RU1813895C - Internal combustion engine - Google Patents

Abstract

Usage: the invention allows to redistribute the thermal balance of the engine in the direction of a significant increase in efficiency, increase liter and specific power, reduce toxicity, eliminate pressure drop during exhaustion by interconnecting changing the configuration and size of parts of the engine components, introduce pressurization of the cylinder and the core - rhenium of combustible gases. The engine comprises a housing 1 with an internal drive 10, a rotor 2 with a cylinder 11 and opposed pistons with support rollers interacting with the drive 10 to form the cavities of the pressure pump 19 and the expansion engine 15. The engine makes two working strokes per revolution. When the rotor 2 rotates, the pistons with supporting rollers, following the profile of the driver 10, perform reciprocating movements, the air that is sucked into the cavity 19 is blown into the cavity of the cylinder 11. After the working stroke in the cylinder 11, the working fluid enters the expansion chamber 15, where, having additionally given energy to the rotation of the rotor 2, the exhaust gas is squeezed out of the expansion chamber by pistons and support rollers. 8 ill. x fe

Description

The invention relates to mechanical engineering, in particular to internal combustion engines. It can be used in transport and stationary installations,

The purpose of the invention is to increase the efficiency, increase the specific and liter power without increasing the number of mutually moving parts in the engine.

The specified goal of redistributing the heat balance of the engine is achieved:

a) reduction of heat loss during cooling, by reducing the areas of the most intense heat loss in the engine - by burning combustible components in a chamber with a smaller area by means of a recharging (pressurization), that is, a significant reduction in the main areas of heat leakage into the cooling system (passing through the ends pistons and the inner surface of the working cylinder);

b) intensification of combustion processes and more complete combustion as a result of increased pressure, as well as more complete combustion due to the extension of the secondary combustion process, expansion;

c) using thermal energy contained in the burned gases to rotate the engine by means of secondary, continued expansion of the combustion products, which includes, in addition to compensating for the energy expended on boosting, and the supply of additional energy from the complete expansion of the burned gases and lowering the exhaust temperature; however, the non-increase in the number of mutually moving parts of the engine compared to the prototype is achieved by an interconnected change in the configuration and size of the parts that make up the engine, with the formation of variables when the engine rotates through the volume of the cavities that serve as a blower and a re-expansion engine.

An internal combustion engine comprising a housing with a profiled inner surface, a rotor with a cylinder in which opposed pistons are located with support rollers interacting with the internal profiled surface of the housing, with the formation of a combustion chamber between the pistons, and channels and discharge cavities covering the cylinder are made in the rotor, with the rotor, a cavity with check valves is formed, between the rotor and the housing there are formed hermetic expansion cavities associated with the combustion chamber of the channel E in the rotor, and injection cavity associated with the cavity when the rotor and the combustion chamber through check valves. An essential distinguishing feature that determines the presence of new properties manifested in the proposed solution is that the internal volume of the casing is made in the form of a boost pump (with Pmax 4 atm) and a re-expansion engine (with Pmax 8 atm) formed by the rotor, pistons and support rollers, for which channels and injection cavities covering the cylinder are made in the rotor, a cavity with check valves is made in the rotor (in the piston), and hermetic expansion cavities are connected between the rotor and the housing and connected to the chamber burn channels in the rotor, and discharge

5 cavities are associated with the cavity in the rotor and with the combustion chamber by means of check valves.

Expected positive effect: adiabatization of the combustion process, i.e.

0 redistribution of the heat balance of the engine in the direction of a significant increase in the proportion of heat converted to mechanical energy, an increase in efficiency by a decrease in heat loss, an increase in liter and

5 specific power of the engine due to boost and over-expansion; reduction in engine toxicity, since the amount of fuel burned per unit of power is reduced, and the process of oxidizing fuel is also prolonged; there is no need to use an exhaust silencer, since the pressure and temperature of the exhaust are insignificant, the exhaust process is extended over time (displacement of exhaust gases from

5 expansion cavities occurs evenly and continuously, since during the operation of the engine the exhaust windows, beyond. by turning on several degrees of their overlap with support rollers, open

0 constantly).

In FIG. 1 shows the proposed engine; in FIG. 2 - the piston; in Fig.3 - rotor; in FIG. 4-7 - section of the engine in plan; in FIG. 8 is a section AA in FIG. 4; in FIG. 9 5 section BB in FIG. 4.

The engine consists of six main parts; housing 1, rotor 2, pistons 3 and 4, support rollers 5 and 6.

The housing 1 of the engine is hermetically made in the form of a hollow duct with an internal O-shaped profile, closed on both sides by side surfaces, with a ratio of internal dimensions; the smallest diameter equal to 2 R, the largest 2.75 R and

5 with a width of 1 R. The opening of the shaft support sleeves 8 and the inlet windows 9 is made in the center of the planes, and the hole for the outlet windows 7 is at the junctions of the side planes with the profile along the smallest diameter. The rotor 2 of the engine is cylindrical

forms, with a circle radius of 1 R and a width of 1 R, with a diametrically located barrel of the working cylinder 11 having through grooves 12 for the axis of the support roller, and with pockets 13 adjacent to the barrel, corresponding to the sizes of the piston 3 and 4 with support rollers 5 and 6 and placed in said pockets 13. In the rotor body, channels of burnt gases 14 are made, which communicate with the combustion chamber of the working cylinder 11c by extension tubes 15. The rotor 2 is installed in the housing 1 on the axis 16, in which the inlet windows 17 and the channel are made fuel supply 18 c hindr. The rotor is an engine flywheel. The piston 3 and 4 with the support roller 5 and 6 form a body with a diameter of 1 R, a width of 1 R in the aggregate being a low pressure piston, both in the boost 19 and in the expansion chamber 15, The piston 3 and 4 covers the barrel of the cylinder 11 In the piston 3, a control high-pressure inlet piston 20 is made with a cavity for delaying a portion of fresh charge 21 (pre-compressed air chamber) and an intake valve 22, a pressure valve 23. A high-pressure exhaust piston 24 is made in the piston 4. The piston 20 and 24 are inside the cylinder 11, through the groove 12 and the piston body 3 and 4 passes the axis of the support roller 5 and b. The cavity of the charge pump 19 and the cavity of the extension 15 are formed by the housing 1, the rotor 2, the pistons 3 and 4 with the support rollers 5 and 6. Interacting often - the housing 1, the rotor 2, the pistons 3 and 4, the support rollers 5 and 6, are made from a material with low coefficients of thermal expansion and processed with the necessary accuracy, up to precision, providing acceptable tightness of the cavities of the charge pump and expansion engine, or equipped with sealing seals. The tightness of the charging 19 and the expansion chamber 15 is facilitated by a low maximum working pressure, up to about four atmospheres in the charging and eight atmospheres in the expansion chamber, as well as low maximum temperatures in them. In addition, the joint arrangement of the working cavities in the sealed housing 1 eliminates the possibility of the working fluid entering the environment in a different way than through the exhaust system. Another sealing factor, when the cavities are located in one housing, the difference in pressure between the cavities 19 and 15 is significant, 2 times lower than

pressure difference between each cavity and atmosphere.

The engine operates on a two-stroke basis. For one revolution, two working 5 strokes are made. When the rotor is rotated 90 ° clockwise (Fig.6) from the position of the maximum proximity of the pistons 3 and 4 (bm), the inlet windows 9 on the housing 1 open, the support rollers 5 and 6 under the action of 0 centrifugal force follow the profile set point 10, the pistons 3 and 4 are extended to the maximum value (bw), air is sucked into the cavity of the pump’s boost-foot, ending with closing

5 inlet windows 9. Then, over 90 °, the pistons 3 and 4 come together and displace the pre-compressed air through the discharge valve 23 into the cavity 21. of the inlet piston 20. In bm discharge

0 valve 23 closes. After 90 °, when the pistons approach NMT, the pressure of a portion of fresh air opens the intake valve 22, since the pressure in the working cylinder T1 has dropped by this time. There is a complete displacement of the burnt gases and their replacement in the cylinder 11 with a fresh portion. The beginning, the displacement of the pistons, is accompanied by the closing, by the action of compressible air, of the inlet valve 22.

0 At the end of the compression stroke along the fuel supply channel 18, a fuel injection is injected; go into the cylinder. 8 positions of the maximum approximation of pistons 3 and 4 (bhp), the combustible mixture ignites, then within 90 °

5, the working stroke continues in cylinder 11, the opening of the burned gas channel by the exhaust piston 24, the discharge of the burnt gas pressure into the cavity of the expansion engine, the beginning of the working stroke in the expansion chamber 15, the pressure of the remaining charge of the burnt gases from the cylinder displacing into the expansion chamber 15, closing the inlet valve 22 and the continuation of the stroke in the expansion valve,

5 .engine. Due to the significant volume of the expansion chamber 15, the pressure with the process of increasing the volume decreases to close to atmospheric, and the temperature of the waste gases also decreases. After the next 90 °, with the approach of the pistons 3 and 4 to VMT support rollers 5 and 6 open the outlet windows 7 in the housing 1 of the engine. Further, during 180 °, i.e. during two cycles of operation of the pistons 3 and 4, the exhaust gases are displaced from the expansion cavities 15 by low pressure pistons, which ends when the exhaust windows 7 are closed by the support rollers 5 and 6 in position c. mt So

Thus, the alternate passage of the working fluid through the engine sections is completely completed through 720 °. However, since the processes in the charge pump, the working cylinder and the expansion engine go simultaneously, in parallel, the duration of the full cycle can be taken as 180 °, since every half revolution the engine absorbs and throws out another portion of the working fluid, from the position of the greatest distance (m .t.) pistons 3 and 4 perform a compression stroke, occupy the position of BMT Over these 90 °, the following happens in parallel:

a) closing the inlet windows 9 in the housing 1, leaking pre-compression in the cavity of the charge pump and displacing the compressed air. through the discharge valve 23 into the cavity 21 of the intake piston 20 (cavity for delaying the portion of fresh charge);

b) closing the intake valve 22 and compressing the air contained in the cylinder 11 between the pistons 20 and 24. At the end of the compression stroke, fuel injection through the fuel supply channel 18 and ignition of the fuel mixture;

c) the course of the working stroke in the expansion chamber 15, which ends when the pistons 3 and 4 approach the BMT. opening of exhaust windows 7;

d) continued displacement of the exhaust gas through the exhaust ports in the housing 1 from the extension chamber by 16 low pressure pistons; following 90 °:

a) opening the inlet windows 9 in the housing 1, increasing the volume of the cavity in the charge pump and filling it under the action of discharge with a fresh charge of air;

b) the working stroke in the cylinder 11, when approaching nm.m. exhaust piston 24

opens the channels of the burnt gases 14, and the burnt gases enter the pre-expansion cavity 15, after the pressure drops, the inlet valve 22 opens with a fresh charge of compressed air in the chamber 21

and crowding out. cylinder 11 of residues of burnt gases;

c) the formation of a re-expansion cavity 15, with the entry of burnt gases - the beginning of the working stroke in a re-expansion engine;

d) displacement of the exhaust gas from the expansion cavities by 15 low-pressure pistons, closing by the support rollers 5 and b of the exhaust windows 7 in the housing 1.

FORMULA AND SECTION

An internal combustion engine comprising a housing with a profiled inner surface, a rotor with a cylinder in which opposed pistons are located with support rollers cooperating with the inner profiled surface of the housing to form a combustion chamber between the pistons, characterized in that, in order to increase the efficiency,

the engine is additionally equipped with injection cavities and channels in the rotor, between the rotor and the casing there are formed hermetic expansion cavities connected with the combustion chamber by channels in

the rotor, and the discharge cavities are connected to the combustion chamber by means of check valves.

FIG. 2

FIG. 3

FIG. H

“Riga. 5

Compiled by P. Derksen Editor N. Rozhkova Tehred M. Morgenthal Corrector A. Kozoriz