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INVENTION
Patent of the Russian Federation RU2200858
ENGINE OF INTERNAL COMBUSTION LEONTYEVA А.А.

ENGINE OF INTERNAL COMBUSTION LEONTYEVA А.А. . ALTERNATIVE ENGINE. ALTERNATIVE DRIVER. NEW TYPES OF ENGINES. KNOW HOW. INTRODUCTION. PATENT. TECHNOLOGIES.

English

INVENTION. ENGINE OF INTERNAL COMBUSTION LEONTYEVA А.А. Patent of the Russian Federation RU2200858

Applicant's name: Leontyev Alexey Alekseevich
The name of the inventor: Leontyev Alexey Alekseevich
The name of the patent holder: Leontyev Alexey Alekseevich
Address for correspondence: 300025, Tula, ul.Oruzheynaya, 29a, ap. 71, AA Leontiev
Date of commencement of the patent: 2001.03.13

The invention relates to the field of engineering, in particular to engine building. The engine contains a disk spool with combustion chambers, injectors, inlet and outlet ducts, cylinder block, output shaft and crankcase with a pallet, cylinder block is made monolithic with a vertical hole in the center and with an axially parallel circle around the hole in a pair of compressor pairs with two pairs optimally in two Times the volume of the expansion cylinders, which together form the sides of the vertical and adjacent angles 72 and 108 o . In the compressor and expansion cylinders located on one side of the bisector of the angle of 108 ° , the monolithic pistons are located at the top dead points, and in the cylinders on the opposite side of the bisector of the angle of 108 ° the pistons are placed in the lower dead spots and are connected by rod parts to the roller bearings installed On the crankshafts of satellite gears fixed to the rim with the teeth of a semi-cylindrical shape formed on the rim, one of which is larger in size and connected monolithically to the crank neck in each satellite, and coupled to the troughs in the shape of the teeth of the inner ring of the fixed gears, two large rims Satellites and equal stroke of the piston. Supporting trunnions monolithically formed by protruding from the center of the ends of the paired satellites are placed eccentrically displaced by the value of one quarter of the stroke of the piston into the bearing holes of the half-shafts equipped with counter-weights at the inner ends of the crescent shape and at the outer ends - gears coaxially mounted on the bearings in the opposite sides of the crankcase Which together with the paired satellites are the primary shafts of the engine, kinematically connected to the gears fixed at the ends of the output shaft, located axially parallel between the primary shafts. The middle part of the output shaft by means of a pair of bevel gears, a vertical shaft installed in the central hole of the cylinder block and the gears is articulated with the inner ring gear of the central hole of the discs, along a circle coinciding with the arrangement of the holes in the cylinder cover, with inlet, outlet channels located along the Ends of the bisector of the angle of 72 ° , two nozzles installed at the ends of the bisector of the angle of 108 ° on the spool cover, in the disks are circumferentially arc length of 36 ° with equal intervals of five combustion chambers of bicylinder form with communicating holes in the adjacent bicylinder wall, with Volumes that provide them at least nineteen times the compression ratio of air and are in constructive agreement with the opening of the cylinder cover above the expansion cylinder and with the piston occupying the bottom dead center therein and with the possibility of rotating the disc for each stroke of the piston by a tenth of a revolution in the direction To the bisector of the angle of 72 ° from the expansion cylinder. The invention provides increased thermal and mechanical efficiency, efficiency, reliability and compactness of the engine.

DESCRIPTION OF THE INVENTION

The invention relates to the field of mechanical engineering, in particular to engine building, namely to internal combustion engines.

The engine design is known (see patent RU 2008476 C1, 5 F 02 B 75/32, 41/02, published February 28, 1994) containing a housing with opposing cylinders, monolithic opposing pistons disposed in cylinders and connected to a crank of the cheeks, rigidly Jointed with satellite gears, planetary gears with fixed gears with a circumference of twice the diameter of the circumference of the teeth of the satellites and equal to the stroke of the pistons, cylinder covers with gas distribution and fuel supply systems, the combustion chambers formed in each cylinder above the piston in the upper portion of its stroke , Variable and variable volume during the combustion time of the fuel.

Essential design disadvantages of the known engine are: firstly, a chamber of variable volume formed in the cylinders above the piston and a chamber of variable volume uninsulated from it in the upper portion of its stroke during the thermodynamic combustion process in it of fuel, which reduces the thermal efficiency of the engine; Secondly, the complexity of the rigid joint joint of the crank's cheeks with satellite gears and the ineffectiveness of the sliding bearings attached to the crank of the cheeks, and thirdly, the noncompactness expressed by the considerable overall length of the opposing cylinders with the gas distribution and fuel supply mechanisms located on their covers with complex structural support Kinematic connection with the output shaft.

The engine design is known (see patent SU 1643754 A1, 5 F 02 B 41/02, published on Apr. 23, 1991) containing a cylinder block with a compressor of small and larger cylinder volume, pistons with displacers at the ends arranged in cylinders and connected Connecting rods to the crankshaft, a common cylinder cover with holes passing through it to each cylinder housing a displacer protruding at the end of the piston, a spool casing located on the cylinder lid provided with two spring-loaded disks coaxially connected to the output shaft coaxially arranged one above the other, With the plane of the cylinder cover and the plane of the cover of the spool housing, in which combustion chambers of constant volume are formed with cylindrical thin-walled shells inside, which isolate the volume of the chambers from the inter-disk clearance gaps. The upper cover of the spool housing is provided with an inlet channel periodically injecting through the combustion chamber and through the holes in the cylinder cover atmospheric air into the compressor cylinder, an outlet channel periodically discharging through the hole in the cylinder lid and through the combustion chamber the exhaust gases from the expansion cylinder into the atmosphere and the nozzle, Connected kinematically with the shaft, periodically injecting fuel into the combustion chambers.

The main disadvantage of such engines, the pistons in which the connecting rods are attached to the crankshaft, is a large friction against the walls of the piston cylinders, caused by the inclination of the connecting rods during the rotation of the shaft, and the consequent need for a constructive increase in the height of the pistons and cylinders does not contribute to the compactness of the engine.

In addition, in such a design engine with one expansion cylinder, the piston in which it makes a working stroke only during each revolution of the shaft, there is uneven rotation of the shaft and power limitation.

The well-known traditional reciprocating engines (VEgoroshkin, BI Tseplovich, Fundamentals of Hydraulics and Heat Engineering, M .: Mechanical Engineering, 1981, p.228) , containing combustion chambers located in cylinders above the piston at the top dead center (TDC ), The compression ratio for which is chosen in practice depending on the type of fuel having a different ignition temperature. The degree of combustion for engines with the ignition of a combustible mixture from an extraneous source is 6-12 for gasoline workers and 5-9 for gaseous fuels. Smaller values ​​of the compression ratio lead to a decrease in efficiency, and large values ​​lead to a premature flash of the mixture before the arrival of the piston at TDC, which, in addition to reducing the efficiency of the cycle, leads to disruption in performance, accelerated wear, and shortened engine life.

In engines with self-ignition of fuel, the compression ratio should be within the range of 12-19. At a compression ratio of less than 12, the self-ignition of fuel in the compressed air chamber is not guaranteed, and at a compression ratio of more than 19, a very high pressure develops after the combustion of the fuel, reducing the efficiency of the cycle due to the danger of destruction of the combustion chamber caused by an equal diameter of the cylinder with the engine cylinder, The compression ratio, the smaller the volume of the combustion chamber, which is possible to produce a small diameter with the required wall thickness value isolated from the cylinder and capable of withstanding a greater pressure than the combustion chamber above the piston in the engine cylinder.

Thus, in the cylinders of traditional reciprocating engines, the combustion chamber formed in the TDC above the piston, not isolated from it during the combustion of the fuel, has a reduced strength characteristic, does not provide the actual isochoric cycle of the engine, reducing its thermal efficiency.

The technical result achieved in the implementation of the proposed invention is to increase the efficiency, power, structural compactness, simplify the engine arrangement and reliability.

This technical result is achieved by the fact that the cylinder block of the engine is made monolithically with a vertical hole in the center around which an axial and crosswise equidistant from the axis of the steam hole of the compressor with a pair of expansion tubes, optimally twice the volume of the cylinders that together constitute the sides of the vertical and adjacent angles At 72 and 108 o with monolithic pistons packed in each cylinder with displacers at the end, where the pistons are located at the top dead center (TDC) in the compressor and expansion cylinders located on one side of the bisector of the angle of 108 ° , and in the cylinders On the opposite side of the angle bisector, the pistons are placed at the bottom dead center (HMT) connected by rod parts to the roller bearings mounted on the crank necks held together by a pair of bushing sleeves of satellite gears with teeth on the rim made of a semi-cylindrical shape, one of which is larger in monolithic form And is connected to the crank neck in each satellite, coupled to the valleys corresponding to the teeth of the mold, made on the inner rim of the fixed gears by twice the rim of the satellites and equal in the direction of the piston, and the supporting journals projected from the center of the ends of the paired satellites are placed eccentrically offset by The value of one quarter of the stroke of the piston bearing openings of the half-shafts, equipped at the inner ends of a crescent-shaped counterweight and gears at the outer ends, coaxially mounted in the bearings on opposite sides of the crankcase, which together form the paired satellite gears, the primary shafts of the motor kinematically connected to the output shaft gears fixed to it Ends and axially located between the primary shafts in the crankcase and connected by its middle part by means of a pair of bevel gears, a vertical shaft passing through the central hole of the cylinder block and three cylindrical gears with teeth of the internal gear ring made through the holes of the spool discs, The circumference coinciding with the holes of the cylinder cover, the inlet and outlet channels located at the ends of the bisector of the angle of 72 ° , and two nozzles located at the ends of the bisector of the angle of 108 ° on the cover of the spool case, in the disks are formed with equal lengths along the arc in 36 O five combustion chambers of bicylinder form with communicating holes in bicylinder dividing adjacent wall, of which one bicylinder chamber is in alignment with the cavity of the open hole of the cylinder cover above the expansion cylinder and with the piston occupying the position of the HMT and the synchronous direction of rotation of the spool disc towards the bisector of the angle At 72 o , making a thirty-six-degree turn for each stroke of the piston.

Thus, according to the design of the proposed engine arrangement, which reduces the force flow from the compressor piston with the expansion cylinder through the hardened cheeks of the cranks of the two satellite gears with a semi-cylindrical shape of the teeth constituting the primary shafts, kinematically transmitting forces to the axis-parallel output shaft Engine, with successive provision with at least nineteenfold compression of air in five constant-volume cylindrical chambers isolated from cylinders with pistons for the time of injection and self-ignition in them of an isochoric engine fuel cycle that is "omnivorous" capable of all kinds of liquid fuel at high The degree of compression of air in it.

The construction scheme of the proposed device of the engine is shown in the drawings:

ENGINE OF INTERNAL COMBUSTION LEONTYEVA А.А.

FIG. 1 - a view of the engine from above with partial cutouts of the cylinder, slide valve and crankcase

FIG. 2 is a section along AA of FIG. 1 - along the axes of a compressor and expansion cylinder with monolithic pistons and along the axis of the engine's input shaft

FIG. 3 is a sectional view along the B-B of FIG. 1 - along the axis of the spool of the combustion chambers and transverse sections of three axes of shafts located in the crankcase

FIG. 4 is a longitudinal section along the BB in FIG. 1 in the spool, a separate bicylinder combustion chamber

5 shows a view of the ends of the fixed gear and the satellite gear

FIG. 6 - principle kinematic diagram of the engine

Radial directions according to the scheme graphically conditionally correspond to vertical directions in the device of the engine.

The engine contains a vertically located cylinder block 1, a cylinder cover 2 common to the block, a spool housing 3 mounted on a cylinder cover, a cover 4 on the top of the spool housing and a crankcase 5 with a tray 6 located at the bottom of the engine.

The cylinder block 1 is made monolithic with a vertical hole 7 in the center around which a pair of compressor 8 and 9 with a pair of expansion cylinders 10 and 11, integrally constituting the sides (see FIG. 1) of the vertical and adjacent corners in 72 And 108 ° . The volume of each of the expansion cylinders 10 and 11 is optimally twice as large as each of the compressor cylinders 8 and 9. A monolithic piston 12 is located in the compressor cylinder 8, and a monolithic piston 13 is located in the compressor cylinder 9. The monolithic piston 14 is located in the expansion cylinder 10, and In the expansion cylinder 11 is a monolithic piston 15. Propellers 16 are made at the ends of each of the pistons.

Cylinder cover 2 is provided with four, one for each cylinder, gas apertures 17 into which propellants 16 are included to reduce volume over the piston at their positions in the upper dead center (TDC).

The rectilinear-return motions of the pistons in the engine cylinders are converted by satellite-planetary mechanisms into rotation of the primary shafts located in the crankcase in an axially parallel manner on both sides of the bisector of the angles at 108 ° .

The piston 12 of the compressor cylinder 8 and the piston 15 of the expansion cylinder 11 arranged (see FIG. 1) to the left of the bisector of the angles at 108 ° and occupying the TDC position in the cylinders are connected to the left-side satellite-planetary mechanism (see FIG. 3) , Located in the crankcase 5, and the piston 14 of the expansion cylinder 10 and the piston 13 of the compressor cylinder 9 located (see FIG. 1) on the right side of the bisector of the angles 108 ° and occupying the position of the bottom dead center (BDC) in the cylinders are connected to the right Satellite-planetary mechanism placed (see FIG. 3) in the crankcase 5.

The kinematic connections of monolithic pistons with left and right satellite planetary mechanisms, which are located in parallel (see Fig. 3), are structurally similar to each other in accordance with Fig. 2, which shows a device of a satellite planetary mechanism located on the left side of the engine in which the rod part of the monolithic piston 15 of the expansion cylinder 11 is connected to the roller bearing 18 mounted on the neck of the crank 19 of the satellite 20, and the rod part of the monolithic piston 12 of the compressor cylinder 8 is connected to A roller bearing 21 mounted on the crank neck 22 of a satellite 23, crank necks 19 and 22 that are rigidly fixed to one another, with the satellites 20 and 23 being axially parallel, by means of a sleeve sleeve 24.

The satellite 20 is planetaryly rolled over a gear ring inside the stationary gear 25, and the satellite 23 is rolled inside by a stationary gear 26 whose diameters are twice the satellite diameter and equal to the stroke of the pistons, the teeth of the satellites 20 and 23 being made of a semi-cylindrical shape with one of them of a larger radius, Together with the crank necks 19 and 22, in which, in the inner rims of the fixed gears 25 and 26, cavities corresponding to the shape of the satellite teeth providing the necessary reliable strength characteristics to the crank pinions of the satellites are made (see FIGS. 3 and 5).

The support pin 27, integrally formed with the satellite 20 protruding from the center of its outer end, is placed in a bearing hole eccentrically offset by a quarter of the stroke of the piston from the axis of the central spigot 28 of the half-piece 29, and the support pin 30 integrally formed with the satellite 23 protruding from the center of its end is placed in a bearing hole eccentrically offset by one-quarter of the stroke of the piston from the axis of the central spigot 31 of the crotch 32.

At the inner end of the central spigot 31, the counterweight 33 is shaped like a crescent, and the counterweight 34 on the inner end of the central spigot 28 is of a crescent shape.

The pinion 35 is fixed on the shaft of the shaft 32 and the pinion 36 is fixed on the shaft. The central journals 28 and 31, located at opposite ends of the crankcase 5, are coaxially mounted in the roller bearings 37 and 38, and the outer ends of the half-shafts 29 and 32 are mounted in the side bearings Covers 39 and 40 of the crankcase 5. The half-shafts 29 and 32 together constitute the left-side primary motor shaft (see FIG. 2), sensing the forces of the working strokes of the piston 15 of the expansion cylinder 11 and transmitting them (see FIG. 3) via gears 35 and 36 to The gears 41 of the engine output shaft 42 fixed at its ends. The right-side primary motor shaft of FIG. 3, on the right side similarly to the left-side primary shaft, senses the forces of the working strokes of the piston 14 of the expansion cylinder 10 and transfers them to the end gears 41 of the engine output shaft 42. Moreover, the pistons 14 together with the piston 13, articulated with the right-handed primary shaft, are in the position of the NTM, and the piston 15, together with the piston 12, which are articulated with the left-side primary shaft (see FIG. 3), are in the TDC position in opposition to them.

The middle of the output shaft 42, through (see FIG. 3), two bevel gears 43 and 44, a vertical shaft 45 passing through the opening 7 formed in the center of the cylinder block 1, and then along the gear 46 and the gears 47 adjacent to it from both sides 47 And 48 is connected to the toothed inner rims 49 of a pair of spool discs 50.

In the spool disks 50, five combustion chambers 51 of constant volume are formed with at least nineteenfold compression ratio of air, a bicylinder shape, with thin-walled cylindrical shells 52, inside the insulating volumes of the bicylinders from the inter-disk clearance gaps. In the adjacent wall of the chamber, holes 53 are formed to communicate the two cylinders of chamber 51 to each other.

The length of the bicylinder chamber 51 and the distance between the chambers is 36 ° along the arc of the rotation circle of the chambers coinciding with the arrangement of the holes 17 in the cylinder cover 2 and with the arrangement of the holes of the inlet channels 54, the outlet channels 55 and the two nozzles 56 located on the spool cover 4.

The nozzles 56 are mounted on the cover 4 of the spool case 3 at diametrically opposite intersection points (see Fig. 1) of the bisector of the angle 108 ° with the rotation circle of the combustion chambers 51 located in the spool disks 50.

Between the discs 50 are springs 57 pressing the upper disc to the cover 4 of the spool housing, and the lower disc to the cylinder cover 2, ensuring continuous contact of the rotating discs with the covers.

The kinematic connection of the monolithic pistons 12, 13, 14, 15 of the cylinder block 1 to the spool discs 50 provides for the discs in one stroke of the pistons a thirty-sixty degree turn or a tenth of their revolution, with complete agreement between the combustion chamber 51 occupied, the position above the port 17 of the cylinder cover 2 in the expansion Cylinder 10 with the position of the BHM of the piston 14 and the retention of the movement of the chamber from the expansion cylinder towards the bisector of the angle of 72 ° .

It should be noted that the volume of the expansion cylinder is optimally two times that of the compressor cylinder. Large volumes of expansion cylinders, firstly, are associated with an increase in the mass of pistons and dynamic tension, secondly, with a high degree of expansion of exhaust gases to the pressure at the end of the expansion below atmospheric and, thirdly, the compactness with the complication of the arrangement of the engine cylinders decreases.

The engine is operated as follows.

In Fig. 6 presents a conditionally graphically simple kinematic diagram of the circular thermodynamic cycle of a continuous engine operation with five bicylinder combustion chambers 51 made in spool discs 50 in a schematic diagram graphically depicted in the form of concentric rings together with an outer ring representing the cover 4 of the spool housing with inlet 54 outlet 55 channels and nozzles 56 thereon, and below to the center of the circuit is an inner ring representing a cylinder cover 2 with holes 17 therein for each cylinder, and in a radial direction to the center of the circuit, a pair of compressor cylinders 8 and 9 with pistons 12 and 13 And a pair of expansion cylinders 10 and 11 with pistons therein 14 and 15 radially disposed with central angles of 72 and 108 ° between themselves synchronously interacting with the bicylinder combustion chambers 51 conventionally designated in the diagrams K1, K2, K3, K4, K5 .

So, the chamber K1, indicated on the diagram, located above the fully open hole 17 of the cylinder cover 2 in the expansion cylinder 10 with the piston 14 reaching the BDC, completed the process of expanding the gases of the fuel burned in it, and the piston in the cylinder finished the working stroke coinciding with the beginning of the piston motion To TDC and the start of the subsequent process of expelling exhaust gases from the expansion cylinder 10 through the opening 17, through the chamber K1 and through the outlet channel 55 to the atmosphere in a synchronous thirty-six-degree turn of the discs with the chamber K1 towards the bisector of the angle of 72 ° and to the exhaust 55 and the inlet 54 channels .

The chamber, indicated on the K2 diagram, located at that moment above the fully open cylinder cap hole in the compressor cylinder 9 with the piston 13 reaching the BDC, completed the process of letting the volume of the cylinder of air from the atmosphere, discharged above the piston, through the inlet channel 54, the chamber K2 and the opening in Cylinder cover, and in the synchronous continuation of the rotation of the disk with the chamber K2 and the reverse movement in the TDC of the piston 13, the process of compressing air in this chamber begins to at least nineteenfold with its isolation from the cylinder. In this case, the compressed air residue in the harmful space above the piston in the TDC is expended on purging the previous chamber K1 from the residues of the exhaust gases in it through channels 54 and 55 into the atmosphere.

The chamber with the volume of compressed air in it, indicated in scheme K3, completely isolated from the cylinders, completed the process of self-ignition and combustion of the mixture with air injected into it from the fuel nozzle 56 during the thirty-six-degree rotation of the chamber under the nozzle synchronously coinciding with the start of the high-pressure gas inlet From the chamber to the expansion cylinder 11 with the TDC piston 15 occupied therein, which senses the pressure of the expanding gases coming from the chamber through the opening holes in the cylinder cover to accomplish the next working stroke from TDC to BDC.

In the chamber indicated in the diagram, K4 at this moment under the outlet 55 and the inlet 54 channels, the process of expelling the exhaust gases to the atmosphere from the expansion cylinder 11 by the piston 15 located in the TDC synchronously coincided with the start of air intake from the atmosphere through the inlet channel 54 Through the chamber and the opening opening in the cylinder cover into the compressor cylinder 8 with the beginning of the movement of the piston 12 from TDC to BDC.

In the K5 chamber at this moment, the process of air compression with its complete isolation from the compressor cylinder 8 synchronously coincided with the start of the intake through the fuel injector 56, self-ignition of the fuel in the mixture with air and the beginning of its combustion during the time of the chamber K5 moving to the expansion cylinder 10 for thirty-six degrees Its rotation in accordance with the displacement in the cylinder of the piston 14 from the HMT to the TDC.

This ends the circular thermodynamic cycle of the engine and continues its new cycles of continuous operation, in which the described processes are alternately repeated with the participation of each of the five bicylinder chambers in synchronous agreement with the movement of the pistons within the dead dead spots of the compressor pair and the pair of expansion cylinders of the unit.

CLAIM

An internal combustion engine comprising a compressor unit and a larger volume of expansion cylinders, pistons disposed in cylinders with protruding extruders at the end, a common cylinder cap with holes in each cylinder disposed in a housing on the cylinder cover two coaxially mounted one above the other and spring-loaded relative to one another The spool of the spool, which is adjacent to the cylinder cover and to the cover of the casing, with combustion chambers formed in them, covered from within with cylindrical thin-walled casings, isolating the chamber volumes from the disk intertool spacings, the spool case casing with the inlet channel periodically entering through the combustion chamber and through the cylinder opening Covers the atmospheric air into the compressor cylinder, with an outlet channel periodically discharging the exhaust gases from the expansion cylinder through the opening of the cylinder cover and through the combustion chamber to the atmosphere, with an injector periodically injecting fuel into the combustion chamber, an output shaft kinematically connected to the pistons of the cylinders and to the discs A spool and a crankcase with a pallet installed in the base of the cylinder block, characterized in that the cylinder block is made monolithic with a vertical hole in the center and with an axially parallel circle around the hole with a pair of compressor pairs with an optimally two times larger volume of expansion cylinders constituting in The combinations of the sides of the vertical and adjacent angles 72 and 108.degree . , In the compressor and expansion cylinders located on one side of the bisector of the angle of 108.degree . , The monolithic pistons are located at the top dead points, and in the cylinders located on the opposite side of the angle bisector, Monolithic pistons are located in the lower dead spots connected by rod parts of pistons to roller bearings mounted on crank journals of satellite gears fastened with a pair of sleeve couplings with riveted teeth of a semi-cylindrical shape, one of which is larger in size and connected monolithically to the crank neck of each satellite, With troughs in the shape of the teeth of the inner ring of fixed gears, twice the rim of the satellites and equal to the stroke of the piston, and the supporting trunnions monolithically projected from the center of the ends of the paired satellites are placed in eccentrically displaced by the value of one quarter of the piston stroke, the bearing holes of the half-shafts Inner ends of a crescent shaped counterweight and at the outer ends - gears coaxially mounted on bearings on the opposite sides of the crankcase and constituting together with the paired satellites the primary shafts kinematically connected to the gears fixed at the ends of the output shaft located axially parallel between the primary shafts and connected by its middle part , A pair of bevel gears, a vertical shaft installed in the central hole of the cylinder block, and cylindrical gears with an inner ring gear of the central hole of the discs, with a circumference coinciding with the arrangement of the holes in the cylinder cover, with inlet and outlet channels located at the ends of the bisector of the angle in 72 ° , two nozzles installed at the ends of the bisector of the angle of 108 ° on the spool cover, the discs are made at equal intervals with an arc length of 36 °, five cylinders of combustion of bicylinder form with communicating holes formed in the adjacent wall of the cylinder and the volumes providing them At least nineteen times the degree of air compression, and in agreement with the opening of the cylinder cover above the expansion cylinder and with the piston occupying the lower dead point in it and with the possibility of rotating the disc for each stroke of the piston by a tenth of a turn in the direction of the bisector of the angle of 72 O from the expansion cylinder.

print version
Date of publication 28.12.2006гг