RU2298678C2 - Rotary engine - Google Patents

Abstract

FIELD: mechanical engineering.

SUBSTANCE: invention relates to pumps, compressors and engines. According to invention, proposed rotary internal combustion engine has body with supports, crankcase, shafts on supports displaced in parallel relative to each other, and cylinders with pistons. Cylinder with systems and mechanisms providing working cycle is mounted on one shaft, and lever hinge-connected with piston is coupled with other shaft. Intake and exhaust valves are arranged in cylinder head, and engine crankcase can be made for combined rotation with cylinder.

EFFECT: provision of rotary internal combustion engine featuring reduced vibratory load and mass-and-dimension characteristics.

22 cl, 18 dwg

Description

The scope of the invention is mechanical engineering, namely the creation of pumps, compressors, engines. Mostly the invention is directed to the creation of internal combustion engines (ICE) with push-pull, four-stroke and six-stroke cycles.

Known piston machine according to the patent of the Russian Federation No. 20133566 C1, IPC F01B 13/04, F02B 57/00, publ. 05/30/1994, where there are two parallel shifted shafts, each of which has a pair of cylinders with pistons rigidly fixed to each other on the cross. Pistons are displaced by means of levers. Fundamentally, this device relates to a cardan transmission, and the displacement of the shafts relative to the crosspiece creates a significant unevenness in the rotation of the shafts and difficult to eliminate vibrations.

Known piston machine according to the patent of the Russian Federation No. 2030593 C1, IPC F01B 13/04, publ. 03/10/95, where one shaft interacts with another shaft made on the crosspiece with pistons through two pairs of opposed cylinders. At the same time, the axis of the shaft on the cross makes circular motions, this mechanism has the principle of movement of the cardan drive, divided into two parts, uneven travel and vibration also occur.

Known piston machine according to the patent of the Russian Federation No. 2030594 C1, IPC F01B 13/4, publ. 03/10/95, where, by analogy with RF patent No. 2030593, there are two shafts interacting through pistons and cylinders fixed rigidly to the crosspiece. Both devices have the same operating principle, uneven rotation and runout are not eliminated.

Known speed variator ed. testimonial. USSR No. 892059, IPC F16H 29/16, publ. 12/23/81, where there are two shafts that are parallel offset from each other. On one shaft there are backstages with slots, on the other levers with fingers. Fingers with joint rotation move in the slots. When one of the shafts rotates, the second shaft rotates smoothly and without vibrations at any speed. The wings during rotation will be uniformly accelerated and decelerated uniformly for each revolution. The drawstring in this case is considered as a cylinder, and the lever with a finger as a piston on the crankshaft. When performing one backstage rigidly on the shaft and installing the flywheel on one of the shafts, the principle of operation of a single-cylinder rotary engine is implemented. By connecting the shafts with levers or shafts with wings, in series or parallel with changing the direction of rotation to the opposite with a 180 ° rotation, the principle of operation of a two-cylinder rotary engine is implemented, the flywheel is not needed in this case. At the same time, making the shafts (or shaft) movable in the radial direction, the rotational engine becomes multi-fuel, because the compression ratio changes.

Known speed variator ed. testimonial. USSR No. 918601, IPC F16H 29/12, publ. 04/07/82, where there are parallel displaced shafts, wings, fingers, a central shaft and a device for its displacement. Here the fundamental principles for the implementation of a rotary multi-fuel engine are laid.

Known single-cylinder engines for aircraft models MK-16, MK-18, MD-5; engines on Oka cars are two-cylinder, DEUs are three-cylinder, Moskvich are four-cylinder. All classic engines have a flywheel and a significant mass crankshaft, as the pistons reciprocate, which are transmitted through the fingers and connecting rod to the crankshaft mounted in the fixed cylinder block. At high speeds, this dramatically reduces the effective efficiency.

The closest device for the combination of essential features (the presence of two parallel shafts, pistons and cylinders) is a piston machine according to the patent of the Russian Federation No. 20133566 C1, IPC F01B 13/04, F02B 57/00, publ. 05/30/1994.

The technical result consists in the possibility of creating a rotary internal combustion engine with reduced vibration load and overall dimensions, which will dramatically increase the efficiency and greatly reduce fuel consumption per unit of power.

According to the invention, the rotary internal combustion engine comprises a housing with bearings, a crankcase, shafts located in the bearings, which are parallel offset from each other, and cylinders with pistons. A cylinder with systems and mechanisms providing a duty cycle is placed on one shaft, and a lever pivotally connected to the piston is connected to the other shaft. In this case, the cylinder and piston can be made curved, for example, in the form of a torus sector within 90 °. The inlet and outlet valves are made in the cylinder head, the valve axes being made radially with respect to the axis of rotation of the shaft, and the cylinder axis is made at an angle to the valve axis. The crankcase of the engine can be made with the possibility of joint rotation with the cylinder. In this case, the inertial mass of the piston head with piston rings may be greater than the inertial mass of the piston skirt with respect to the hinge axis or the inertial mass of the piston skirt may be greater than the inertial mass of the piston head with piston rings with respect to the hinge axis. Lubrication of the piston group is provided by radial holes made in the cylinder, and the hinge lubrication between the piston and the lever is provided through the hole made in the hinge supports on the lever side. The cylinder shaft can be hollow, where electrical equipment, mixture formation, coolant, exhaust gas systems are located. On the axis of the hollow shaft of the cylinder, a high-pressure fuel pump can be rigidly fixed with the possibility of joint rotation with the shaft. A forced exhaust turbine may be rigidly fixed to the exhaust pipe. The diffuser of the supply of the combustible mixture can be made on the cylinder in the form of a ring. When engines are connected, the shaft with the lever and piston of one engine is rigidly connected to the shaft for the lever and piston of another engine, and the shaft with the cylinder of one engine is rigidly attached to the shaft with the cylinder of another engine. In one embodiment of the invention, the cylinder and the lever pivotally connected to the piston can be made with a counterweight, and the counterweight of both the cylinder and the lever can be made adjustable.

There are no rods in the rotary engine, there are no inertial shock forces from the reciprocating motion of the piston, the piston has no provisions of V.M.T. and N.M.T., there is an upper point - V.T., a lower point - N.T., the engine is completely balanced, which will sharply increase the efficiency and greatly reduce fuel consumption per unit of power.

The invention is illustrated by drawings, which depict the following.

Figure 1 shows a schematic kinematic diagram of a single-cylinder rotary engine, where 1 is the engine body (base), 2 is a rotary crankcase, 3 is a cylinder in the form of a ball-tor sector, 4 is a piston in the form of a ball-tor sector, 5 - piston shaft, 6 - lever, 7 - piston pin, 8 - adjustable counterweight of the piston group and lever, 9 - adjustable counterweight of the cylinder with systems and mechanisms that provide a duty cycle, 10 - inlet valve, 11 - exhaust valve, 12 - diffuser inside the shaft , 13 - cylinder shaft, 14 - cylinder bearings, 15 - shaft bearing, 16 - propeller.

Figure 2 is a schematic kinematic diagram of a single-cylinder rotary engine, where 17 is a flywheel, the remaining designations are the same as in the previous illustration.

Figure 3 - kinematic diagram of the pairing of the piston and cylinder in a curved design. Designations are the same as in the previous illustrations.

Figure 4 - kinematic diagram of the installation of a straight piston and cylinder at an angle to the common vertical axis, where 18 is the cylinder, 19 is the piston, the remaining designations are the same as in the previous illustrations.

Figure 5 is a schematic kinematic diagram of a single-cylinder rotary engine, where 20 is an annular diffuser, 21 is a shaped knee (lever), 22 is a radial piston in the form of a ball-tor sector, 23 is a radial cylinder in the form of a ball-tor sector, 24 is radial finger. The remaining notation is the same as in the previous illustrations.

In Fig.6 is a schematic kinematic diagram of a single-cylinder rotary engine, the designations are the same as in the previous illustrations.

7 is a kinematic diagram of the coupling of the radial piston, the radial cylinder in a curved design, the designations are the same as in the previous illustrations.

On Fig - kinematic diagram of the installation of a linear radial piston and a radial cylinder, section AA, 25 - radial piston, 26 - radial cylinder, the rest of the designations are the same as in the previous illustrations.

Figure 9 is a schematic kinematic diagram of a two-cylinder rotary engine, where 27 is a bevel gear, 28 is an output shaft, 29 is a clutch, the remaining designations are the same as in the previous illustrations.

Figure 10 is a schematic kinematic diagram of a four-cylinder rotary engine, where 30 is a cylinder counterweight with systems and mechanisms that provide a duty cycle, 31 is a piston group counterweight with a lever. The remaining notation is the same as in the previous illustrations.

In Fig.11 is a schematic kinematic diagram of a two-cylinder rotary engine, the designations are the same as in the previous illustrations.

On Fig - schematic kinematic diagram of a four-cylinder rotary engine, the designations are the same as in the previous illustrations.

On Fig - schematic kinematic diagram of a four-cylinder rotary engine, consisting of two connected engines with piston groups, located opposite at the beginning of the working stroke. Designations are the same as in the previous illustrations.

On Fig - schematic kinematic diagram of a four-cylinder rotary engine, consisting of two connected engines with radial piston groups, located opposite at the beginning of the stroke, where 32 is the hypoid gear, the rest of the designations are the same as in the previous illustrations.

On Fig - diagram of the device injection (carburetor) four-stroke single-cylinder rotary engine with liquid cooling, where 33 is a fixed crankcase, 34 - minus brush mass of the cylinder, 35 - high voltage chopper, 36 - fixed gear, 37 - movable gear, 38 - camshaft, 39 - intake valve pusher, 40 - exhaust valve pusher, 41 - intake valve rocker, 42 - exhaust valve rocker, 43 - exhaust end pipe, 44 - forced exhaust turbine, 45 - high-voltage wire , 46 - spark plug, 48 - fuel supply pipe, other designations are the same as in the previous illustrations.

In Fig.16 is a diagram of the device injection (carburetor) four-stroke two-cylinder engine with air cooling, where 49 is a louvered grille intake of cooling air, 50 is an annular grille to release heated air and exhaust gases, 51 is a radial exhaust pipe, 52 is the cooling fins of the cylinder, 53 - crankcase oil seal, 54 - fuel supply pipe, other designations are the same as in the previous illustrations.

On Fig - diagram of the device injection (carburetor) four-stroke four-cylinder engine with air cooling, where 55 is the interrupter-distributor, 56 is the low voltage circuit, 57 is the high voltage circuit, 58 is the shielded high voltage wire, 59 is the cooling cooling ring inlet air, 60 - fuel supply pipe, 61 - bearing, other designations are the same as in the previous illustrations.

In Fig.18 is a diagram of the device of a diesel four-stroke two-cylinder rotary engine with air cooling, section AA in Fig.8, cylinder mounting and direction of rotation, where 62 is a high-pressure fuel pump with rotation, 63 is a nozzle, 64 is a leading fuel supply drive drive gear, 65 - axial movement of the fuel feed drive drive gear, 66 - fuel supply drive cam, 67 - diaphragm type high pressure pump drive cam, 68 - unitary enterprise thrust bearing, 69 - axial displacement shaft, 70 - bearing, 71 - fuel supply control pedal, 72 - rotary fuel supply pipe, 73 - fuel supply gland, 74 - fixed fuel supply pipe, other designations are the same as in the previous illustrations.

The following is a continuous numbering of the designations of all nodes and parts in Fig.1-18.

1 - housing (base), 2 - crankcase with rotation, 3 - cylinder in the form of a ball-tor sector, 4 - piston in the form of a ball-tor sector, 5 - piston shaft, 6 - lever, 7 - piston pin, 8 - adjustable counterweight of the piston group and the lever, 9 - adjustable counterweight of the cylinder with systems and mechanisms that provide a duty cycle, 10 - inlet valve, 11 - exhaust valve, 12 - diffuser inside the shaft, 13 - cylinder shaft, 14 - cylinder bearings, 15 - bearings shaft, 16 - propeller, 17 - flywheel, 18 - cylinder, 19 - piston, 20 - ring diffuser, 21 - shaped knee (lever), 22 - pore radial in the form of a ball-tor sector, 23 - a radial cylinder in the form of a ball-tor sector, 24 - radial pin, 25 - radial piston, 26 - radial cylinder, 27 - bevel gear, 28 - output shaft, 29 - coupling, 30 - cylinder counterweight with systems and mechanisms that ensure the duty cycle, 31 - piston group counterweight with lever, 32 - hypoid gear, 33 - fixed crankcase, 34 - negative brush for cylinder mass, 35 - high voltage chopper, 36 - fixed gear, 37 - movable gear, 38 - camshaft, 39 - intake pusher o valve, 40 - exhaust valve pusher, 41 - intake valve rocker, 42 - exhaust valve rocker, 43 - exhaust outlet pipe, 44 - forced exhaust turbine, 45 - high-voltage wire, 46 - spark plug, 47 - combined cooling system oil seal , 48 - fuel supply pipe, 49 - louvre grille for cooling air intake, 50 - annular grille for heated air and exhaust gases, 51 - radial exhaust pipe, 52 - cylinder cooling fins, 53 - crankcase oil seal, 54 - fuel supply pipe go, 55 - breaker-distributor, 56 - low-voltage magnetic circuit, 57 - high-voltage magnetic circuit, 58 - high-voltage shielded wire, 59 - cooling air intake ring grille, 60 - fuel supply pipe, 61 - bearing, 62 - high pressure pump rotary fuel supply, 63 - nozzle, 64 - drive gear of the fuel supply mechanism, 65 - driven gear drive of the fuel supply mechanism, 66 - cam drive of the fuel supply mechanism, 67 - cam drive of the high pressure pump th type 68 - ball bearings 69 - a shaft with the possibility of axial displacement, 70 - bearing 71 - the accelerator pedal 72 - the fuel supply pipe rotatably, 73 - fuel supply gland, 74 - the fixed fuel supply conduit.

The rotary engine has eight different modifications in kinematic relationships: cylinder - piston-PTO; piston - cylinder-PTO.

Rotary single-cylinder engines are shown in the kinematic diagrams of FIG. 1, FIG. 2, FIG. 3, FIG. 4, FIG. 5, FIG. 6, FIG. 7, FIG. 8.

Common to all engines are the shaft 13 in the bearing 14 and the shaft 5 in the bearing 15.

Performing on the shaft 13 the cylinder of FIG. 3, FIG. 4, FIG. 1, we obtain two modifications of the rotary engine and FIG. 7, FIG. 8, FIG. 5 - two modifications of the rotational engine. The power take-off shaft is the shaft 5 in figure 1, figure 5.

Performing on the shaft 13 the cylinder of FIG. 3, FIG. 4, FIG. 2, we obtain two modifications of the rotary engine and FIG. 7, FIG. 8, FIG. 6 - two modifications of the rotational engine. The power take-off shaft is a shaft 13 in FIG. 2, FIG. 6.

A rotary engine has two distinctive features in the intake of a combustible mixture (air): the diffuser 12 is made in the hollow shaft 13 in Fig. 15, Fig. 16, Fig. 18; annular diffuser 20 mounted on the cylinder, Fig.17.

The rotary engine has two distinctive features for exhaust gas: the exhaust end pipe 43 is made in the hollow shaft 13 in Fig.15; radial exhaust pipe 51 is made in the annular lattice of ejection of heated air and exhaust gases 50 in Fig.16, Fig.17, Fig.18.

The rotational engine has two modifications of the crankcase: the crankcase rotatably 2, FIG. 1, FIG. 2, FIG. 5, FIG. 6, FIG. 13, FIG. 14, FIG. 16, FIG. 17, FIG. 18, is made on shaft 13; fixed crankcase 33, Fig, is made in the housing 1.

Fig. 9 shows a rotary two-cylinder engine consisting of two single-cylinder rotational engines of Fig. 1, Fig. 3 with one common shaft 5 and 180 ° offset levers, bevel gear 27 on the shaft 5 is kinematically connected to the output shaft 28 and the coupling 29 .

Figure 10 shows a rotational in-line four-cylinder engine, which consists of four series-connected engines of figure 1, figure 3, contains a counterweight 30 of the cylinder with systems and mechanisms that provide a duty cycle, a counterweight 31 of the piston group and lever, a common shaft 5 on all cylinders.

11 shows a rotary two-cylinder engine containing two single-cylinder engines on a common shaft 5 with curly bends (levers) 21, rotated diametrically 180 °.

On Fig shows a rotational inline four-cylinder engine of Fig.5, Fig.7, which contains four single-cylinder engines on a common shaft 5.

On Fig shows a rotary four-cylinder engine containing two two-cylinder rotary engines, the output shaft 28 is made on the side of the engine.

On Fig shows the rotational four-cylinder engine of Fig.7, which contains two two-cylinder engine, kinematically connected by hypoid transmission via gears 32, the output shaft 28 is located at the end of the engine.

On Fig shows a rotary four-stroke single-cylinder liquid-cooled engine with external mixture formation and forced ignition from an electric spark, which contains a housing 1, a fixed crankcase 33, a negative brush mass of the cylinder 34, a high voltage chopper 35, inside the housing 1 fixed gear 36, movable gear 37 made on the camshaft 38, the intake valve pusher 39 and the exhaust valve pusher 40, the intake valve rocker 41, the exhaust valve rocker 42, kinemat associated with the inlet valve 10 and the exhaust valve 11, the end pipe of the release 43 located on the radial axis of the shaft 13, the longitudinal axis of the stationary gear 36 and the end turbine of the forced release 44, the shaft 13 (made hollow), in which the high-voltage wire 45 is arranged in series diffuser 12 for supplying air and fuel, a liquid cooling system and an end pipe of exhaust 43 with a reduced flow cross section, a combined oil seal of the liquid cooling system 47 and fuel supply pipelines 48, are made motionless. The shaft 13 in the bearing 14 is made integrally with the cylinder 3 in the form of a ball-tor sector and an adjustable counterweight 9. The shaft 5 in the bearing 15 is made integrally with the lever 6 of the piston 4 in the form of a ball-tor sector with a finger 7 and an adjustable counterweight 8 .

On Fig shows a rotational four-stroke two-cylinder air-cooled engine with external mixture formation (injector) and positive ignition from an electric spark. One cylinder is shown, the second cylinder is rotated 180 °. The engine corresponds to FIG. 9, FIG. 4 and comprises a housing 1, a rotary crankcase 2, a fixed gear 36, a movable gear 37 kinematically connected through a block of bevel gears with a camshaft 38, an intake valve 10, an exhaust valve 11, a diffuser 12 in hollow shaft 13, bearings 14, cylinder 8, adjustable counterweight 9, louver grille for cooling air intake 49, annular grille for heated air and exhaust gases 50, radial exhaust pipe 51, cooling fins for cylinder 52, crankcase oil seal 53, fixed fuel supply conduit 54, the piston 19 with the finger 7, adjustable counterweight 8, the lever 6 to the shaft 5, the bearing 15, the common shaft 5 with two levers 6.

On Fig shows the third cylinder of the rotary four-stroke four-cylinder engine of figure 10 with air cooling, with external mixture formation and positive ignition from an electric spark. The engine comprises a housing 1, a movable crankcase 2, a cylinder 3, a cylinder counterweight with systems and mechanisms providing a duty cycle 30, a piston 4 with a finger 7, a piston group counterweight with a lever 31, a breaker-distributor 55, a low voltage circuit 56 installed in the housing 1, a high-voltage magnetic circuit mounted on a movable crankcase 2, a high-voltage shielded wire 58, a cooling air intake ring grille 59, a common shaft 5 for four cylinders, a lever 6, a bearing 61 on a lever, an annular diffuser 20, behind mounted on cylinder 18.

On Fig shows a rotary two-cylinder four-stroke engine (see Fig. 11, Fig. 8, section AA) with internal mixture formation and ignition from contact with air that is very hot by compression (diesel). The engine comprises a common shaft 5, shaped elbows (levers) 21, a radial piston 25 in the cylinder 26, a high-pressure fuel pump rotatably 62, a shaft 13, an injector 63, a drive gear of a fuel supply mechanism 64, made in conjunction with a shaft 13, driven gear of the fuel supply drive with axial displacement 65, cam of the fuel supply 66, shaft with axial displacement 69 in the bearing 70, the fuel control pedal 71, the spring-loaded cam of the high pressure pump drive 67, the supply pipe fuel rotatably 72, a fuel feed seal 73, a stationary fuel supply pipe 74.

The operation of one of the eight modifications of the rotary single-cylinder engine (Fig. 1, Fig. 3, Fig. 15) is carried out as follows: piston 4 under gas pressure, moving from the upper point (BT) to the lower point (NT) and simultaneously rotating within 180 °, acts on the lever 6 through the piston pin 7. The parallel displacement of the axes of the shaft 5 and shaft 13 creates a torque relative to the housing 1. The propeller 16 or flywheel 17 provides further rotation of the shaft 5. The total inertial mass of the propeller 16 or flywheel 17, piston 4 , lever 6, finger 7 and p adjust- able counterweight 8 should significantly exceed the total inertial mass of the cylinder 3 an adjustable counterweight 9 and systems providing work cycle. Under this condition, the cylinder 3 on the shaft 13 rotates with uniform acceleration in the range of 180 ° and uniform deceleration in the range of 180 °, which equals one rotation in a 360 ° cylinder-piston pair to uniform rotation (friction losses increase only slightly). This is the most economical kinematic modification of the cylinder - piston-shaft. Because there are no reciprocating movements of the piston; it only rotates uniformly. The execution of the piston in the form of a ball-tor sector provides smooth, shock-free operation of the piston in the cylinder, which will increase the efficiency and motor life of the rotary engine. The wear of the piston and cylinder during working strokes is reduced, as they are in contact over the large diameter of the ball-tor sector, and the resulting torque is the piston-arm-cylinder shoulder acting on the principle of a reduction gear during operation. The foregoing relates to the kinematic diagram of FIG. 5, FIG. 7, FIG. 8, FIG. 18, changes only to the back shoulder of the cylinder — the shoulder of the piston.

The operation of the rotary single-cylinder engine of FIG. 2, FIG. 3, FIG. 4, FIG. 6, FIG. 7, FIG. 8 is carried out similarly, but the piston is uniformly accelerated and uniformly slowed, the cylinder with the flywheel will rotate uniformly. When arranging an in-line multi-cylinder engine, the common shaft 5 can be made stationary on all cylinders, and each piston lever is placed on a separate bearing, the support of which will be a shaft 5, rigidly fixed in the housing 1. The cylinder, as a rule, has more inertial mass than the piston , therefore, the piston will work in worse conditions, and the efficiency will be lower, because The principle of overdrive applies.

With a two-cylinder, three-cylinder, etc. the rotary engine is fundamentally unnecessary for the flywheel, the uniformity of the output shaft (directly at the engine) is achieved by mutual cancellations of uniform accelerations and uniform decelerations of the cylinder-cylinder or piston-piston pair, this sharply increases the efficiency and improves idling performance.

When operating a two-cylinder rotary engine, the rotating parts (piston group, cylinder, gas distribution mechanism) wear out, therefore, routine work is necessary to balance the engine (arrows on the balances 8 and 9 show the direction of their movements) or mechanisms for automatic balancing.

With four, six, eight, etc. cylinders balancing can be done once during engine assembly.

In Fig.15, Fig.16, Fig.17, Fig.18 shows a diagram of the device four-stroke engines, they have in common that for the rotation of the shaft 5, the gear 37 rotates half a turn, because the gear 36 is fixed stationary, in Fig. 18, the gear 64 rotates one revolution, the gear 65 half the revolution.

The intake system acquires the properties of boost, because the cylinders rotate, centrifugal forces appear, the air in front of the inlet valve is compressed, and at the moment of inlet is compressed as much as possible. the cylinder at this moment ends the deceleration. As a result, the pressure increases sharply, the purge and the filling of the cylinder improves.

The exhaust system also acquires the properties of forced centrifugal exhaust emissions, there is also the effect of maximum exhaust (vacuum) when the piston is in the VT. For this purpose, a centrifugal turbine 44 is installed on the rotating end pipe of exhaust 43, with its installation the dimensions of the combined oil seal of the cooling system 47 are reduced, because reduced passage section of the end pipe 43 (Fig.15).

A sector piston with a ball torr 4 with piston rings and a piston 19 with piston rings must be balanced with respect to the axis of the piston pin 7 during rotation, i.e. the inertial mass of the piston head with piston rings must be greater than or equal to the inertial mass of the piston skirt, FIG. 1, FIG. 2, FIG. 3, FIG. 4.

A radial piston in the form of a sector ball-torus 22 with piston rings and a radial piston 25 with piston rings must be balanced with respect to the axis of the piston pin 24 during rotation, i.e. the inertial mass of the piston skirt must be equal to or greater than the inertial mass of the piston head with piston rings, FIG. 5, FIG. 6, FIG. 7, FIG. 8.

The inlet and outlet valves should be performed along the radial axis to the axis of rotation of the shaft 13. With the upper arrangement of the valves (figure 3, figure 4) this arrangement of the valves will ensure reliable operation, as centrifugal forces at high speeds press the valve against the seat. When performing a high-speed rotary engine, this condition is necessary with the lower location of the valves (Fig.7). The inertial mass of the rocker arm of the intake valve 41 and exhaust valve 42 from the side of the shoulder of the toe of the valve relative to the axis of installation of the rocker arm must be equal to or greater than the total inertial mass of the arm of the rocker arm with all free drive mechanisms (pushers, rods, or levers) on the other side relative to the axis of the rocker arm installation (Fig. .fifteen). This condition will ensure tight valve closure.

For reliable operation of the oil scraper rings of the piston 4 in the cylinder 3 (Fig. 3) of the piston 19 or in the cylinder 18 (Fig. 4), it is necessary to make radial through inclined holes in the cylinder walls from the piston to eject oil from the piston due to centrifugal forces (Fig. 3 4).

For reliable operation of the compression rings of the radial piston 22 in the radial cylinder 23 (Fig. 7) of the radial piston 25 or in the radial cylinder 26 (Fig. 8), it is necessary to make radial through inclined holes in the cylinder walls to the piston to supply oil to the piston due to centrifugal forces (Fig.7 and Fig.8).

When lubricating by spraying the oil of the bearing 61 with the finger 7, the hole for oil supply is made from the side of the lever 6 (Fig.17).

When lubricating by spraying the oil of the bearing 61 with the radial pin 24, the hole for supplying oil is made on the opposite side of the curly elbow (lever) 21 (Fig. 18).

When the axes of the shaft 5 and shaft 13 are shifted by a very small value, the rotary engine acquires the properties of a turbine and turbojet aircraft engine, because revolutions will significantly increase, the engine starts to work on itself, directing a stream of exhaust gases along the axis of the shaft, we obtain jet thrust.

Claims (22)

1. An engine comprising a housing with bearings, a crankcase, shafts located in the bearings, which are parallel offset from each other, and cylinders with pistons, characterized in that on one shaft there is a cylinder with systems and mechanisms that provide a duty cycle, and with another shaft connected lever pivotally connected to the piston. 2. The engine according to claim 1, characterized in that the cylinder is made curved. 3. The engine according to claim 1, characterized in that the piston is curved. 4. The engine according to claim 2, characterized in that the cylinder is made in the form of a torus sector within 90 °. 5. The engine according to claim 3, characterized in that the piston is made in the form of a torus sector within 90 °. 6. The engine according to claim 1, characterized in that the inlet and outlet valves are made in the cylinder head, the valve axes being made radially with respect to the axis of rotation of the shaft. 7. The engine according to claim 6, characterized in that the axis of the cylinder is made at an angle to the axis of the valve. 8. The engine according to claim 1, characterized in that the crankcase is made with the possibility of joint rotation with the cylinder. 9. The engine according to claim 1, characterized in that the inertial mass of the piston head with piston rings is greater than the inertial mass of the piston skirt relative to the axis of the hinge. 10. The engine according to claim 1, characterized in that the inertial mass of the piston skirt is greater than the inertial mass of the piston head with piston rings relative to the axis of the hinge. 11. The engine according to claim 1, characterized in that the lubrication of the piston group is provided by radial holes made in the cylinder. 12. The engine according to claim 1, characterized in that the lubrication of the hinge between the piston and the lever is provided through an opening made in the bearings of the hinge from the side of the lever. 13. The engine according to claim 1, characterized in that the cylinder shaft is hollow, where electrical systems, mixture formation, coolant, exhaust gas systems are located. 14. The engine according to item 12, characterized in that on the axis of the hollow shaft of the cylinder a high pressure fuel pump is rigidly fixed with the possibility of joint rotation with the shaft. 15. The engine according to item 12, characterized in that the exhaust pipe is rigidly fixed to the exhaust pipe. 16. The engine according to claim 1, characterized in that the diffuser for supplying the combustible mixture is made on the cylinder in the form of a ring. 17. The engine according to claim 1, characterized in that the shaft with the lever and piston of one engine is rigidly connected to the shaft for the lever and piston of another engine. 18. The engine according to claim 1, characterized in that the shaft with the cylinder of one engine is rigidly attached to the shaft with the cylinder of another engine. 19. The engine according to claim 1, characterized in that the cylinder is made with a counterweight. 20. The engine according to claim 1, characterized in that the lever pivotally connected to the piston is made with a counterweight. 21. The engine according to claim 19, characterized in that the counterweight is adjustable. 22. The engine according to claim 20, characterized in that the counterweight is adjustable.

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