets of duckbill wheel comma-shaped cams on a straight shaft, a large amount of processes for manufacturing complex cranks are reduced, 6 swing arms and side wall sliders of the 6-cylinder 2-unit triangle type engine are respectively installed on two sides of the straight shaft in a case in a group of 3 swing arms, the installation positions of the two duckbill wheels are close to two side walls of the case, the stress capability of the straight shaft is enhanced, the arc vertex of the duckbill wheel is at an angle of 45 degrees during fuel oil explosion, the normal force transmitted to the straight shaft is far smaller than the stress of the crankshaft, no reinforcement measure is needed in the middle of the straight shaft, one cam on a straight shaft of an air inlet system pushes 6 push rods on 3 sets of swing plates, and an air inlet valve is opened and closed through 6 rocker arms on a cylinder cover, the improvement that the swing sheet of a horizontal placing machine type is arranged on a cylinder of the swing sheet frame, and a cylinder base is arranged in the middle of a case, as shown in 28-3 in figure 28, one cam of the machine replaces 12 cams of a crankshaft internal combustion engine, a large number of processes for manufacturing and installing a camshaft system of the crankshaft internal combustion engine are saved, and the machine body is further miniaturized.

Multi-cylinder multi-unit model: compared with the multi-cylinder multi-unit type and the 2-unit type, the multi-cylinder multi-unit type and the 2-unit type have the advantages that besides the addition of a plurality of units, a reinforcing straight shaft measure similar to a crankshaft bearing bush fixing part of a crankshaft internal combustion engine is added in the middle of a straight shaft, for example, a V-shaped 8-cylinder 4-unit type and a triangular 12-cylinder 4-unit type are added, a bearing bush is added in the middle of 4 units of the straight shaft, the reinforcing effect of the straight shaft is achieved, and the structures of other parts are completely consistent with those of the 2-unit type.

The internal combustion engine only has two strokes of explosion and compression, so that the piston is driven to run to a bottom dead center under the action of explosion pressure in the explosion stroke, when the internal combustion engine is stopped and no pressure exists in a cylinder, the swing arm and the piston are in an uncontrolled free running state, the thrust of the steady spring pushes the piston and the swing arm at the moment, the combination of the swing arm, the side arm arc slide block and the duckbill wheel comma-shaped cam is in a contact state no matter what angle the duckbill on the straight shaft stops, and the spring rod on the swing arm can also detect the specific positions of the swing arm and the piston and can adjust the positions of the swing arm and the piston.

A speed regulator is arranged on a straight shaft of the outer wall of the right side of a case, a hole is drilled on the side wall of the case, the oil supply amount of an oil injection pump is controlled through a link rod, a triangular one-unit type cylinder is vertically and horizontally arranged, when the cylinder is vertically arranged, see figure 20, an oil injection cam controls 3 oil injection pumps, the speed regulation system is the same as the V type, the speed regulator is arranged on the straight shaft of the outer wall of the right side of the case, a hole is drilled on the side wall of the case, the oil supply amount of the oil injection pump is controlled through the link rod, when the cylinder is horizontally arranged, a high-pressure common rail oil supply mode is adopted, the types of the two units adopt the high-pressure common rail oil supply mode, and the high-pressure common rail oil supply speed regulation system belongs to the prior art and is not introduced in detail.

The fuel oil explosive force at the ignition advance angle stage of the crankshaft type internal combustion engine is used for doing negative work, the arc top point of the duckbilled wheel at the ignition advance angle stage of the engine can be made into an arc section which is several millimeters and vertical to the axis, and the enlarged part in 6-5 in fig. 6 avoids the phenomenon that the fuel oil explosive force at the ignition advance angle stage does negative work, provides a stable explosive environment for fuel oil explosion, and further improves the efficiency of the engine. Because this local duckbilled wheel right arc section promotes the swing arm when upwards moving, arc point also gives duckbilled wheel right arc section a thrust down simultaneously under the swing arm, and this thrust is done positive power to the output shaft, just compare two boats that opposite direction went, pushes away another boat from a boat, and the boat of oneself has also obtained the power that gos forward, so local duckbilled wheel right arc section promotes the swing arm and rises and feel not hard when going to the top dead center, and this provides the advantage for this local further improvement compression ratio. And the explosive point of the machine is positioned at the 45-degree angle of the vertical line of the axis of the straight shaft, the impact force of the explosive force on the straight shaft is greatly reduced, and favorable conditions are provided for further improving the compression ratio of the machine.

The contact part of the arc point under the swing arm of the machine and the left arc section of the duckbilled wheel has the arc section of several millimeters and the radian of the left arc section of the duckbilled wheel, and the radian is the same as that of the arc section of 9-2, so that the friction pressure in the operation of the contact part of the arc point under the swing arm is reduced, and the durability of the arc point under the swing arm under the condition of strong frequent impact during fuel oil outbreak is increased.

The rotation of the engine has a plurality of intermittent points which are in quick contact, the operation stability is poorer than that of a crankshaft internal combustion engine, the engine is more suitable for medium-speed or medium-high-speed operation, and the rotating speed ratio can be increased to increase the rotating speed of the engine when the engine needs to operate at a high speed due to the increase of the output power of the engine. Three intermittent contact points of a single cylinder type are respectively in sequence, the first intermittent contact point is that a lower arc point of a swing arm is in contact with the top point of the left end of a duckbill wheel and moves downwards, the inner tooth of the swing arm is in contact with the duckbill part of the duckbill wheel, see 10-2 in figure 10, the second intermittent contact point is that a piston operates at a bottom dead point, the inner tooth of the swing arm is in contact with an arc slide block of a side arm of the swing arm when the circular orbit operation of the duckbill wheel is about to end, see 11-2 in figure 11, the third intermittent contact point is that the lower arc point of the swing arm rotates to contact with the top dead point by 12 mm, at the moment, the rear half section of the arc slide section of the comma cam controls the slide block of the side wall of the swing arm, so that the lower arc point of the swing arm is in stable contact with the right arc slide section of the duckbill wheel, see 13-2 in figure 13, the contact process of the three contact points adopts two parts to approach and contact in a form of an asymptotic line in the contact process, the collision and noise generated during contact are successfully eliminated, and the intermittent contact point of the multi-cylinder type is completely the same as the single-cylinder contact form.

The straight shaft internal combustion engine can also rotate in the opposite direction, taking a single-cylinder one-unit type as an example, at the moment, the straight shaft of the duckbilled wheel combination is used as the main power, the arc point at the lower end of the swing arm is at the bottom dead center, and the inner teeth of the swing arm are in contact with the circular track of the duckbilled wheel, as shown in 11-2 in fig. 11. Under the drive of external force, the anticlockwise counter-rotation of straight axle, duckbilled transition arc section promotion swing arm middle part internal tooth of duckbilled wheel upwards moves, see 10-2 in figure 10, arc point under the swing arm is contacted to the left arc section left end top point of duckbilled wheel, promote the swing arm and continue rising, the epaxial duckbilled wheel of straight continues anticlockwise rotation, arc point rises to the circular arc summit of duckbilled wheel along duckbilled wheel left arc section slide under the swing arm all the time, gaseous in the cylinder is in compression state, see 7-6 in figure 7. When external force is large enough, the arc point at the lower end of the swing arm can cross over the arc vertex of the duckbill wheel, compressed gas in the cylinder pushes the arc point under the swing arm to move downwards along the right arc slideway of the duckbill wheel, the comma-shaped cam starts to contact with the arc at the side end of the swing arm in the anticlockwise direction to slide quickly, when the right end of the right arc sliding section of the duckbill wheel is operated, the arc point under the swing arm is separated from the right sliding section of the duckbill wheel, the side wall slide block of the swing arm continues to move downwards along the arc slideway of the comma-shaped cam, see 13-2 in fig. 13, the straight shaft continues to move anticlockwise, under the thrust of the external force and the steady spring, the comma-shaped cam controls the side wall slide block of the swing arm to move downwards to the lower dead center, and the straight shaft rotates 360 degrees anticlockwise.

The hardness requirements of the swing arm side wall slide block, the duckbill wheel comma-shaped cam and the straight shaft surface are HRC58-64, and the hardness requirements of the swing arm lower arc point and the duckbill wheel top arc slide section are hard alloy.

The theory that the power of the swing arm type two-stroke straight shaft internal combustion engine is improved by 4-6 times proves that: the improvement of the power of the internal combustion engine by 4-6 times is difficult to be questioned or denied, because in the heat engine theory, the heat engine efficiency theory represented by the carnot cycle sets a plurality of limits for improving the efficiency of the internal combustion engine, the heat efficiency does not exceed dozens of percent, in the direction of improving the heat engine efficiency, the direction of improving the heat engine efficiency is pointed out (the T1 is improved, the T2 is reduced, the irreversible losses such as heat dissipation, air leakage and friction are reduced, the cycle is close to the carnot cycle as much as possible), in the consistency of the carnot cycle efficiency, any working substance is provided to be used as the carnot cycle, the efficiency is consistent, the efficiency of the heat engine is improved, and the temperature of a high-temperature heat source and the temperature of a low-temperature heat source are improved.

These limitations produce serious misleading and confinement effects in the field of internal combustion engines, which results in that a large number of crankshaft internal combustion engine researchers spend a great deal of time, energy and capital investment, but deviate from the core of problems in the research direction of improving efficiency, and the reasons are always omitted, so that the reciprocating piston type internal combustion engine can not greatly improve the output efficiency all the time in nearly two hundred years.

The misleading of the carnot cycle heat engine efficiency theory is: it is not clearly explained that the work of the internal combustion engine needs the explosive force generated by fuel explosion and the mechanical work made by pressure, the heat energy is only a conversion mode, the same fuel releases the same heat energy, the output power of combustion and explosion is different by more than ten thousand times, a huge explosive force is generated by explosion than combustion, the explosive force is lost most in the crankshaft internal combustion engine, and the Carnot cycle theory blurs that the explosion ratio is higher than that of combustion and a huge explosive force is generated. The Carnot cycle combines the huge difference of the heat engine efficiency and the mechanical efficiency of the internal combustion engine, the same fuel generates the same high temperature and pressure, the working output efficiency is different by several times under different mechanical conditions, the useless component force generated by the crankshaft internal combustion engine connecting rod pushing the crank loses a large amount of energy, and the mechanical efficiency is greatly reduced. The Carnot cycle does not divide a steam engine, the steam turbine and the internal combustion engine are of different working modes, the working mechanisms of the steam engine and the internal combustion engine are different and can not work in the same day, the steam engine and the steam turbine both work by burning fuel, the efficiency is greatly different because the eccentric wheel of the steam engine generates useless component force to reduce the efficiency, the steam turbine is pushed by the air pressure of the steam turbine at an angle of 90 degrees to work, the useless component force is not generated to lose mechanical energy, the internal combustion engine does work by exploding the fuel, and a huge explosive force is generated compared with the fuel burning. The carnot cycle heat engine efficiency theory only provides a fuzzy concept of heat engine efficiency in a general way, but summarizes the whole heat engine system, and by using the fuzzy and serious misleading theory, billions of people in the world are influenced to eat and drink a trip and a national economic life line in nearly two hundred years, which is not responsible for science and human beings in any aspect, and the loss is immeasurable and certainly unwilling before carnot. It is misled in that: 1. the explosive force of the internal combustion engine is the main energy for doing work, the explosive power of fuel oil is more than ten thousand times of the combustion power, the Carnot cycle obscures that the explosion ratio and the combustion can generate a large explosive force in the heat engine efficiency theory, and the heat efficiency theory derived by the push-down of the quasi-static condition of the Carnot cycle is obviously not suitable for limiting the explosive force of the internal combustion engine to do work. 2. The working of the internal combustion engine is moment work which is obtained by pushing a connecting rod to rotate a crank under pressure, the influence of different angles in the vertical direction of the connecting rod on the output efficiency is different by several times, the carnot cycle heat engine efficiency theory does not show the point, and the basic fact that a large amount of energy is lost due to useless component force of the crankshaft internal combustion engine is avoided.

The heat engine efficiency theory represented by the Carnot cycle has been proposed for nearly two hundred years, the major defects and misleading in the Carnot cycle theories are not found to be questioned by relevant authoritative documents and further supplement and improvement of theories, and the misleading is that people often limit the mechanical efficiency of the internal combustion engine by the Carnot cycle heat engine efficiency, so that the internal combustion engine is further afraid of the Reynolds pool in greatly improving the efficiency, and therefore, the internal combustion engine has a major breakthrough in the output efficiency, and a new breakthrough in the internal combustion engine theory is needed firstly. The defects and misleading meanings of the carnot cycle heat engine efficiency theory are pointed out as follows: the internal combustion engine has a huge space for improving efficiency, the advantages of the internal combustion engine after reasonable improvement far exceed those of a pure electric vehicle and a hydrogen fuel cell vehicle, particularly the ultra-light engine body of the engine, huge output power and large energy conservation are realized, an excellent power source is provided for the aircraft to enter a family, and people can go out in the near future and are convenient like birds.

The applicant's new theory in greatly improving the efficiency of an internal combustion engine: 1. the work of the internal combustion engine needs the explosive force generated by fuel explosion and the mechanical work made by pressure, the heat energy is only a conversion means, the same fuel releases the same heat energy, the output power of combustion and explosion is different by more than ten thousand times, the steam engine theory and the internal combustion engine theory can not be mixedly explained 2. 3. The crankshaft internal combustion engine does work, namely moment work of pushing a connecting rod by pressure to enable a crank to rotate, and as the crank is close to a zero-degree angle of an upper dead point at the moment of fuel oil explosion, a large amount of energy is lost due to useless component force, the mechanical efficiency is greatly reduced, the mechanical structure of the internal combustion engine is reasonably changed, the angle of a moment arm at the moment of fuel oil explosion in the vertical direction is increased, the output efficiency is different by several times, and 4 after the mechanical structure of the crankshaft internal combustion engine is reasonably improved, the mechanical efficiency can be improved by several times.

The evidence of the greatly improved output power of the internal combustion engine is as follows: the proof that the output power of the local machine is greatly improved is a specific process from theory to practice, part of data given in the proof is average data and measurement experiment data, and part of measurement experiment values and calculation data have small errors, but the proof result that the output power of the local machine is improved by 4-6 times can be met. The improvement of explosive power and the improvement of pressure power are proved. The proving method is divided into a working data proving and a working area proving. The principle that the explosive power of said machine can do work by 4.1 times higher than that of crankshaft internal combustion engine is proved, and compared with said machine, said machine is a 4-horsepower diesel engine produced by Zhejiang Tiancheng diesel engine plant, and its cylinder diameter and stroke are identical, and its rotating speed is identical, except the components related in the application, other components still adopt the original diesel engine components.

The explosive force is the main working power of the internal combustion engine, the working output power of the explosive force stage must be ensured to be high to greatly improve the output power, the working time of the explosive force of the internal combustion engine is very short, as can be seen from the first line of the list in fig. 31, the whole working stroke of the explosive force is only 0.85 mm, the crankshaft rotates by about 12 degrees, but the short explosion is a whole energy source for the internal combustion engine to work at one moment. The energy lost by the explosive force of the crankshaft internal combustion engine is proved in two steps, and in the first step, the useful component force output of the explosive force working is very low on the whole, 0.27 of an angle of 0-12 degrees is output from the top dead center, and the average output conversion rate is only 0.135. In the second step, in the very low output conversion rate, a large part of the rotation angles are performed at a very low work output conversion rate. As can be seen from the first row in fig. 31, when the crankshaft rotates from the top dead center 0 degree to about half 5.8 degrees of the 12 degrees, the explosion stroke only goes by 0.2 mm, the vertical line from the origin 0 to 0.85 of the ordinate in fig. 30 is the explosion stage of the crankshaft internal combustion engine, and 30-1 in fig. 30 is the explosion curve, and it can be seen from the graph that the closer the explosion curve is to the ordinate, the lower the pressure output value is, and when the explosion stroke goes by 0.2 mm in volume, the pressure rises by a small section of curve from the ordinate, but the crankshaft rotates by about half of the explosion stroke.

The principle that the output power of the explosive force moment doing work of the engine is improved by about 4.1 times compared with that of a crankshaft internal combustion engine is proved as follows: when the piston of the straight shaft internal combustion engine descends by 0.85 mm, the straight shaft rotates by 4.7 degrees, in order to compare with the straight shaft internal combustion engine, the explosion stroke of the crankshaft internal combustion engine is taken as a dividing point from 7.1 degrees, the front half part of the crankshaft internal combustion engine rotates by 0-7.1 degrees, the rear half part of the crankshaft internal combustion engine rotates by 7.1-12 degrees, the crankshaft internal combustion engine rotates by about 4.9 degrees, and the crankshaft internal combustion engine rotates by about the same angle as the rotation angle of the straight shaft internal combustion engine.

Firstly, the working condition of the crankshaft from 0-7.1 degrees is analyzed, the output conversion rate of useful component force is 0.16 when the crankshaft is at 7.1 degrees, the average output conversion rate of useful component force is 0.08 when the crankshaft is at 0-7.1 degrees, as can be seen from the first row and the second row of the list in fig. 31, the working stroke of piston explosive force at 7.1 degrees runs from 0 to 0.3 mm, the 0.3 vertical line on the right side of the ordinate is at the 0.3 mm stroke, as can be seen from 30-4 in fig. 30, the corresponding pressure point of the explosive force curve of the stroke can be seen from the ordinate, and rises from 1250 kg to about 1800 kg, the average pressure value is 1525 kg, and the average output conversion rate of useful component force is multiplied by 0.08, that is equal to 0.08, that is to

1525 multiplied by 0.08 is 122 kilograms, the average tangential force output value of the crankshaft from an angle of 0-7.1 degrees is very small, the crankshaft can do negative work due to explosive force in an ignition stage before the top dead center, the angle reaches about 20 degrees, and the negative work can be offset and balanced with the positive work done at the angle of 0-7.1 degrees. Therefore, the explosive force at an angle of 0-7.1 degrees after the top dead center of the crankshaft internal combustion engine can be ignored.

The work of the crankshaft from 7.1 to 12 degrees is analyzed, from fig. 31, it can be seen that the useful component output conversion rate at 7.1 degrees is 0.16, the output conversion rate at 12 degrees is 0.27, the tangential force of the crankshaft at 7.1 degrees is 1800 × 0.16 ═ 288, the tangential force of the crankshaft at 12 degrees is 4000 × 0.27 ═ 1080, the pressure point corresponding to the explosive force curve can be seen from the 30-3 ordinate in fig. 30, the pressure point rises from about 288 kilograms to 1080 kilograms, and the average pressure value is 1080 kilograms

1080+288/2 is 684 kg, i.e. the average tangential force output of the crankshaft from an angle of 7.1-12 degrees is 684 kg.

Analyzing the work of the straight shaft from 0-4.7 degrees, the tangential force output conversion rate of the straight shaft of the fuel oil in the explosion stage is an experimental data and is about 0.52, the distance between the peak of the duckbill wheel of the straight shaft and the shaft center is 43.5 mm and is 1.45 times of the crank length of the 4 horsepower diesel engine which is 30 mm, the power arm of the straight shaft is 1.2 times of the resistance arm, the useful component force output conversion rate is 0.52 multiplied by 1.45 multiplied by 1.2 which is 0.9, the output conversion rate is almost constant and is always equal to 0.9 due to the short stroke of the straight shaft in the fuel oil explosion stroke, the rotation angle of the straight shaft and the piston descending stroke are also approximately proportional, the explosion tangential force of the straight shaft at the vertical coordinate is 1250 multiplied by 0.9 which is 1125 kg, the explosion force of the straight shaft at 0.85 mm is 4000 multiplied by 0.9 which is 3600 kg, the corresponding pressure point of the explosion force curve can be seen from 30-2 vertical coordinate in the graph 30-2 kg, and can be increased from 1125 kg to 3600 kg, the average pressure value is 1125+ 3600/2-2925 kg, that is, the average tangential force output value of the straight shaft rotating by 4.7 degrees is 2925 kg, and then multiplied by 0.2 degrees which are less than the crank shaft, that is, multiplied by 4.7/4.9-0.96, and 2925 x 0.96-2808 kg.

2808÷684＝4.1

Therefore, the power of the straight shaft internal combustion engine in the fuel oil explosion stage is roughly 4.1 times of the work power of the crankshaft internal combustion engine. The actual explosion pressure volume is not as wide as the pressure volume between the origin 0 and 0 in the graph 30, if the compression of the pressure volume between 0 and 0 in the graph is narrowed, the power multiple of the straight shaft is further increased, so that the straight shaft internal combustion engine is more than 4 times of the work power of the crankshaft internal combustion engine in the fuel explosion stage.

From the working area, the area enclosed by the vertical line from the ordinate to the highest point of the explosion pressure of the curve 30-2 and the area enclosed by the vertical line from the 0.3 to the highest point of the explosion pressure of the curve 30-3 in the graph 30 can be roughly estimated, and the straight shaft working area is 4 times of the crankshaft working area.

The principle that the pressure work of the engine is improved by 1.39 times compared with the pressure work power of the crankshaft internal combustion engine is proved, the pressure work is a main work source of the crankshaft internal combustion engine, and the mechanical efficiency of the crankshaft internal combustion engine is further proved to be lost and the efficiency of the engine is improved by researching the pressure work. The crankshaft internal combustion engine also loses a large amount of energy due to useless component force in pressure work, the output efficiency is very low, the engine adopts a reasonable mechanical structure design, the useful work output is greatly increased, the rotating angle of an output shaft of the engine at the initial stage of fuel oil explosion is increased compared with that of the crankshaft internal combustion engine, and each data on a straight shaft at the stage is experimental data obtained through repeated experimental measurement and calculation.

For the convenience of demonstration, the applicant adds a horizontal line above the abscissa, see 30-7 in fig. 30, divides 6 equal parts between horizontal lines 0 and 6, and divides 6 equal parts for the piston 60 mm stroke, each equal part represents a stroke volume of 10 mm of the piston, the vertical line at 0 point on the horizontal line represents the boundary between the highest point of the explosion pressure and the work starting point of the subsequent pressure, the work stroke volume is between 0 and 5 on the horizontal line, the cylinder stroke volume of the exhaust valve opening to the bottom dead center is between 5 and 6 on the horizontal line, and the total volume of the explosion volume in the fuel explosion stage is between the coordinate origin 0 and the horizontal line 0. In fig. 30, the curve of the lower half section at the inflection point of the small circle of the 30-6 thick curve is a compression pressure curve, the actual compression pressure value is not so high, the curve of the upper half section at the inflection point of the small circle is an explosion pressure curve, the increase of the compression pressure is the negative work done by the inertia wheel of the internal combustion engine, the negative work is not removed temporarily for the convenience of calculation of the crankshaft and the straight shaft of the two internal combustion engines, and the actual pressure value of the internal combustion engine, which is increased to the highest point, is taken as the calculation basis, so that the power comparison of the two internal combustion engines is not influenced. The curve labeled 30-1 in fig. 30 is a burst pressure curve, the actual burst pressure being accomplished in a very small space, not as wide as in the figure, for the sake of convenience of analysis, the curve with small dots 30-2 in fig. 30 is a curve of 0.9 of the output conversion rate of the useful component of the explosive force of the straight-axis internal combustion engine, the curve with small dots 30-3 in fig. 30 is a useful component force output curve calculated by the formula T ═ P sin (a + β) for a crankshaft internal combustion engine, the coordinate line from the origin 0 to the pressure peak 4000 on the ordinate is also divided into five equal parts, the pressure increases by 800 kg for each equal part, the vertical line 0.3 to the right of the ordinate is at the stroke where the piston descends by 0.3 mm, see 30-4 in fig. 30, 30-5 in FIG. 30 is a P-V curve with inverse proportionality between pressure and volume for pressure work after explosive force is over.

It was confirmed that the whole is divided into two steps

The first step, from the demonstration of the piston descending distance in the cylinder and the output shaft rotation angle, the demonstration is divided into 3 steps again, in the first step, when the piston descends to 10 millimeters from the top dead center, the crankshaft rotates by 42.6 degrees, the piston descends by 0.85 millimeter and rotates by 12 degrees in the explosion removing stage, the crankshaft rotates by 30.6 degrees, the straight shaft rotates by 43.6 degrees, the straight shaft rotates by 38.6 degrees in the explosion removing stage, and the straight shaft rotation angle is greater than the crankshaft rotation angle. Secondly, when the piston descends to 20 mm from 10 mm, as can be seen from fig. 31, the straight shaft rotates to 74.6 degrees from 43.6 degrees, the straight shaft rotates to 31 degrees, the crankshaft rotates to 63 degrees from 42.6 degrees, and the crankshaft rotates to 20.4 degrees, so that when the pistons of the two engines descend to 20 mm at the initial stage of fuel explosion, the rotation angle of the straight shaft is greatly increased compared with that of the crankshaft. And thirdly, when the piston descends to the exhaust valve from 20 mm to open the exhaust valve to exhaust the exhaust gas, the crankshaft rotates from 63 degrees to 130 degrees, the crankshaft rotates 67 degrees, the straight shaft rotates from 74.6 degrees to 122 degrees, the straight shaft rotates 47.4 degrees, and the crankshaft rotates 19.6 degrees more than the straight shaft.

Second, proof of torque and power of straight shaft and crankshaft

For the sake of convenience of demonstration, a table is shown in fig. 31, in which the first row is the detailed values of the piston at 0.85 mm of the explosion stroke, the second row is the rotation angle of the corresponding point in the explosion stroke, the third row is the stroke point of the piston at every 2 mm drop, the stroke point at every 6 mm drop after 20 mm, the fourth row is the corresponding pressure value of the stroke point of the third row, the sixth row of the fifth row is the associated values of a, β angle in the rotation of the crankshaft, the seventh row is the pressure output conversion rate value at the time of the rotation of the crankshaft at angle a + β, the eighth row is the P-V curve in which the pressure and the volume are inversely proportional to each other in fig. 30-5, the calculated value of the useful component of t.p.sin (a + β), the ninth row is the value of the work of the moment of the crankshaft a ═ angle of the crankshaft rotation x a angle of the crankshaft at the fifth row, and the tenth row is the corresponding rotation angle of the piston at the stroke point of the third row in the table, the eleventh row is the moment arm multiple ratio of the straight shaft and the crankshaft, the moment arm of the crankshaft is 30 mm long and unchanged, the moment arm of the straight shaft is continuously shortened due to the fact that the moment arm is lowered along with the descending of the arc point under the swing arm, the moment arm length value is obtained from a corresponding value on the descending stroke point of the third row piston, the length from the contact position of the arc point under the swing arm and the duckbill wheel to the axis in the rotation of the straight shaft is obtained, and the twelfth row is the tangential force output conversion rate value of the straight shaft duckbill wheel, which is experimental data obtained from a prototype of the invention. The multiple ratio of the swing arm power arm to the resistance arm is small in numerical value change, the piston descends by 20 mm to serve as a dividing point, the piston is about 1.2 times before 20 mm, the piston is about 1.18 after 20 mm, the piston is not listed in a table any more, and the thirteenth straight shaft torque is the fourth row stroke point pressure multiplied by the straight shaft output conversion rate multiplied by the moment arm multiple of the swing arm power arm to the resistance arm compared with the crankshaft. The fourth row, i.e., the straight-axis moment work, is multiplied by the straight-axis rotation angle of the tenth row, and the 15 th and 16 th rows are multiplied by the straight-axis work and the area.

The table shows various detailed data of the crankshaft and the straight shaft in explosive force and pressure work, and the table shows that the straight shaft internal combustion engine after the swing arm and the duckbill wheel comma-shaped cam combination rotates in a matched mode has great change in all aspects of operation data and the crankshaft internal combustion engine, the torque work is greatly improved compared with the crankshaft internal combustion engine, the angular torque work of the crankshaft internal combustion engine a in the table can be 102049 joules through addition calculation, the torque work of the straight shaft internal combustion engine can be 141813 joules through addition calculation, and the torque work of the straight shaft and the crankshaft internal combustion engine is 141813/102049 times as 1.39 times compared with that of the crankshaft internal combustion engine.

Therefore, the power of the straight shaft internal combustion engine in the pressure working stage is 1.39 times of the working power of the crankshaft internal combustion engine.

From the working area, the area enclosed by the thick curve representing the direct shaft work in fig. 32 can be roughly estimated to be 1.39 times of the crankshaft power area compared with the area enclosed by the broken line representing the crankshaft work.

Compared with the explosive power and the pressure power, the direct-axis internal combustion engine is increased by about 4.1 times and 1.39 times respectively compared with the crankshaft internal combustion engine, so that the output power of the direct-axis internal combustion engine is increased by 4-6 times compared with the output power of the comprehensive two engines.

The key technical problems of the swing arm type two-stroke straight shaft internal combustion engine are completely solved, along with the promotion of a straight shaft high-efficiency internal combustion engine with simple structure and easy modification, the automobile market which is undergoing drastic change has a new permutation and combination, and the methanol gasoline fuel internal combustion engine automobile can occupy the mainstream status in various automobile fields.

The invention has the following beneficial effects:

1. at the moment of fuel oil explosion at an angle of 0-12 degrees at a top dead center, the output conversion rate of the crankshaft internal combustion engine is increased from 0 to 27 percent, the average output conversion rate of useful component force is 13.5 percent, the output conversion rate of the engine is always about 90 percent, the work power of the engine is about 4.1 times that of the crankshaft internal combustion engine, and in the pressure work stage after the explosive force of the fuel oil is finished, the work power of the engine is increased by 1.39 times again compared with that of the crankshaft internal combustion engine, and the power of the engine is increased by 4-6 times compared with that of the crankshaft internal combustion engine with the same volume.

2. Because the cylinders on the case are arranged in a V shape and a triangle shape, when the duckbill wheel comma-shaped cam of one unit on the straight shaft rotates for one circle, the fuel oil of the cylinder is driven to explode for 4 times and six times, the output power is obviously increased, the weight of the engine body is reduced by 4-6 times, and a wide space is provided for realizing the miniaturization and the light weight of a high-power engine.

3. The V-shaped machine type and the triangular machine type of the engine are simple in structure, the production process of the multi-cylinder internal combustion engine is greatly reduced, the manufacturing price is reduced by 4-6 times, and the engine is transformed on the basis of the traditional internal combustion engine, only a part of parts of the traditional internal combustion engine are required to be changed, so that the transformation is easy, and the transformation cost is low.

4. The rotating angle of the explosion angle of the machine, the length of the force arm and all parts on the machine can be further changed and improved on the premise of improving the mechanical efficiency, so that the efficiency of the machine still has a space for improving.

5. The efficiency of the engine is greatly improved, the output power is increased, the oil consumption of a car in hundred kilometers is only about two liters, the use amount of gasoline can be reduced to the negligible degree if methanol gasoline is used, the oil consumption can be greatly reduced after all equipment needing power is refitted into the internal combustion engine, and the problem of high petroleum energy inlet pressure in China is thoroughly solved.

6. Compared with the crankshaft internal combustion engine with the same capacity, the efficiency is greatly improved, fuel oil is greatly saved, tail gas emission is greatly reduced, and waste gas emission pollution is reduced to a negligible degree.

7. The duckbill wheel comma-shaped cam on one unit straight shaft of the engine can replace 4-6 cranks on a crankshaft, so that a large number of processes for manufacturing the crankshaft are reduced, a plurality of bearing bush parts which are easy to damage in a crankshaft internal combustion engine are removed, a large number of precise manufacturing and complex bearing bush scraping work are reduced, the failure rate of the internal combustion engine is greatly reduced, and the service life of the engine is prolonged.

8. The intake and exhaust system simplifies a whole set of devices of the exhaust system, and one intake cam on one to two unit straight shafts can replace 4 to 12 intake cams on the crankshaft internal combustion engine, so that half parts such as rocker arms and the like in the intake system are simplified, the manufacturing and installation processes are greatly simplified, the failure rate of the machine is reduced, the loss of useful power is further reduced, and the production cost is reduced by 4 to 6 times.

9. The compression ratio can be further increased, so that the efficiency of the machine is further improved.

10. The invention integrates all the advantages of the 2-stroke and 4-stroke crankshaft internal combustion engines, overcomes the defects of low output efficiency and incapability of improving the efficiency, inherits the advantages of small size, light weight and large output power of the rotor engine, has stronger output power compared with the rotor engine, greatly reduces the oil consumption, and promotes the development of the internal combustion engine to the advanced field by using advanced technologies such as direct injection in a cylinder, air pressurization and the like due to the specific structure of the engine.

Drawings

FIG. 1 is a schematic diagram of a prior art crankshaft internal combustion engine cylinder piston connecting rod crank configuration,

FIG. 2 is a P-V indicator diagram and a P-theta pressure crank angle diagram of an automotive 4-stroke engine downloaded from the Internet,

FIG. 3 is a diagram of the conversion rate of useful force component output at an angle of 10-63 degrees for a crankshaft internal combustion engine,

figure 4 is an experimental plot of the valve stem spring distance at the striking force of the spring many times greater than the spring force,

figure 5 is a schematic view of a swing arm and side arm slider,

figure 6 is a schematic straight axis view of the duckbill wheel and comma cam combination,

FIG. 7 is a schematic structural diagram of a single-cylinder one-unit model, a swing arm side arm slide block and a duckbill wheel comma-shaped cam on a straight shaft which are matched with a unit and an air inlet and oil injection system,

FIG. 8 is a schematic view showing the structure of the intake cam engaged with the intake rocker arm through the rocker push rod and the structure of the injection cam engaged with the injection valve,

figure 9 is a schematic diagram of the duck bill wheel arc segment vertex contacting the lower arc point of the swinging arm when the swinging arm 1 on the left side is at the 45 degree angle of the duck bill wheel arc vertex at the top dead center, and the duck bill wheel 2 on the right side is rotated by 43.6 degrees when the swinging arm 2 on the right side is descended by 10 millimeters,

figure 10 is the diagram of duckbilled wheel left circular arc section summit contact duckbilled wheel lower circular arc point when duckbilled wheel circular arc summit has rotated 74.6 degrees when swing arm 1 on the left side descends 20 millimeters and swing arm 2 on the right side in the figure descends 50 millimeters when swing arm internal teeth contact the duckbilled wheel duckbilled.

Fig. 11 is a schematic diagram of the left side oscillating arm 1 with the internal teeth reaching the duckbill wheel circular slideway oscillating arm and stopping at the bottom dead center, and a schematic diagram of the right side oscillating arm 2 with the side wall slide block and the comma cam circular slideway contact gap of 0.2 mm.

FIG. 12 is a schematic diagram showing the upper piston ring of the piston descending to the upper side of the exhaust hole on the side wall of the cylinder, and the structure of the air inlet cam on the straight shaft pushing the valve stem to open the air inlet valve through the swing sheet push rod and the upper rocker arm.

Figure 13 is the arc part of the comma cam begins to contact the arc slideway of the side arm of the swing arm 1 on the left, the swing arm begins to rise and the arc point of the lower end of the swing arm 2 on the right in the figure rises to the top point of the right end of the arc slideway on the right half of the duckbill wheel to be contacted,

figure 14 is a schematic view of the structure of a two-cylinder one-unit V-type,

FIG. 15 is a schematic structural diagram of a structure that an air inlet cam on a straight shaft pushes two sets of swing pieces on a swing frame, then an air inlet valve is pushed to be opened and closed through a push rod and an upper rocker arm, an air exhaust hole on the side wall of an air cylinder is connected with an exhaust pipe on the outer side wall of the air cylinder, and the exhaust pipe rises,

figure 16 is a schematic structural diagram of oil supply of an oil injection cam on a straight shaft pushing a swing block on a swing frame and then pushing an oil injection valve,

FIG. 17 is a schematic structural diagram of the structure that the lower arc point of the swing arm 1 on the left side in the figure is contacted with the top point of the left arc section of the duckbill wheel, the sliding section of the middle part of the comma-shaped cam on the straight shaft is contacted with the right top point of the arc sliding section of the side arm of the swing arm 2, the internal tooth in the middle part of the front end of the swing arm 1 on the right side in the figure is cut into the arc section of the duckbilled top of the duckbilled wheel, and the right arc section of the duckbilled wheel pushes the lower arc point of the swing arm 2 to enable the piston to rise to the upper stop point,

FIG. 18 is a schematic structural diagram of the piston in the cylinder 1 descending to the bottom dead center, the comma-shaped cam circular slideway on the straight shaft contacting the arc slideway on the side wall of the swing arm 1, and the piston 2 descending to about 10 mm from the top dead center pushed by the oil explosion in the cylinder 2,

FIG. 19 is a schematic diagram showing the structure that the slide section in the middle of the comma-type cam on the left side is contacted with the left-side tail part of the slide block on the side wall of the swing arm 1, the internal tooth in the middle of the front end of the swing arm 2 is cut into the duckbill of the duckbill wheel, the slide section in the middle of the comma-type cam on the right side is contacted with the slide block in the left-side position in the middle of the slide section on the side wall of the swing arm 1, the swing arm 2 descends to the lower dead point, and the contact difference between the slide section in the middle of the slide section on the side wall and the comma-type cam is 0.2 mm,

FIG. 20 is a schematic view showing the construction of an oil supply system of a three-cylinder one-unit cylinder vertical type in which an injection cam on a straight shaft pushes three oscillating blocks and an injection valve which are formed at an angle of 120 degrees with each other,

FIG. 21 is a schematic view showing a three-cylinder one-unit cylinder vertical type air intake system, in which an air intake cam on a main shaft pushes three swing pieces forming an angle of 120 degrees with each other, respectively, and a push rod on the swing piece pushes three upper rocker arms to open and close an air intake valve,

FIG. 22 is a schematic view showing the configuration of a chassis and the internal structure of a vertical type machine with three cylinders and one unit cylinder, wherein the piston in the cylinder 1 is at the top dead center, the piston in the cylinder 2 is at the position 20 mm above the bottom dead center, and the internal teeth at the middle part of the front end of the swing arm 3 corresponding to the lower part of the piston in the cylinder 3 start to cut into the duckbill part of the duckbill wheel,

FIG. 23 is a schematic structural diagram of the drawing in which the lower arc point of the left swing arm 1 contacts the top of the left end of the left arc slide section of the duckbill wheel, the middle slide section of the comma cam on the straight shaft contacts the top of the right side of the arc slide section of the side arm 2, the arc slide section behind the circular slide section of the comma cam at the position of the swing arm 3 starts to gradually contact the side wall slide block of the swing arm 3, the right side of the drawing is a schematic structural diagram of the middle internal tooth of the front end of the swing arm 1 cutting into the duckbill of the duckbill wheel, the lower arc point of the swing arm 2 is about to reach the arc top of the duckbill wheel, and the tail part of the side wall slide block of the swing arm 3 contacts the middle slide section of the comma cam,

FIG. 24 is a schematic structural view showing that a middle sliding section of a comma-shaped cam of a three-cylinder one-unit cylinder vertical type machine is in contact with the left-side tail part of a sliding block on the side wall of a swing arm 1, internal teeth in the middle of the front end of the swing arm 2 start to cut into the duckbilled part of a duckbilled wheel, and a lower arc point of the swing arm 3 reaches the arc vertex of the duckbilled wheel,

FIG. 25 is a schematic diagram showing the structure that the vertex of the right end of the side wall slide block of the swing arm 1 on the left side contacts the slide section at the middle part of the comma-shaped cam, the slide section at the middle part of the comma-shaped cam contacts the tail part of the side wall slide block of the swing arm 2, and the lower arc point of the swing arm 3 runs to the vertex of the left end of the left arc section of the duckbill wheel, and the right side is a schematic diagram showing the structure that the lower arc point of the swing arm 1 runs to the oil injection section of the right arc section of the duckbill wheel, the vertex of the left end of the side wall slide block of the swing arm 2 contacts the slide section at the middle part of the comma-shaped cam, and the internal teeth at the middle part of the front end of the swing arm 3 start to cut into the arc section at the duckbill position of the duckbill wheel,

figure 26 is a schematic view of the internal structure of a four-cylinder two-unit V-type,

figure 27 is a schematic diagram of the structure of the inlet and outlet ports of a four cylinder two unit V-shape type,

FIG. 28 is a structural diagram of a triangle model with a horizontally placed triangular machine body, wherein a bottom layer unit and a 28-3 intake cam swing system in FIG. 28 form a triangle horizontal unit model, a lower layer unit model and an upper layer unit of 28-4 in FIG. 28 form a structural diagram of a triangle model with a horizontally placed 6 cylinder and a second unit,

FIG. 29 is an external view of a machine case of a two-cylinder one-unit type, in which the lower half is an external view in the axial direction of the machine case and the upper half is a left-hand view of the lower half, which is a view suitable for all unit types of the present invention;

fig. 30 is a schematic diagram of the fuel explosion force curve and the pressure curve P-V.

Figure 31 is a schematic diagram of a detailed data list of explosive and pressure rotation angles and work,

fig. 32 is a comparison of the crankshaft pressure work area and the straight shaft work area, and the small dots on the two curves respectively represent a stroke point of every 2 mm of piston descending and a stroke point of every 6 mm of piston descending after 20 mm.

Detailed Description

First embodiment of swing arm type two-stroke straight-shaft internal combustion engine

The embodiment is a single-cylinder one-unit internal combustion engine, the specific structure is shown in figure 7, and the single-cylinder one-unit internal combustion engine is composed of a duckbill wheel comma-shaped cam combination body, shown in figure 7 as 7-8, and a side arm slide block type swing arm, shown in figure 7 as 7-5, to form a matching unit, a piston in a cylinder is connected with the front end of the side arm slide block type swing arm through a connecting rod by a steel pin, the rear end of the swing arm is connected with the side wall connection position of a case by a steel pin, shown in figure 7 as 7-3, the front end of the side wall slide block type swing arm is rotationally matched with the duckbill wheel comma-shaped cam, shown in figure 7 as 7-6, the piston in the cylinder reciprocates up and down, a stabilizing spring is arranged on the swing arm, shown in figure 7-2, the upper end of the spring is fixed on the case on the outer wall of the cylinder, shown in figure 7 as 7, an internal tooth is arranged in the middle part of the front end of the swing arm, shown in figure 5-7, the internal tooth is matched with an arc sliding section at the duckbill position on the duckbill wheel, 10-2 in figure 10, the lower part of the front end of the swing arm is provided with an arc point, 5-8 in figure 5, the arc point is provided with a small arc section, 9-2 in figure 9 is enlarged, the lower side of the slide block of the side wall slide block of the swing arm is provided with an arc slide way, 5-9 in figure 5, the horizontal line of the center of the connecting hole at the rear end of the swing arm is provided with an included angle with the connecting line of the arc point at the lower part of the swing arm, 5-3 in figure 5, the connecting hole circle center at the upper part of the front end of the swing arm to the circle center point of the connecting hole at the rear end of the swing arm is provided with an included angle with the connecting line of the arc point at the lower part of the swing arm, 5-1 in figure 5, the combination body of the duckbill wheel and the comma-shaped cam is arranged on a straight shaft, 7-8 in figure 7, the slide way at the top of the duckbill wheel is divided into a left slide section and a right slide section by the arc vertex, 6-1 and 6-6, the arc section of the arc vertex of the duckbill wheel which is vertical to the shaft center, see the enlarged part 6-5 in figure 6, the duckbilled part of the duckbilled wheel is a smaller arc-shaped sliding section, 6-2 in figure 6, a transition arc-shaped sliding section is arranged between the small arc-shaped sliding section and the circular sliding section, 6-3 in figure 6, the circular sliding section is shown as 6-4 in figure 6, the working surface part of the comma-shaped cam is a larger arc-shaped sliding section, 6-7 in figure 6, an air inlet cam and an oil injection valve cam are further arranged on a straight shaft, see 8-9 and 8-10 in figure 8, the lower end of the cylinder is provided with a left exhaust hole and a right exhaust hole which are communicated with the exhaust holes of the chassis and are connected with the exhaust pipeline of the outer wall of the chassis, the exhaust pipeline of the chassis belongs to the prior art of the internal combustion engine and is not described in detail, the right side of the middle lower part of the cylinder in figure 7 is provided with an exhaust hole, see 7-4 in figure 7, the exhaust hole on the left side is symmetrical to the exhaust hole in figure 7-4, see fig. 27, the opening and closing of the air inlet valve is completed by the air inlet cam on the straight shaft pushing the air inlet valve through the swing sheet push rod and the upper rocker arm, see 8-9, 8-5, 8-3 and 8-2 in fig. 8, the air inlet is compressed air entering the air cylinder through the air inlet on the cylinder cover, see 8-1 in fig. 8, the swing sheet and the swing block are installed on the swing frame through the shaft pin, the swing frame is installed on the side wall of the left case on the right side in fig. 8, see the section of the right side 8-4 in fig. 8, the oil supply system also pushes the oil injection valve through the swing block through the oil injection cam on the straight shaft, and then supplies oil to the oil injection nozzle on the cylinder cover through the oil pipe, see 8-10, 8-7 and 8-6 in fig. 8, the oil pipe and the oil injection nozzle belong to the prior art, and the detailed description is omitted, and the inertia wheel is larger than the inertia wheel of the crankshaft internal combustion engine with the same power, see 7-7 in FIG. 7.

The technical scheme of the embodiment is as follows, the engine parts in the embodiment are improved on the basis of a 4-horsepower diesel engine in Changzhou province in Zhejiang province, the axial width of a case is 150 mm, the diameter of a straight shaft is 30 mm, when viewed from the left side in figure 7, the inner wall of the left side of the case is 25 mm to a duckbill wheel, the width of a comma-shaped cam combination body of the duckbill wheel is 40 mm, the comma-shaped cam is 25 mm to an air inlet cam and an oil supply cam, the width of the air inlet and oil supply cam is 25 mm, the duckbill wheel is 25 mm to the inner wall of the right side of the case, the distance from the circle center of a connecting hole at the upper part of the front end of a swing arm to the circle center of a connecting hole at the rear end of the swing arm is 165 mm, as shown in dotted lines of two holes of 5-6 and 5-3 in figure 5, the center of the connecting hole at the upper part of the front end of the swing arm is 30 mm to the end point of an inner tooth, the circle center of the upper connecting hole at 50 mm to the arc point at the lower part of the swing arm, and the included angle of the connecting line of the horizontal line of the lower arc point at the rear end of the swing arm is 3.7 degrees, see 5-3 in FIG. 5, the line connecting the circle center of the connecting hole at the upper part of the front end of the swing arm to the circle center of the connecting hole at the rear end of the swing arm, the dotted line, and the arc point at the lower part of the swing arm forms an included angle of 15 degrees, see 5-1 in FIG. 5, the length difference between the power arm and the resistance arm of the swing arm, see 5-5 in FIG. 5, the length of the power arm is 170 mm, the length of the resistance arm is 142 mm, and the power arm is 1.2 times of the resistance arm. The swing arm has a small arc section of an arc point at the lower part of the swing arm of 5 mm, the small arc section is enlarged at the position 9-2 in figure 9, the swing arm has a thickness of 20 mm, the lower part of a steady spring is connected, the center point of the steady spring is 60 mm to the center of a connecting hole at the upper part of the front end of the swing arm, the total length of the spring is 210 mm, the spring is 7-2 in figure 7, the compression elasticity is 5-8 kg, the arc length of an arc slideway at the lower side of a side wall slide block of the swing arm is 35 mm, the chord height is 15 mm, the spring is 5-9 in figure 5, the thickness is 18 mm, the included angle between the connecting line from the axle center of a duckbill wheel to the arc vertex and the vertical line of the axle center is 45 degrees, the arc vertex of a duckbill wheel is at the position 45 degrees in figure 6, the arc vertex of 6-5 in figure 6, the radius from the axle center of the duckbill wheel to the arc vertex is 43.5 mm, the left arc sliding section at the top of the duckbill wheel is 30 mm, the right arc sliding section is 35 mm, the vertex of the arc sliding section, the vertex tangent line of the left arc section is 25 degrees between the horizontal line at the vertex, see angle 25 in figure 6, duckbilled arc slide length 5 mm, see 6-2 in figure 6, transition arc slide length 8 mm, circular slide radius 20 mm, duckbilled wheel width 20 mm, comma cam working surface arc slide length 50 mm, chord height 15 mm, width 18 mm, intake cam diameter 35 mm, cam vertex height 8 mm, width 10 mm, rocker length 70 mm, width 22 mm, rocker shaft pin hole 8 mm, rocker length 60 mm, oil supply cam diameter 35 mm, cam height 10 mm, width 18 mm, rocker length 45 mm, rocker block bearing inner diameter 12 mm, outer diameter 28 mm, width 8 mm, cylinder lower end side wall 2 exhaust holes, the exhaust hole is rectangle, height 10 mm, width 22 mm, inertial wheel weight 8.5 kg.

Second embodiment

The present embodiment is a two-cylinder one-unit model, and the machine parts used are the same as those in embodiment 1, and the differences are as follows: the device is designed on the basis of an equilateral triangle, the specific structure is shown in figures 14 and 29, a base is arranged on the bottom edge of the triangle, a cylinder is respectively arranged on two oblique edges, the cylinder 1 and the cylinder 2 in figure 14 are shown, the cylinder is arranged at the position where the vertical center line of the oblique edge is deviated to the right clockwise, the included angle between the center line of each cylinder and the vertical center line of the bottom edge of the triangle is 60 degrees, a side arm slider type swing arm is correspondingly arranged below each cylinder, the number of the corresponding swing arms below each cylinder is several, the number of the corresponding swing arms below the cylinder 1 in figure 14 is 14-2, the number of the corresponding swing arms below the cylinder 2 is 14-5, the upper connecting hole at the front end of each swing arm is connected with a connecting rod, the bottom at the right side of the cylinder 1 is the position where the rear end of the swing arm 2 is connected with a machine body, the rear end of the swing arm 1 is connected with the machine base in figure 14-1, the rear end of the machine case is 14-3 in figure 14, the left side view of the upper half part of figure 29, the center point of the triangle is the position of a straight shaft of a duckbill wheel comma-shaped cam complex, 14-4 in figure 14, a duckbill wheel comma-shaped cam complex and two side arm sliding block type swing arms on the straight shaft form a matching unit, the straight shaft rotates for a circle, the duckbill wheel and the comma-shaped cam are respectively in contact fit with the two swing arms sequentially, fuel in two cylinders on a case respectively explodes once through six intermittent contact points, and a set of duckbill wheel comma-shaped cam on the straight shaft replaces 4 cranks on a crankshaft, so that a large number of processes for manufacturing complex crankshafts are reduced. The explosion interval of the fuel oil of the two cylinders is that the cylinder 2 starts to explode when the explosion stroke of the cylinder 1 is finished, and the two explosion strokes do not overlap, so that the output efficiency is exerted to the maximum extent.

The improvement makes one cam of the engine replace 4 cams of a crankshaft internal combustion engine, and a camshaft and a transmission system are omitted. The oil supply system also pushes the swing block on the swing frame to push the oil injection pump through the oil injection cam on the straight shaft to supply oil to the oil injection nozzle on the cylinder cover, the oil injection cam is shown as 16-1 in figure 16, the swing block is shown as 16-2 in figure 16, the swing piece and the swing block are arranged on the same swing frame, and the difference between the two sets of swing frames is 120 degrees. The speed regulating system is that a speed regulator is arranged on a straight shaft on the outer wall of the right side of the case, a hole is drilled on the side wall of the case, the oil supply amount of the two oil injection pumps is controlled by a link rod,

the left and right cases of the two cylinders are respectively provided with two exhaust holes, the two exhaust holes are used for exhausting outwards through the side wall of the case, the two exhaust holes on each side of the case are connected together through an exhaust pipe and send waste gas outwards, the exhaust pipe on the right side is shown as 15-4 in figure 15, the exhaust hole on the left side is shown as the left and right cylinder exhaust holes of the two-unit type 27, and the exhaust hole on the lower side of the cylinder is directly communicated with the outside through the exhaust pipe of the case, so that the exhaust pipe is lifted up by 15-4 in figure 15 after being connected with the case, and lubricating oil in the case is prevented from leaking outwards through the exhaust pipe.

Third embodiment

The present embodiment is a 3-cylinder one-unit model, and the machine parts used are those of embodiment 1, which are different in that: the triangle type is also designed on the basis of an equilateral triangle, the triangle type unit type air cylinder is vertically arranged, see figure 22 and horizontally arranged, see figure 28, the rotation matching relationship of the duckbilled wheel swing arm when the triangle type unit air cylinder is horizontally arranged is completely the same as that when the triangle type unit air cylinder is vertically arranged, only the speed regulating system and the V type speed regulating system when the triangle type unit air cylinder is vertically arranged are basically the same, the speed regulators are arranged on the outer straight shaft at the right side of the case, a hole is drilled on the side wall of the case, the oil supply amount of the oil injection pump is controlled through the link rod, when the triangle type unit type air cylinder is vertically arranged, the oil injection part is shown in figure 20, and the air intake system is shown in figure 21.

The structure diagram of the triangle model body is horizontally arranged, the bottom layer swing arm is matched with a duckbill wheel in figure 28, the middle air inlet system is shown as 28-3 in figure 28, the vertical triangle model body is horizontally arranged on the basis of the triangle three-cylinder one-unit vertical arrangement model body, because an air outlet in an air cylinder is directly communicated with an air outlet pipe outside a chassis, the vertical triangle model body is shown as 26-1 and 26-3 in figure 26 in a v-shaped model body, when the triangle model body is horizontally arranged, engine oil in the model body can flow out along the air outlet, therefore, when the triangle model body is horizontally arranged, the air outlet hole is changed into the position of which air outlet hole is arranged under 28-2 in figure 28, the triangle bottom part of the chassis is totally closed to prevent oil leakage, the bottom layer one unit in figure 28 and the 28-3 air inlet cam swing piece system in figure 28 form a triangle horizontal one model unit, each swing piece in 28-3 in figure 28 pushes an air inlet valve to work through a push rod, when the triangular one-unit type cylinder is horizontally placed, the speed-regulating oil supply system adopts a high-pressure common rail mode.

The triangle is vertical and the same with the horizontal type, three sides of the triangle are respectively provided with a cylinder, see the cylinder 1, the cylinder 2 and the cylinder 3 in figure 22, the three cylinders form an angle of 120 degrees at the position of the vertical central line of the bevel edge which is clockwise and deviated from the right, the lower part of each cylinder is connected with a side arm slide block type swing arm through a piston, the number of the corresponding swing arms below the cylinder is several, and the rear end of each swing arm is connected with the bottom of the right side of the last cylinder. The straight shaft of the duckbilled wheel comma-shaped cam combination is arranged at a vertical center point of a triangular plane, the straight shaft rotates for a circle, the duckbilled wheel and the comma-shaped cam are respectively contacted and matched with the three swing arms one time after another, and through nine intermittent contact points, 3 cylinders on the case explode one time respectively, and the duckbilled wheel comma-shaped cam combination explodes 6 times compared with a crankshaft internal combustion engine which explodes 1 time in two weeks in a four-stroke cylinder.

The intake cam on the main shaft respectively pushes three sets of rocker arm systems which form an angle of 120 degrees with each other to open and close the intake valve, as shown in figure 21, each intake valve works once when the straight shaft rotates for a circle, and the improvement ensures that one intake cam of the engine replaces 6 cams of a crankshaft internal combustion engine, and simultaneously, a great number of manufacturing processes such as a camshaft, a transmission system and the like are omitted. The oil supply system also respectively pushes three swing blocks and an oil injection pump which form an angle of 120 degrees with each other through an oil injection cam on the straight shaft, oil is respectively supplied to oil injection nozzles on a cylinder cover through oil pipes, the straight shaft rotates for a circle and each oil injection pump works once, the improvement saves a large amount of manufacturing processes of the oil supply system, the horizontally placed machine type oil supply system adopts a high-pressure common rail oil supply mode in the prior art, belongs to the prior art and is not described in detail.

The high-pressure fan supplies air to three air cylinder air inlets simultaneously, a triangle unit air cylinder is vertically placed in a model type, the air exhaust mode is approximately consistent with that of a two-cylinder one-unit model type, when the triangle model is placed horizontally, the air exhaust holes are changed into the positions which are 28-2 in the figure and are located below the air exhaust holes, the air exhaust holes are located at the right side of the right side face of a machine box and are in a horizontal plane with a swing arm, the other air exhaust holes are located at the right side of the right side face of the machine box, 6 air exhaust holes are located at the upper side and the lower side, 3 exhaust gases are connected together and are sent outwards, because the air exhaust holes in the air cylinder are directly communicated with the air exhaust pipes outside the machine box, a lifting process is arranged behind the air exhaust pipe connected with the machine box to prevent lubricating oil in the machine box from flowing outwards, and a bearing with a straight shaft assembled at the bottom of the triangle is totally closed in the machine box to prevent the lubricating oil in the box from leaking.

Fourth embodiment

This embodiment is of a four-cylinder two-unit V-type, using the same machine elements as in the two-cylinder one-unit embodiment 1, except that: the engine is characterized in that a unit is added on the basis of two cylinders and one unit, 4 cylinders are provided in total, the engine is equivalent to an eight-cylinder four-stroke crankshaft internal combustion engine, the specific structure is shown in figure 26, figure 27, two sets of duckbill wheel comma cams on a straight shaft replace 8 cranks on the crankshaft, a large number of processes for manufacturing complex cranks are reduced, 4 side wall sliding block type swing arms of a two-unit V-shaped engine are respectively arranged on two sides of the straight shaft in a case in a group, figure 26-4 and figure 26-9 in figure 26, the stress capacity of the straight shaft is enhanced because the combined installation position of the two duckbill wheel comma cams is close to two side walls of the case, the arc vertex of the duckbill wheel is at an angle of 45 degrees, the normal impact force transmitted to the straight shaft by fuel burst force is far smaller than the stress of the crankshaft, a reinforcement measure is not needed in the middle of the straight shaft, and the manufacturing process is reduced.

The bottom seat of the swing sheet frame is arranged at the middle position of the case, see 26-2 in figure 26, the cam on the straight shaft pushes 4 push rods on two swing sheets to respectively push 4 upper rocker arms on two cylinder covers to work through a middle through hole of two cylinders and a middle through hole of the cylinder cover, so that an exhaust valve is opened and closed, see 26-7 and 26-5 in figure 26 and 27-8 in figure 27, the swing sheets are arranged at the top end of a cylinder and are fixed on the case through the cylinder bottom seat, see 27-4 in figure 27, and the improvement enables one cam of the engine to replace 8 cams of a crankshaft internal combustion engine, thereby saving a large number of processes for manufacturing and installing a cam system.

27-1 and 27-6 in FIG. 27 are the positions of the intake ports, two intake ports of 27-6 are on the right bottom surface of the cylinder head, 26-6 in FIG. 26 are the steady spring baffles, and the dotted lines in the middle of the baffles are the inner spring rods. The exhaust part is exhausted by 6 exhaust ports at the lower part of 4 cylinders, 26-1 in figure 26 is that two exhaust holes at the lower sides of two cylinders close to the middle part are combined into one, and the exhaust is exhausted outwards through one exhaust hole on a chassis, 26-10 in figure 26 is a flange interface of the exhaust hole at the middle part of the other two cylinders, 4 exhaust holes at the outer side wall of the chassis are shown as 27-2 and 27-5 in figure 27, 27-3 and 27-7 in figure 27 are flanges of the interface of the middle exhaust hole, 4 exhaust holes at two outer sides are connected together by two exhaust pipes at each side for exhausting outwards, the structure is referred to 15-4 in figure 15, 2 exhaust holes at the middle position are respectively connected on the exhaust pipes at the outer sides for exhausting outwards, the exhaust mode omits the whole set of rocker arm type exhaust system on the crankshaft internal combustion engine, and the manufacturing process is greatly simplified, the oil supply mode adopts a high-pressure common rail mode in the prior internal combustion engine technology to supply oil to 4 cylinders.

Compared with the technical scheme of the machine parts added in the embodiment 1, the technical scheme of the machine parts comprises the following steps: the axial width of two outer walls of the case is 240 mm, the diameter of a straight-axis duckbill argument is 35 mm, the diameter from the right side inner wall of the case to the right duckbill wheel in fig. 26 is 25 mm, the width of a comma-shaped cam combination of the duckbill wheels is 40 mm, the width of the comma-shaped cam combination to the air inlet cam is 25 mm, the width of the air inlet cam to the left side comma-shaped cam combination is 25 mm, the width of the comma-shaped cam combination of the duckbill wheels is 40 mm, the width of the comma-shaped cam combination to the left inner wall of the case is 25 mm, the thickness of two walls of the case is 15 mm, the diameter of a cylinder for installing the swinging piece is 35 mm, the length of the cylinder is 90 mm, the width of the swinging piece is 30 mm, the diameter of the push rod is 7 mm, and the length is 240 mm.

Fifth embodiment

The present embodiment is a triangular six-cylinder two-unit model, the used machine parts are the same as those in embodiment 1 and embodiment 4, the different parts are that the machine body is vertically and horizontally placed, the vertically placed model is that a unit is added on the basis of the triangular one-unit vertical model, the arrangement sequence of the duckbilled wheel comma cam on the internal structure straight shaft, the side wall slide block swing arm and the middle position cam is consistent with the structure in the V-type two-unit model, every three of the six swing arms and the side wall slide blocks are respectively installed on two sides of the straight shaft in the machine case as a group and are matched with the duckbilled wheel comma cams on two sides of the straight shaft, because the installation positions of the two duckbilled wheel comma cam combinations are close to the two side walls of the machine case, the stress capacity of the straight shaft is enhanced, and the arc vertex of the duckbilled wheel is at an angle of 45 degrees, the normal force transmitted to the straight shaft by the fuel oil burst force is far smaller than the stress of the crank shaft, no reinforcement is required in the middle of the straight shaft. The swing sheet frame base is installed in the middle of the case, the air inlet cam on the main shaft respectively pushes three sets of rocker arm systems which form an angle of 120 degrees, so that the air inlet valve is opened and closed, 6 air outlets on two sides of 6 cylinders are connected together by an exhaust pipe to exhaust outwards for 3 air outlets on each side, corresponding 3 air outlets in the middle are connected together on 3 exhaust pipes on the outer side by the exhaust pipe to exhaust outwards, and the oil supply system adopts a high-pressure common rail mode.

The 6-cylinder two-unit horizontal placement machine model is characterized in that a unit is added on the basis of a 3-cylinder one-unit horizontal placement machine model, as shown in 28-4 in figure 28, 6 cylinders are totally used, the engine is equivalent to a 12-cylinder four-stroke crankshaft internal combustion engine, 12 cranks on a crankshaft are replaced by two sets of duckbill wheel comma-shaped cams on a straight shaft, a large number of processes for manufacturing complex cranks are reduced, the volume of a machine body is greatly reduced, the weight of the machine body is reduced by 4-6 times, the oil explosion interval of the internal combustion of the 3 cylinders is that when the explosion stroke of each cylinder is completed, the second cylinder starts to explode, no overlapping part exists between 3 explosion strokes, the output efficiency is exerted to the maximum extent, 6 side wall type swing arms are respectively arranged on two sides of the straight shaft in a machine case in a group, the 6 side wall type swing arms are matched with the duckbill wheel comma-shaped cams corresponding to two sides of the straight shaft, and the installation positions of two duckbill wheel comma-shaped cams are close to two side walls of the machine case, the stress point of fuel oil explosion is close to the side wall of the case, and the stress capacity of the straight shaft is enhanced, so that no reinforcement measure is needed in the middle of the straight shaft.

A cam on the straight shaft of its air inlet system pushes 6 push rods on 3 sets of pendulums which are mutually formed into 120 degrees and 6 rocker arms on the cylinder cover to work, so that the air inlet valve on the cylinder cover is opened and closed, a pendulum frame cylinder is installed in the middle of two cylinders, see 28-3 in figure 28, the improvement makes one cam of the engine replace 12 cams of a crankshaft internal combustion engine, a large number of processes for manufacturing and installing the camshaft and a transmission system of the crankshaft internal combustion engine are saved, the oil supply mode adopts a high-pressure common rail mode in the prior internal combustion engine technology, and the speed of the 6 cylinders is regulated and supplied with oil, and the high-pressure common rail mode belongs to the prior art and is not introduced in detail.

The exhaust part is directly communicated with the exhaust pipe outside the chassis because the exhaust port inside the cylinder of the engine is horizontally arranged, the exhaust holes are changed from a vertically arranged type to the positions shown by 28-1 and 28-2 in figure 28, 28-1 in figure 28 is that two exhaust holes of two cylinders on the right side close to the middle part are combined into one, and the exhaust is outwards exhausted through one exhaust hole on the chassis, 28-2 in figure 28 is that two exhaust holes are arranged on the upper and lower outer walls on the left side of the right side of the chassis, and the exhaust structures on the other cylinders are completely the same as 28-1 and 28-2 in figure 28. 9 gas vents on 6 cylinders, 3 corresponding gas vents on the upper side are connected together by the exhaust pipe and exhaust outwards from the upper side, 3 corresponding gas vents on the lower side are connected together by the exhaust pipe and exhaust outwards from the lower side, 3 corresponding gas vents in the middle are connected together by the exhaust pipe and exhaust outwards from the exhaust pipe on the upper side, a lifting process is carried out after the exhaust pipe is connected with a case, see 15-4 in fig. 15, so that lubricating oil in the case is prevented from leaking outwards along the exhaust pipe, and a bearing of a triangular bottom assembly straight shaft is totally enclosed in the case so as to prevent the lubricating oil in the case from leaking.

Claims (11)

1. The utility model provides a swing arm formula two-stroke straight axle internal-combustion engine, including the duckbilled wheel comma-shaped cam complex straight axle of straight epaxial intake cam and fuel feeding cam, side arm slider formula swing arm, lateral wall exhaust hole formula cylinder, swing piece fuel feeding pendulum block and rocker admit air, steady spring, increase the flywheel, quick-witted case, there is the connecting hole on the upper portion of swing arm front end, connect through steel pin and piston rod, swing arm rear end connecting hole passes through the steel pin and connects on quick-witted case and can the luffing motion, the fuel explosive force passes through piston rod and promotes the swing arm front end, it is rotatory to make the circular arc point of its lower part promote the epaxial duckbilled wheel of straight, rethread comma shape cam and swing arm lateral wall arc slider normal running fit, make piston straight reciprocating motion convert the circular motion of straight axle, a serial communication port: the duckbilled wheel and the comma-shaped cam on the straight shaft are respectively connected and matched with the lower arc point at the front end of the swing arm, the internal teeth at the middle part and the arc-shaped slide blocks on the side wall in an alternate manner in rotation, so that stable contact operation is realized when a plurality of intermittent points with irregular shapes are in rotary contact.

2. The swing arm two-stroke, straight shaft internal combustion engine of claim 1, wherein: the duckbill wheel comma-shaped cam combination body on the straight shaft of the single-cylinder single-unit type machine is rotationally matched with the side arm sliding block type swing arm, one cylinder on a case is driven to explode once by rotating a circle, the length from the axis of the duckbill wheel to the arc vertex is longer than that of a crank of a volume crankshaft internal combustion engine, an included angle is formed between a connecting line from the arc vertex of the duckbill wheel to the axis center and the vertical line of the axis center of the straight shaft when the upper stop ignites oil to explode, a top slide way of the duckbill wheel is divided into a left arc slide section and a right arc slide section by the arc vertex, an included angle is also formed between a leading-out line of the vertex of the left arc slide section and a horizontal line, the duckbill position of the duckbill wheel is an arc slide section, a transition arc slide section is arranged between the arc slide section and the circular slide section of the duckbill wheel, the working surface part of the comma-shaped cam is an arc slide way, the upper part of the front end of the swing arm is provided with a connecting hole, the middle part is provided with inner teeth, the lower part is provided with an arc point, and the upper side of the swing arm is provided with a stable spring, the side arm of the swing arm is provided with an arc slide block, the lower working surface part of the arc slide block is an arc slide way, the horizontal line of the center of a connecting hole at the rear end of the swing arm and the connecting line of the arc point at the lower part of the swing arm form an included angle, the connecting line from the center of a connecting hole at the upper part of the front end of the swing arm to the center of a connecting hole at the rear end of the swing arm and the connecting line from the center of a connecting hole at the upper part of the front end of the swing arm to the arc point at the lower part of the swing arm form an included angle, the side wall at the lower end of the air cylinder is provided with an exhaust hole communicated with an exhaust hole on the case, the exhaust holes on the air cylinder and the case are divided into a left exhaust hole and a right exhaust hole, the opening and closing of the air inlet valve are completed through the exhaust pipes at two ends, the opening and closing of the air inlet valve are completed through the air inlet cam on the straight shaft pushing the swing piece, the swing piece and the swing piece are installed on the swing frame which is installed on the case on the left side of the right side surface of the straight shaft, the oil injection system is formed by the oil injection cam on the straight shaft pushing the oil injection pump to push the oil injection pump to supply oil injection nozzle, compared with the inertia wheel of an internal combustion engine with the same power, the inertia wheel of the engine is enlarged.

3. The swing arm two-stroke, straight shaft internal combustion engine of claim 2, wherein: the radius from the center of a duckbill wheel to an arc vertex is 43.5 mm, the included angle between the connecting line from the arc vertex of the duckbill wheel to the center of the axle and the vertical line of a straight axle center is 45 degrees when the upper stop ignites oil and explodes, the arc length of a left arc-shaped sliding section is 33 mm, the chord height is 3.5 mm, the arc length of a right arc-shaped sliding section is 35 mm, the chord height is 3 mm, the included angle between the leading-out line of the vertex of the left arc-shaped section and the horizontal connecting line is 25 degrees, the length of a small section of arc-shaped sliding section at the duckbilled part is 5 mm, the length of a transitional arc-shaped sliding section is 8 mm, the arc length of a working part of a circular sliding section is 12 mm, the diameter of the straight axle duckbilled wheel of a duckbilled wheel combination body of a comma-shaped cam with an air inlet cam and an oil supply cam is 30 mm, the arc length of the arc-shaped sliding section is 50 mm and the chord height is 15 mm, the center of the connecting hole at the upper part at the front end of the swinging arm is 165 mm, the center of the connecting hole at the upper part of the swinging arm is 30 mm, the inner tooth end point of the swinging arm, the connecting hole at the lower part of the swinging arm is 60 mm, the distance between a steady spring and the center of a connecting hole at the upper part of the front end of a swing arm is 70 mm, the maximum compression length of the spring is 110 mm, the arc length of an arc slideway at the lower side of an arc sliding block at the side wall of the swing arm is 35 mm, the chord height is 15 mm, the included angle between the horizontal line of the center of the connecting hole at the rear end of the swing arm and the line of the center of the connecting hole at the upper part of the front end of the swing arm and the lower part of the swing arm are 3.7 degrees, the included angle between the line of the center of the connecting hole at the rear end of the swing arm and the line of the center of the connecting hole at the upper part of the front end of the swing arm and the line of the center of the connecting hole at the lower part of the swing arm are 15 degrees, the thickness of the swing arm is 20 mm, the side wall sliding block of the swing arm is 18 mm, the side wall exhaust holes at the lower end of a cylinder are communicated with the exhaust holes of a case, the left side and a left side, the exhaust hole are respectively in a rectangle shape, the height is 12 mm, the height is 6 mm, the height is 10 mm, the height of an air inlet cam bulge on a straight shaft is 10 mm, the width is 70 mm, the left side of the swing frame is 8 mm, the pin hole of the swing frame, the length of the swing piece is 60 mm, the diameter of the intake valve push rod is 7 mm, the length of the intake valve push rod is 240 mm, the length of the swing block is 45 mm, the inner diameter of a bearing on the swing block is 12 mm, the outer diameter of the bearing on the swing block is 28 mm, the width of the bearing on the swing block is 8 mm, the height of a cam bulge of the fuel injection pump on a straight shaft is 6 mm, the width of the cam bulge is 10 mm, and the weight of an inertia wheel is 8.5 kg.

4. The swing arm type two-stroke straight shaft internal combustion engine according to claim 1 or 2, wherein: the two-cylinder one-unit type engine is characterized in that a cylinder is additionally arranged on the basis of a single-cylinder one-unit type engine, an engine body of the engine is designed on the basis of an equilateral triangle, an engine base is arranged on the bottom edge of the triangle, one cylinder is respectively arranged on each inclined edge, the cylinder is arranged at the position where the vertical center line of each inclined edge is deviated to the right clockwise, the included angle between the center line of each cylinder and the vertical center line of the bottom edge of the triangle is 60 degrees, a side arm slider type swing arm is correspondingly arranged below each cylinder, a connecting hole at the upper part of the front end of each swing arm is connected with a piston in the cylinder through a connecting rod, the bottom of the right side of the cylinder 1 is the connecting position of the rear end of a swing arm 2 and the engine body, the central point of the triangle is the straight shaft position of a duckbill wheel and comma cam combination, the straight shaft rotates for a circle, the duckbill wheel and the comma cam are respectively in contact fit with the two swing arms in sequence, and the diesel oil in the two cylinders on a case respectively explodes through six intermittent contact points, the air inlet cam on the straight shaft respectively pushes two sets of air inlet systems, each air inlet valve works once when the straight shaft rotates for a circle through the swinging piece push rod and the upper rocker arm, the oil injection cam on the straight shaft respectively pushes the two swinging blocks to enable the two oil supply pumps to supply oil, each oil injection pump works once when the straight shaft rotates for a circle, two exhaust holes on each side of the four exhaust holes on two sides of the engine body are connected together to send waste gas outwards, and one section of exhaust pipe is raised after being connected with the engine case.

5. The swing arm two-stroke, straight shaft internal combustion engine of claim 1, wherein: a triangle three-cylinder one-unit vertical placing machine is characterized in that a cylinder is added on the basis of a two-cylinder one-unit machine, a machine body of the machine is designed on the basis of an equilateral triangle, a cylinder is placed on each of three sides, the cylinder is arranged at the position where the vertical center line of an oblique side is clockwise and deviated from the right side, the included angle between the center line of each cylinder and the vertical center line of the triangle side is 60 degrees, the three cylinders mutually form an angle of 120 degrees, a side arm sliding block type swing arm is correspondingly placed below each cylinder, a connecting hole at the upper part of the front end of the swing arm is connected with a piston in the cylinder through a connecting rod, the lower part of the right side of each cylinder is the connecting position of the rear end of the next swing arm and the machine body, a straight shaft of a duckbill wheel comma-shaped cam combination body is placed at the central point of the triangle, the straight shaft rotates for a circle, a duckbill wheel and a comma-shaped cam are respectively in contact fit with the three swing arms one time, and the oil in the three cylinders on a machine case respectively explodes once through nine intermittent contact points, the air inlet cams on the straight shaft respectively push three sets of air inlet systems, each air inlet valve works once after rotating for a circle, the oil injection cams on the straight shaft respectively push three oil injection pumps, each oil injection pump works once after rotating for a circle on the straight shaft, and three exhaust holes on each side of six exhaust holes on two sides of the engine body are connected together through three exhaust pipes to supply waste gas outwards.

6. The swing arm two-stroke, straight shaft internal combustion engine of claim 1, wherein: a triangular three-cylinder one-unit horizontal placing machine is characterized in that a vertical triangular machine body is horizontally placed on the basis of a triangular three-cylinder one-unit vertical placing machine, after the triangular machine is horizontally placed, an exhaust hole is changed into a horizontal plane at the bottom of the exhaust hole and a horizontal plane at the swing arm, the other exhaust hole is symmetrically arranged at the right side of the right side face of a machine box, three sets of rocker arm systems forming an angle of 120 degrees with each other are respectively pushed by an air inlet cam on a straight shaft, each rocker arm pushes one push rod to open and close an air inlet valve through an upper rocker arm, and when a triangular one-unit machine type cylinder is horizontally placed, an oil supply system adopts a high-pressure common rail mode.

7. The swing arm two-stroke, straight shaft internal combustion engine of claim 1, wherein: the four-cylinder two-unit V-shaped machine is characterized in that a unit is additionally arranged on the basis of a two-cylinder one-unit, 4 cylinders are provided in total, 4 swing arms and side wall sliders of the four-cylinder two-unit V-shaped machine are respectively arranged on two sides of a straight shaft in a machine case in a group, and are matched with duckbill wheel comma-shaped cams on two sides of the straight shaft, a swing frame base is arranged in the middle position of the machine case, 4 push rods on two swing pieces are pushed by the cams on the straight shaft to respectively pass through a middle through hole of the two cylinders and a middle through hole of a cylinder cover to respectively push 4 upper rocker arms on the two cylinder covers to work, so that air valves on the cylinder covers are opened and closed, the swing pieces are arranged at the top ends of cylinders, the cylinder base is fixed at the positions of air inlets on the machine case, an exhaust part exhausts through 6 exhaust ports at the lower parts of the 4 cylinders, two exhaust holes close to the middle parts of the lower parts of the two cylinders are combined into one, and exhausts outwards through one exhaust hole on the machine case, the middle exhaust holes of the other two cylinders are combined into a flange interface, 4 exhaust holes are arranged on the outer side wall of the case, 4 exhaust holes on two outer sides of the flange interface of the middle exhaust hole are connected together by two exhaust pipes on each side to exhaust outwards, 2 exhaust holes in the middle position are respectively connected on the exhaust pipes on the outer sides by the exhaust pipes to exhaust outwards, and the oil supply mode adopts a high-pressure common rail mode in the prior internal combustion engine technology to supply oil to the 4 cylinders.

8. The swing arm two-stroke, straight shaft internal combustion engine of claim 7, wherein: the axial width 240 millimeters of two outer walls of quick-witted case, straight axle duckbilled wheel department diameter 35 millimeters, quick-witted case right side inner wall is 25 millimeters to right duckbilled wheel left side edge, duckbilled wheel comma type cam complex is 40 millimeters wide, comma type cam is to intake cam 25 millimeters, intake cam width 30 millimeters, intake cam is to left duckbilled wheel comma type cam complex right side 25 millimeters, the comma type cam of duckbilled wheel complex is to quick-witted case left side inner wall 25 millimeters, quick-witted case two wall thickness 15 millimeters, the cylinder diameter 35 millimeters of installation balance staff, the cylinder length 90 millimeters, balance staff width 30 millimeters, push rod diameter 7 millimeters, length 240 millimeters.

9. The swing arm two-stroke, straight shaft internal combustion engine of claim 1, wherein: the triangular six-cylinder two-unit vertical type is characterized in that a unit is added on the basis of a three-cylinder one-unit vertical type, duckbill wheel comma-shaped cams on two sides of a straight shaft are matched with side wall slide block swing arms, an air inlet cam is arranged in the middle position and has the same structure as that of a V-shaped four-cylinder two-unit type, every three of the six swing arms and the side wall slide blocks are respectively arranged on two sides of the straight shaft in a case in a group and are matched with the duckbill wheel comma-shaped cams on two sides of the straight shaft, a swing frame base is arranged in the middle position of the case, the air inlet cam on the straight shaft respectively pushes three sets of rocker arm systems which form an angle of 120 degrees with each other, each swing piece pushes two push rods, the six air inlet valves are opened and closed once by rotating one circle of the air inlet cam, 9 air outlets on the lower sides of 6 air cylinders, 3 corresponding 6 air outlets on each side of the two sides are connected together to exhaust outwards, the air outlets on the right side of the middle position are connected together to exhaust outwards, the oil supply system adopts a high-pressure common rail mode.

10. The swing arm two-stroke, straight shaft internal combustion engine of claim 1, wherein: the six-cylinder two-unit horizontal placement machine type is characterized in that a unit is added on the basis of a three-cylinder one-unit horizontal placement machine type, every three of six swing arms and side wall sliders of the six-cylinder two-unit horizontal placement machine type are respectively installed on two sides in a machine case in a group, duckbill wheel comma cams corresponding to two sides of a straight shaft are matched with the duckbill wheel comma cams, the air inlet cams on the straight shaft respectively push three sets of air inlet systems, each swing sheet pushes two push rods to open and close an air inlet valve, a swing frame base is installed in the middle of the machine case, exhaust holes are changed into positions on the same horizontal plane with the swing arms, 9 exhaust holes are formed in the positions, 3 exhaust pipes on each side of corresponding 6 exhaust pipes on two sides are connected together to exhaust outwards, the exhaust pipes in the middle of the positions are connected to 3 exhaust pipes on the outer side wall to exhaust outwards, and the oil supply systems adopt a high-pressure common rail mode.

11. The swing arm two-stroke, straight shaft internal combustion engine of claim 1, wherein: the multi-cylinder multi-unit machine type has the advantages that a measure for reinforcing the straight shaft is added among a plurality of units of the straight shaft, a V-shaped 8-cylinder 4-unit machine type and a triangular 12-cylinder 4-unit machine type are added among 4 units of the straight shaft, the reinforcing effect on the straight shaft is achieved, and the structures of other parts are completely consistent with those of the 2-unit machine type.

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