RU2455507C1 - Method for running cycle realisation and design of pulse internal combustion engine - Google Patents

Abstract

FIELD: engines and pumps.

SUBSTANCE: as a working medium discrete gas flow generated using compressor and pulse combustion chamber is used. At that quantised portions of working medium, generated by means of pulse combustion chamber by set of generation microprocesses including successive formation of working mixture, combustion of working mixture upon constant volume and thermodynamic expansion of working medium, are accumulated in succession during piston full travel in cylinder of preliminary expansion.

EFFECT: increasing specific useful energy efficiency of running cycle of internal combustion engine due to partial recuperation of energy losses during compression and expansion.

3 cl, 7 dwg

Description

The invention relates to engine building and mainly for automobiles, tractors, etc.

Further, the internal combustion engine is an internal combustion engine. Known (hereinafter referred to as analogues) is a method of implementing a duty cycle and an ICE device with heat supply at a constant volume, used in modern piston gasoline and gas ICEs [1, 2].

The practical interest in these ICEs is due to the fact that the ICE duty cycle with heat supply at a constant volume (Otto cycle) is a good approximation to the theoretical Carnot cycle, which provides the highest efficiency (hereinafter - efficiency) compared to other possible operating cycles of heat engines, working with a fixed mass of the working fluid in a simply connected working space with a limited variable volume (in this case, in working cylinders with a movable piston).

The disadvantage of the above analogues is the significant and fundamentally irreplaceable with this method of implementing the internal combustion engine operating cycle energy losses in the compression and expansion processes that determine the energy balance of the engine. In addition, the Otto cycle imposes significant restrictions on the properties of the fuel, the method of mixture formation and the thermodynamic parameters of the generated working fluid, and ultimately on the resulting indicator and effective indicators of a traditional piston engine.

Closest to the proposed method for the implementation of the working cycle and the device of a pulsating ICE are the well-known (hereinafter referred to as prototypes) method of implementing the working cycle and the device of a five-stroke ICE (patent RU 2326250 C1: A.F. Ravich, V.N. Opryshko, A. S. Kutin The method of implementation and the device five-stroke internal combustion engine). In this ICE, the working fluid is the stationary gas stream generated by the sequence (compressor → constant pressure combustion chamber), and pre-expansion cylinders and subsequent expansion cylinders are used as energy converters of the working gas stream to useful work. In the process of preliminary expansion, the cylinder space released by the moving piston is synchronously replaced by the corresponding new mass of the working fluid from the combustion chamber, i.e. the variable accumulating mass of the working fluid is working. At a certain ratio of the flow rate of the working fluid for the full stroke of the piston and the volume of the cylinder, the pressure and density of the working fluid during this process will be constant (the same as in the combustion chamber) and part of the energy spent on compressing the air in the compressor is recovered. In the cylinder of subsequent expansion of a larger volume, the process of polytropic expansion of the working fluid spent in the cylinder of preliminary expansion is carried out. With the same flow rate of the working fluid and ceteris paribus, this engine theoretically significantly (by 15-30%) surpasses the traditional piston internal combustion engine in terms of the main indicator indicators - efficiency, power and specific fuel consumption. The lack of prototypes is energy losses in the expansion process. In addition, when implementing a five-cycle internal combustion engine with a centrifugal or axial compressor, anti-surge automatics should be provided to prevent possible reverse operation from the combustion chamber to the compressor (surge) in the “off-design” mode.

The technical result of the claimed invention is an increase in the specific (per unit mass of the working fluid) useful energy output of the ICE working cycle due to the partial recovery of energy losses in the compression and expansion processes.

This means superior in terms of efficiency, power and specific fuel consumption compared to analogues and prototypes with the same flow rate of the working fluid and all other conditions being equal.

The above technical result provides the proposed method for the implementation of the duty cycle in an internal combustion engine, including sequentially:

process of generating a working fluid

by means of a compressor, a fuel supply device and a combustion chamber,

the process of accumulation and pre-expansion of the working fluid in the pre-expansion cylinder,

process of thermodynamic subsequent expansion of the working fluid from the cylinder pre-expansion

into the cylinder of the subsequent expansion,

exhaust process

from the cylinder of the subsequent expansion,

and different from the prototype in that

the process of generating a working fluid is carried out discretely, sequentially accumulating, over a full stroke of the piston, in the pre-expansion cylinder quantized portions of the working fluid generated by a pulsating combustion chamber by a series of microprocesses of generation, including sequentially forming the working mixture, burning the working mixture with a constant volume and thermodynamic expansion of the working body.

The above technical result is provided by the proposed internal combustion engine,

including in series:

compressor,

combustion chamber

pre-expansion cylinders,

expansion cylinders,

a system for automatically controlling gas exchange between the combustion chamber and the preliminary expansion cylinders, between the preliminary and subsequent expansion cylinders and between the subsequent expansion cylinders and the external environment,

power take-off mechanism

and different from the prototype in that

Instead of a constant pressure combustion chamber, a pulsating combustion chamber is used, which generates a discrete working gas stream that accumulates a working fluid with a pressure not lower than the compression pressure and with a density lower than the compression density in the compressor during the full stroke of the piston in the pre-expansion cylinder.

A pulsating combustion chamber includes an inlet flap, with a certain frequency blocking or opening the channel (compressor → combustion chamber) for a full stroke of the piston, and an automatic synchronizer device that controls the flap options, responding to changes in the working fluid pressure in the space between the flap and the piston in pre-expansion cylinder;

the valve is opened at the moment when the pressure of the working fluid in the space between the closed valve and the piston becomes equal to a predetermined value less than or equal to the inlet pressure from the compressed air compressor or working mixture;

in the interval between the opening and subsequent closing of the damper in the combustion chamber with the help of a compressor, the charge of the compressed working combustible mixture is formed, after which the combustion process is initiated;

the shutter is closed at the moment when the pressure of the working fluid as a result of the initialization of the combustion process exceeds a predetermined value;

in the period between the closing and the subsequent opening of the valve, a preliminary expansion of the working fluid is carried out;

at the moment of completion of the forward stroke of the piston, the combustion chamber is switched to another cylinder of preliminary expansion, and during the reverse stroke of the piston, the subsequent expansion of the working fluid into the cylinder of the subsequent expansion of a larger volume is carried out;

in the process of the piston return stroke in the cylinder of the subsequent expansion, the spent working fluid is released.

The following is the theoretical justification of the invention, including thermodynamic analysis and assessment of the competitiveness of the proposed engine.

We consider the minimum configuration of the proposed engine, consisting of two tandem blocks, which consistently include two cylinders of preliminary and subsequent expansion.

A schematic diagram of such an engine configuration is shown in FIG. The table in figure 2 shows the dynamics of the state of the elements of the power unit during the two subsequent phases of the duty cycle, during which the working volumes of the cylinders monotonically change from zero to maximum (forward stroke) and vice versa (return stroke) or vice versa.

From this table it can be seen that for one synchronous piston stroke in the cylinders of the proposed engine of the minimum configuration, two working strokes are performed.

Thermodynamic analysis of a pulsating ICE

The following abbreviations and notation are taken:

KS - pulsating combustion chamber,

C1 - the first working cylinder of the preliminary expansion;

C2 - the second working cylinder of the subsequent expansion;

PC - working mixture (air + fuel at the beginning of the combustion process),

RT - working fluid (combustion products in the process of expansion);

p - pressure (MPa), r - density (kg / m ³ ), T - temperature (K),

t - time (s), v - speed (m / s),

V is the volume (m ³ ),

G - fuel consumption, air, RT (per piston stroke kg, second kg / s),

Δq is the specific amount of heat (MJ / kg of working fluid);

the indices _{a, c, b, z, d, e} denote respectively:

_a - air parameters at the inlet to the compressor,

_C is the process of compressing air in a compressor,

_b - the process of intake of compressed air from the compressor,

_z is the process of supplying heat to the COP,

_k is the process of accumulation of combustion products,

_d - the process of preliminary expansion of RT in C1,

_e is the process of the subsequent expansion of the RT in (C1 → C2).

Initial data:

a) inlet air parameters r _a , p _a , T _a , air compression ratio ε,

b) min (air / fuel) of complete combustion m _af (kg / kg), coefficient of excess air α,

c) second fuel consumption G _f = const, fuel consumption per piston stroke G _fS ,

d) piston stroke S (m),

e) specific heat input Δq (MJ / kg RT),

f) CS ripple frequency ν (Hz).

Piston speed v _p . In order to simplify the analysis, the condition v _p = const is further adopted.

The method of forming a charge of a working combustible mixture

Next, a scheme of distributed injection of liquid fuel during the intake of compressed air from the compressor is adopted, which ensures the formation of a charge of the working combustible mixture directly in the compressor station.

Air and working fluid consumption

Secondary air flow rate G _a (kg / s), per piston stroke G _aS (kg):

G _a = G _f · m _a = const, G _aS = G _fS · m _a , where

m _a = α m _af .

RT flow rate second G _z (kg / s), per piston stroke G _zS (kg):

G _z = G _f + G _a = G _f · m _z = const, G _zS = G _fS + G _aS = G _fS · m _z (kg), where

m _z = 1 + m _a .

Work processes

Compressor air compression process

The initial state of the process: p _a , r _a , T _a ; final state:

,

,

, где n_c - показатель политропы сжатия.

,

,

, where n _c is an indicator of the polytropic compression.

Compressed air inlet process from compressor

During the intake process, compressed air from the compressor displaces previously exhausted combustion products from the compressor station into the space Ts1 released by the piston. Synchronization of the shutter options with the movement of the piston (details below) ensures the process at constant pressure and density: p _b = const = p _c , r _b = const = r _s .

Pre-expansion process.

The initial state of the process is determined by the final state of the process of heat supply to the compressor:

r _z = r _c · (m _z / m _a ), p _z = p _c · µ · (T _z / T _c ), where m _a , m _{z as} defined above, µ = R _z / R _c , R _c , R _z - specific gas constant, respectively, RS, RT (MJ / (kg · K)); temperature T _z is found from the well-known combustion equation for the case of heat input at a constant volume

ξ _z · Δq = u _z -u _c , where

ξ _z <1 - heat utilization coefficient,

Δq is the specific amount of heat supplied (MJ / kg of working fluid),

u _z = (R _z / R) · mcV [T ₀ , T _z ] · (T _z -T ₀ ), u _c = (R _c / R) · mcV [T ₀ , T _c ] · (T _c - T ₀ ) is the amount of internal energy at the end, the beginning of the process, mcV [T ₀ , T] = mcV ₀ (TT ₀ , α) is the tabular heat capacity of RT (MJ / (kmol · K)) in the temperature range [T ₀ , T]

T ₀ = 273.15 K,

R = 10 ^-3 · 8.3144 (3) MJ / kmol · K is the universal gas constant.

Final state of the pre-expansion process:

,

,

где

,

,

Where

λ = p _z / p _c , n _d is the indicator of polytropes of preliminary expansion.

The process of accumulation of the spent working fluid in the cylinder pre-expansion

At the time of completion of the preliminary expansion process, the corresponding next portion of the working fluid is attached to the mass of the previously worked working fluid in C1. Synchronization of the flapper options with the movement of the piston (details below) ensures the implementation of this process at constant pressure and density:

p _k = const = p _c , r _k = const = r _d .

Subsequent Expansion Process

The initial state of the process: p _d = p _c , r _d , T _d ; final state:

,

,

где

,

,

Where

V ₂ > V ₁ - a given volume of C2, V ₁ - volume of C1,

δ = r _d / r _e ,

n _e is an indicator of polytropes of subsequent expansion.

Workflow synchronization

The synchronization of working processes in the proposed engine provides a lower pressure level in C1, exceeding the compression pressure p _s , over the full stroke of the piston.

Piston full stroke time interval:

t _S = S / v _p = G _fS / G _f = G _aS / G _a = G _zS / G _z (c).

Period and number of ripples

Ripple Period:

t _ν = 1 / ν (s).

The number of pulsations KS for the full stroke of the piston:

c _ν = t _S / t _ν = t _S · ν.

Further, in order to simplify the analysis, it is assumed that the ripple period t _ν is consistent with the period of the working cycle, i.e. in the time interval of the full stroke of the piston "fits" an integer number of pulsations:

c _ν = integer.

Air Charge Parameters

Mass, volume (= volume of COP), respectively:

ΔG _b = G _aS / c _ν , V _c = ΔG _b / r _c .

Synchronization of volumes released by the piston space

In the proposed engine, the processes of intake and preliminary expansion are synchronized with the stroke of the piston so that the pressure p _c and density r _{d of the} displaced (spent in the processes of previous pulsations) RT do not change. Such synchronization is ensured with the following values of the corresponding volumes ΔV _b , ΔV _{d of the} space C1 released by the piston:

(inlet)

ΔV _b = V _c ,

(preliminary extension)

.

.

With each subsequent pulsation, the mass of the spent working fluid (combustion products) in C1 increases by:

ΔG _k = G _zS / c _ν

Synchronously, by

ΔV _k = V ₁ / c _ν ,

the volume of space freed by the piston in C1 increases.

Based on the data above the synchronization conditions:

.

.

Wherein:

r _k = ΔG _k / ΔV _k = r _d ,

p _k = p _c .

Pre-expansion cylinder volume

From the previous it follows:

.

.

Interval and pre-expansion time intervals

From the previous for the corresponding time intervals t _b and t _d it follows (s _b and s _d - the corresponding intervals of the piston stroke):

. On the other hand:

t _b + t _d = t _ν .

Searched time intervals:

,

.

,

.

These formulas provide a complete calculation of the proposed engine based on the data of a pulsating combustion chamber, or, conversely, a complete calculation of a pulsating combustion chamber based on the data of the working cylinders.

Specific work cycle

The following is determined (theoretical indicator) specific (per 1 kg RT) work I _{i of the} proposed cycle:

I _i = I ₁ + I _e , where

I ₁ - the resulting specific work of the processes

in the compressor and in the working space (KS → Ts1),

I _e is the specific work of the process of subsequent expansion in (Ts1 → Ts2).

The specific work of the air compression process in the compressor:

I _c = - (p _c / r _c -p _a / r _a ) / (n _s -1) · (m _a / m _z ) <0.

Specific work processes in the workspace

(combustion chamber → first cylinder)

In the workspace (KS → Ts1) there are three processes:

_b - the process of intake of compressed air from the compressor,

_d - the process of preliminary expansion of the RT as a result of combustion in the COP of the charge of the working combustible mixture,

_k is the process of accumulation of spent RT.

From the above thermodynamic analysis it follows:

I _b = (p _c / r _c ) · (m _a / m _z ),

I _d = (p _z / r _z -p _c / r _d ) / (n-1),

I _k = p _c / r _d .

The above processes are carried out with increasing changes in the working volume in C1 and therefore make a positive contribution to the resulting specific work I ₁ .

The resulting specific work of the processes in the compressor and in the working space (combustion chamber → first cylinder)

From the previous it follows:

I ₁ = I _b + I _d + I _k + I _c , I _b , I _d , I _k > 0, I _c <0.

The specific work of the process of subsequent expansion in (Ts1 → Ts2):

taking into account the negative work of expansion in C1 (against the movement of the piston) I _e = (p _c / r _d -p _e / r _e ) / (n _e -1), where p _c , r _d , p _e , r _e , n _e defined above.

The desired specific work cycle:

I _i = I _b + I _k + I _d + I _e + I _s , where all terms are defined above,

I _b , I _k , I _d , I _e > 0, I _s <0.

Competitiveness assessment

Formulation of the problem

Objects of comparative analysis

Prototype ₍₁₎ - a conventional four-stroke internal combustion engine operating on a thermodynamic cycle with heat supply at a constant volume (V = const).

Project ₍₂₎ - the proposed pulsating ICE.

Comparison method

Comparison of the values of the theoretical (indicator) specific (per 1 kg RT) operation of the prototype cycle I _{i (1)} and project I _{i (2)} under the initial conditions equalizing the “starting” parameters of the working fluid.

Baseline

For the prototype and the project should be the same:

inlet air parameters p _a , r _a , T _a , air compression ratio ε, fuel, air excess coefficient α,

specific heat input Δq (MJ / kg RT),

RT parameters at the outlet r _e , r _e , T _e (determined by setting the volume of C2).

Comparative analysis

Further, “specific work” = “theoretical specific work”.

Specific work of the prototype cycle

I _{i (1)} = I _{w (1)} + I _{c (1)} , where

I _{w (1)} , I _{c (1)} - specific work, respectively, expansion of the RT, air compression.

I _{c (1)} = - (p _{s (1)} / r _{s (1)} -p _{a (1)} / r _{a (1)} ) / (n _{s (1)} -1) · (m _{a (1)} / m _{z (1)} ) <0.

For subsequent comparison with the project, the process (z ₍₁₎ → e ₍₁₎ ) of RT expansion in the prototype is further considered as a sequence of two constituent subprocesses (z ₍₁₎ → d ₍₁₎ ) and (d ₍₁₎ → e ₍₁₎ ), where

z ₍₁₎ is the initial state of the process with parameters p _z , r _{z (1)} , T _{z (1)} ,

e ₍₁₎ is the final state of the process with parameters p _{e (1)} , r _{e (1)} , T _{e (1)} ,

d ₍₁₎ is the intermediate state of the process with parameters p _{d (1)} = p _{c (1)} , r _{d (1)} , T _{d (1)} .

From the previous it follows:

I _{w (1)} = I _{d (1)} + I _{e (1)} , where

I _{d (1)} = (p _{z (1)} / r _{z (1)} -p _{c (1)} / r _{d (1)} ) / (n _{d (1)} -1),

I _{e (1)} = (p _{c (1)} / r _{d (1)} -p _{e (1)} / r _{e (1)} ) / (n _{e (1)} -1),

n _{d (1)} , n _{e (1)} - polytropic indicators in the corresponding subprocesses.

In this way:

I _{i (1)} = I _{d (1)} + I _{e (1)} + I _{c (1)} , where all terms are defined above, I _{d (1)} , I _{e (1)} > 0, I _{c (1)} < 0.

Project cycle specific work

From the above thermodynamic analysis it follows:

I _{i (2)} = I _b + I _k + I _{d (2)} + I _{e (2)} + I _{c (2)} , where

I _b = (p _{s (2)} / r _{s (2)} ) · (m _{a (2)} / m _{z (2)} ), I _k = p _{s (2)} / r _{d (2)} ,

I _{d (2)} = (p _{z (2)} / r _{z (2)} -p _{c (2)} / r _{d (2)} ) / (n _{d (2)} -1),

I _{e (2)} = (p _{c (2)} / r _{d (2)} -p _{e (2)} / r _{e (2)} ) / (n _{e (2)} -1),

I _{c (2)} = - (p _{c (2)} / r _{c (2)} -p _{a (2)} / r _{a (2)} ) / (n _{c (2)} -1) · (m _{a (2)} / m _{z (2)} ),

Absolute Benchmark

Absolute Benchmark

ΔI _i = I _{i (2)} -I _{i (1)}

is based on the above thermodynamic analysis of the proposed ICE and the accepted initial conditions of comparison, from which it follows

• ₍₁₎ = • ₍₂₎ = • for

• = p _a , r _a , m _a , m _z , p _c , r _c , n _s , p _z , r _z , p _d , r _d , n _d , p _e , r _e , n _e , I _d , I _e , I _c .

Seeking grade:

.

.

Relative benchmark

Relative comparative assessment:

θI _i = I _{i (2)} / I _{i (1)}

is based on the adopted initial conditions of comparison given above, the absolute comparative evaluation of ΔI _i and thermodynamic analysis of the prototype, from which it follows:

n _z is an indicator of the polytropic expansion of RT in the prototype.

Seeking grade:

.

.

Figure 3 presents the results of a computer calculation of θI _i ; in the form of an indexed family of graphs θI _i (ε) _[α] for a 4-stroke prototype defined by the data indicated in the description of the illustrations below.

Estimates of efficiency, power, specific fuel consumption.

Indicator parameters of efficiency η _i , power N _i , specific fuel consumption g _i are functions of specific indicator work I _i :

η _i = I _i / Δq = (I _i / H _u ) m _z ,

N _i = I _i · G _z = I _i · G _f · m _z (MW),

g _i = G _f / N _i = 1 / (I _i · m _z ) (kg / (MW · s)), where

N _u - net calorific value of fuel (MJ / kg of fuel),

m _z , G _f , G _z , Δq defined above.

From here follow relative comparative estimates:

Illustrative example

Figure 4.-7 presents the results of a computer calculation of the theoretical indicator parameters of the project in the form of indexed

family of graphs of functions f (α) _[ε] , where f = η _i , N _i , g _i for a 4-stroke prototype defined by the data specified in the illustrations below.

Recovery Effects

The working balance of a traditional internal combustion engine includes energy losses in the processes of compression and expansion, due to the known method of converting the supplied heat into useful mechanical work. This method is based on the thermodynamics of a fixed mass of the working fluid and fundamentally excludes the possibility of making up for these losses.

In the proposed internal combustion engine, the compressed air inlet from the compressor and the accumulation of exhaust combustion products provide for the recovery of some of the energy losses indicated above.

Estimates of the effect of recovery of energy losses during compression

Absolute estimate of energy loss during compression:

Δσ _c = -I _c = (p _c / r _s -p _a / r _a ) / (n _s -1) · (m _a / m _z ).

Absolute estimate of recuperated energy during the air intake from the compressor:

Δρ _c = p _c / r _c .

From the previous follows a relative assessment of the recovery effect for the compression process:

.

.

Really n _c > 1.33, whence

θρ _c > 30%.

Estimates of the effect of energy recovery during expansion

Absolute estimate of energy loss during expansion:

Δσ _e = (p _e / r _e ) / (n _z -1).

Absolute assessment of recuperated energy during the accumulation of exhaust combustion products:

Δp _e = p _c / r _d .

From the previous follows a relative assessment of the recovery effect for the expansion process:

.

.

и n_z>1.25, откудаReally

and n _z > 1.25, whence

θρ _e > 25%.

Description of illustrations

Figure 1 - schematic diagram of the proposed design.

Two successive phases of the engine duty cycle are shown; figures in round frames:

- компрессор,

- compressor

- пульсирующая камера сгорания,

- pulsating combustion chamber,

- цилиндры предварительного расширения,

- pre-expansion cylinders,

- цилиндры последующего расширения,

- cylinders for subsequent expansion,

- заслонка на впуске пульсирующей камеры сгорания,

- the inlet flap of the pulsating combustion chamber,

- воздух окружающей среды,

- ambient air

- топливо,

- fuel

- рабочее тело;

- working fluid;

figures in square frames:

one - inlet 2 - compression 3 - preliminary expansion, four - subsequent expansion, 5 - release.

Figure 2 - table of the dynamics of the state of the elements of the power unit:

1 - expansion - intake process - preliminary expansion,

2 - expansion - the process of subsequent expansion.

- рабочий ход поршня.The values of the states are shown in the form of a “two-story” fraction: accordingly, the numerator is the first phase, the denominator is the second phase of the working cycle. The arrows indicate the direction of change of the cylinder’s working volume: → - increase, ← - decrease, big arrow

- piston stroke.

Figure 3 - relative comparative assessment of θI _i .

Prototype data:

i (number of cylinders) = 4, the distributed fuel injection, fuel is gasoline, S = 0.77 m, D (diameter of the piston) = 0.8 m, T _a = 299 _{K, p a = 0.0866, ξ} z = 0.85.

FIG. 4-6 - calculation results of theoretical indicator parameters:

FIG. 4 - indicator efficiency η _i

FIG. 5 - indicator power N _i .

FIG. 6 - indicator specific fuel consumption g _i .

The initial data of the prototype are the same as for figure 3, ε ₍₁₎ = 11, α ₍₁₎ = 1.

The data ε ₍₁₎ , η _{i (1)} , N _{i (1)} , g _{i (1)} are marked with underlined values on the coordinate scales and the corresponding coordinate lines.

Literature

1. Internal combustion engines. Ed. V.N.Lukanina and M.G. Shatrova. M .: Higher school, 2010. Book 1: Theory of work processes.

2. A.I. Kolchin, V.P. Demidov. Calculation of automobile and tractor engines. M .: Higher School, 2008.

Claims (3)

1. A method of implementing a duty cycle in an internal combustion engine, including the process of generating a working fluid by means of a compressor, a fuel supply device and a combustion chamber, a process of accumulating and pre-expanding a working fluid in a pre-expansion cylinder, a process of subsequent thermodynamic expansion of the working fluid from the pre-expansion cylinder subsequent expansion cylinder, the process of releasing the spent working fluid from the subsequent expansion cylinder to the outside environment, characterized in that the process of generating the working fluid is carried out discretely, sequentially accumulating, over the full stroke of the piston, in the pre-expansion cylinder quantized portions of the working fluid generated by a pulsating combustion chamber with a series of microprocesses of generation, including sequentially forming the working mixture, burning the working mixture with a constant volume and thermodynamic expansion of the working fluid. 2. The method according to claim 1, characterized in that the control of a series of microprocesses for generating the working fluid is carried out automatically by means of a damper that blocks or opens a channel with a compressor — a combustion chamber for a full stroke of the piston, and a synchronizer device that synchronizes the damper options with a change in the pressure of the working fluid in the space between the shutter and the piston in the pre-expansion cylinder; the valve is opened at the moment when the pressure of the working fluid in the space between the closed valve and the piston becomes equal to a predetermined value less than or equal to the inlet pressure from the compressed air compressor or working mixture; in the interval between the opening and subsequent closing of the damper in the combustion chamber with the help of a compressor, the charge of the compressed working combustible mixture is formed, after which the combustion process is initiated; the shutter is closed at the moment when the pressure of the working fluid as a result of the initialization of the combustion process exceeds a predetermined value; in the period between the closing and the subsequent opening of the valve, a preliminary expansion of the working fluid is carried out; at the moment of completion of the forward stroke of the piston, the combustion chamber is switched to another cylinder of preliminary expansion, and during the reverse stroke of the piston, the subsequent expansion of the working fluid into the cylinder of the subsequent expansion of a larger volume is carried out; in the process of the piston return stroke in the cylinder of the subsequent expansion, the spent working fluid is released. 3. An internal combustion engine including a compressor, a combustion chamber, preliminary expansion cylinders, subsequent expansion cylinders, an automatic gas exchange control system between the combustion chamber and preliminary expansion cylinders, between preliminary and subsequent expansion cylinders and between subsequent expansion cylinders and the external medium, a selection mechanism power, characterized in that a pulsating combustion chamber is used, which generates a discrete working gas otok accumulating over the full stroke of the piston in the expansion cylinder prior to the working fluid pressure is not lower than the compression pressure and a density less than the density of the compression in the compressor.

Images