RU2006616C1 - Method of operation of internal combustion engine and internal combustion engine - Google Patents

Abstract

FIELD: engine engineering. SUBSTANCE: method is implemented by fresh charge entering a rotor positive-displacement compression machine, by- passing the charge to a combustion chamber at a constant volume, supplying fuel to the combustion chamber through at least one nozzle, igniting and burning out a fuel-air mixture, by-passing hot gases from the combustion chamber, and two-stage expanding of exhaust gases to convert a work of expansion to rotation of an output shaft and consequence discharging the gases to the atmosphere. The gases are by-passed back from the combustion chamber to rotor machine wherein the gases are expanded. The fuel is constantly supplied to the combustion chamber, and final expanding of the hot gases is carried out by by-passing the gases from the rotor positive-displacement machine to a piston expander. A rate of the fuel supplied to the combustion chamber is controlled by changing the number of connected nozzles. The internal combustion engine has case, rotor supercharger and expander, which are made of a hollow cylinder provided with radial baffles and cylindric rotating piston and set on the output shaft within the case, machine for repeated expansion, combustion chamber with a constant volume coupled with the supercharger and expander through gas passages provided with valves having drive and provided with at least one nozzle and ignitor. The rotor expander and supercharger are made in block, working surface of the supercharger cylinder is provided with a ring flexible seal. The rotating piston is made of a rolling bearing eccentrically mounted on the output shaft for contacting with the cylinder seal by its race. The baffles are mounted in cylindrical guides secured within the cylinder. The machine for repeated expansion is piston-type and provided with gas distributing mechanism and crankshaft coupled to the output shaft. The drive of the valve is made of cam disks positioned coaxially to the output shaft and coupled with it kinematically through a reduction gear. The gas distributing mechanism of the additional expansion machine is made of a slide, which encloses the piston machine, kinematically coupled with the cam disk and provided with a ring gas intake coupled with the expander of the rotor machine . EFFECT: enhanced efficiency. 3 cl, 13 dwg

Description

 The invention relates to internal combustion engines and can find application in the national economy, in transport, and in the case of applying a boost from a turbocharger, in aviation.

 Known internal combustion engines operating on a carbureted mixture.

 However, in these engines low values of the degree of air compression are realized due to the occurrence of detonation combustion of gasoline in compressed air in the cylinders. For this reason, in such engines it is impossible to improve efficiency to the level of efficiency of diesel engines.

 To ensure detonation-free combustion in carburetor internal combustion engines, an additive in the form of tetraethyl lead is added to gasoline used as fuel. It is known that the products of the combustion of gasoline with the addition of tetraethyl lead pollute the atmosphere. In addition, such engines do not use a fully available degree of gas expansion, which does not contribute to improving the efficiency of such an engine.

According to the proposed method and device, the combustion of fuel in compressed air is provided for at high values of compression ratio, use of gasoline without tetraethyl lead as a fuel, high values of air excess coefficient α ₁ and continuous combustion of fuel in a combustion chamber installed outside the chambers of the working fluid of an air compression machine and gas expansion.

 The degree of compression of air in this case may be at the level of compression ratios of known diesel engines.

 The internal combustion engine, made by the proposed method and device, has a reliable start regardless of weather conditions and, for this reason, compares favorably with known diesel engines. In addition, compared with diesel engines, the proposed internal combustion engine can be performed with high values of the rotational speed of the shaft of the machine for air compression and gas expansion.

This is achieved by burning fuel in a combustion chamber installed outside the chambers of the working fluid of an air compression and gas expansion machine, supplying compressed air to the combustion chamber in portions from the working fluid chambers, removing products from the combustion chamber to the working fluid chambers in portions when the combustion chamber is disconnected from the chambers the working fluid during the implementation in the chambers of the working fluid of the processes of filling air, compressing air, the processes of expansion of gases and exhaust gases, the implementation after the processes of filling air of compression of air in the chambers of the working fluid and the supply of compressed air from the chambers of the working fluid to the combustion chamber, the processes of supplying products to the chambers of the working fluid from the combustion chamber, the expansion of gases in the chambers of the working fluid and the exhaust of gases from the chambers of the working fluid, additional expansion of the gases leaving the chambers of the working fluid body, in an additional gas expansion machine, by performing an air compression and gas expansion machine in the form of a rotor machine, the working fluid chambers of which are formed between the rotor sleeve mounted on the bearings on the rotor cylinder and located eccentrically relative to the axis of rotation, the housing and reciprocating moving partitions mounted on fixed cylindrical guides mounted on the housing, the implementation of an additional gas expansion machine in the form of a piston machine having a gas distribution rim in which an annular intake is made gases from the outlet of the working fluid chambers with channels and cavities for supplying gases to the cylinders of the additional machine, an annular intake of atmospheric air from the channel and the supply cavities of this air for cooling the cylinder, the pistons of the machine for additional expansion of gases, while the shaft of the gas distribution rim is connected to the shaft of one of the two cam discs of the valve drive of the working chamber chambers, each shaft of which is kinematically connected to the rotor of the air compression and gas expansion machine through gearbox with gear ratio i = n _rotor / n _KD = 2, where n of the _rotor is the rotational speed of the rotor of the machine for compressing air and expanding gases; n _cd - the frequency of rotation of the shaft of the cam discs, the shaft of the additional machine is connected to the rotor shaft and the power take-off shaft.

In FIG. 1 shows a longitudinal section of the proposed engine; in FIG. 2 is a section AA in FIG. 1; in FIG. 3-6 - section BB in FIG. 1 (every 90 ^{about the} rotation of the rotor with the designations of the processes at the chambers of the working fluid); in FIG. 7 is a section BB of FIG. 1; in FIG. 8 is a section GG in FIG. 6; in FIG. 9 is a section DD in FIG. 1; in FIG. 10 is a cross-section EE in FIG. 1; in FIG. 11 - on an enlarged scale, the sealing elements between the cylinders of the additional expansion machine and the gas distribution rim; in FIG. 12 - an option is made of a labyrinth seal between the cylinders of an additional gas expansion machine and its rim; in FIG. 13 - a combustion chamber of the engine with fuel combustion in three zones.

 In FIG. 1, the air compression and gas expansion machine 1 consists of a rotor 2 having a cylinder eccentrically mounted relative to the axis of rotation, on which the sleeve 3 is located by means of rolling bearings 4. On both sides of the rotor, on the body of the air compression and gas expansion machine, covers 5 and 6. On these covers are respectively cylinders 7 and 8 of valves 9 and 10 of the working medium chambers.

 Valves 9 and 10 are made in the form of pistons with sealing elements - piston rings (not shown) and have rods 11 and 12, respectively. Valve 9 is used to exhaust expanded gases from one chamber of the working fluid, and valve 10 is used to exhaust compressed air from one chamber working fluid in the combustion chamber.

 Rollers are installed at the ends of the valve rods: for the rod 11, the rollers 13, for the rod 12, the rollers 14.

 Valve rods through respective rollers are supported on cam discs 15 and 16. Each pair of valve rod rollers is located symmetrically with respect to the axis of the rods. Moreover, when the rollers of one valve stem are located in the central part, each pair of rollers of the other valve stems is placed on the outer sides of the rollers of the previous rods.

 The valves 9 and 10 are pressed against the respective cams of the disks 15 and 16, respectively, using the springs 17 and 18.

 Cam discs 15 and 16 are kinematically connected to the rotor shaft with gears 19 and 20, respectively.

The gear ratio n _p / n _KD is chosen equal to 2, where n _p is the rotor speed; n _cd - frequency of rotation of cam discs.

 The internal combustion engine, made by the proposed method and device, has an additional gas expansion machine with a block of 21 cylinders 22 and 23.

 A connecting rod 24 is located in the cylinder 22, and a connecting rod 25 in the cylinder 23. The connecting rod 24 is kinematically connected to the piston 26, and the connecting rod 25 is connected to the piston 27. Both connecting rods 24 and 25 are kinematically connected to the crankshaft 28 connected to the rotor shaft 2.

The additional gas expansion machine has a second cylinder block 29. The axes of the first and second cylinder blocks are located at an angle of 90 ^about .

 In FIG. 1 shows one of the air intakes 30. Compressed air leaves the chambers of the working fluid through a valve 10 through a channel 31. This channel is in communication with the input of the combustion chamber 32, in which a continuous fuel injector 33 is installed.

 One of the channels for the expansion of the expanded gas from the chamber of the working fluid of the gas compression and expansion machine is indicated by 34. This channel is in communication with the cylinder 7 of the gas exhaust valve 9.

 In FIG. 1 shows an annular intake 35 for supplying gases from the chambers of the working medium of an air compression and gas expansion machine to an additional expansion machine and an annular intake 36 for supplying cooling atmospheric air to the cylinders of an additional gas expansion machine. Both intakes are located on the rim 37 of the distribution of the working fluid.

 There are counterweights 38 for balancing the rotor. The power take-off shaft is indicated at 39. This shaft is designed as an extension of the rotor shaft.

 Position 40 denotes one of the supports of the rim 37 of the distribution of the working fluid.

 Between the covers 5 and 6, the sleeve 3 of the rotor is made of the seal 41.

 In FIG. 2 shows cylinders 42 of air supply valves. These cylinders communicate with the air intakes 30 through respective valves (not shown). The gear housing 19 is designated 43. The remaining symbols correspond to the accepted symbols in FIG. 1.

 In FIG. 3, cylindrical guides 44 are shown mounted on the housing 45. Partitions 46 are installed in these guides. Between the guides 44 and the partitions 46, cavities 47 are provided for supplying liquid to squeeze the partitions to the sleeve 3 for sealing. The housing 45 on the inside has the shape of a cylinder to which elastic sealing elements 48 are attached, on which the sleeve 3 of the rotor 2 is rolled. Metal rubber can be used as elastic elements.

 In FIG. 3, reference numeral 49 denotes a valve for discharging compressed air from the chamber of the working fluid in the combustion chamber, and reference numeral 50 denotes a valve for supplying products from the combustion chamber 32 to the chambers 51 and 52 of the working fluid.

 The air compression and gas expansion machine is represented by two chambers of the working fluid. These chambers of the working fluid are formed by partitions 46, the sleeve 3 of the rotor and the inner cylindrical surface of the housing 45, on which elastic elements 48 are mounted.

 To supply fluid in the cavity 47 on the rails 44 made fitting 53.

 In FIG. 3 for the initial position of the rotor at the chambers of the working fluid, the corresponding processes in them are indicated. VG means gas exhaust, N.V. - air filling.

In FIG. 4 pokazzan rotor rotation through ¹⁸⁰ ° with respect to the initial position. Sr. V. means air compression.

In FIG. 5 shows the position after the rotor is rotated 360 ^° with respect to the initial position. R. G. Means the expansion of gases.

In FIG. 6 shows the position after a rotation of ⁵⁴⁰ ° with respect to the original position. V. G. means exhaust gases.

FIG. 3 also corresponds to a rotation ^of the rotor 720 with respect to the original received rotor position.

 In FIG. 7, some designations correspond to the designation of FIG. 1, cylinders 54 of valves 50 (see FIG. 3) for supplying combustion products to the chambers of the working fluid from the combustion chamber 32 are shown — gear wheel 55 of the gearbox 20 (see FIG. 1), the crankcase 56 of the gearbox 20.

 In FIG. 8 shows the channels 57 of the fluid outlet, made in the partitions 46 (see Fig. 3), the stops 58 of the springs 59, the spring 60 of the compression elements of the seals 41 (see Fig. 1).

 In FIG. 9 shows a cavity 61 for supplying expanded gases from an air compression and gas expansion machine. This cavity through the annular intake 35 is constantly in communication with the channels 34 of the exit of gases from the machine 1 compression expansion of gases. The cavity 61 is made on the rim 37 of the distribution of the working fluid. On the same rim there is a cavity 62 for exhaustion from the upper cylinder of the gas expanded in the cylinders, a cavity 63 for supplying cooling atmospheric air to the upper cylinder, a cavity 64 for exhausting cooling air from the upper cylinder.

 In FIG. 10, cavities corresponding to the designations of FIG. 9 for the lower cylinder.

 In FIG. 11 enlarged with respect to FIG. 1 shows a cylinder with seals of an additional gas expansion machine. Here, a variant of the labyrinth seal of cylinders with a rim 37 is shown. The combs of the labyrinth seals are indicated by numbers 65-67, position 68 is the cavity of the labyrinth.

 In FIG. 12 shows scallops 69 of labyrinth seals.

 For the cylinder block 29, these cavities and seals are performed similarly.

 In FIG. 13, an embodiment of a three-zone combustion chamber 32 is given. In this case, three flame tubes 70-72 are installed in the combustion chamber. Each flame tube has nozzles 73-75 for supplying primary air, pipelines 76-78 for supplying fuel to nozzles 33, 79 and 80. At the exit of each flame tube there are corresponding mixers 81-83. The supply of secondary air to the flame tubes are indicated by 84-86, respectively. In addition, mounting brackets 87, flame spreaders 88 and 89 from the flame tube downstream to the previous flame tubes are shown.

 The channel for the removal of combustion products to the chambers of the working fluid of an air compression and gas expansion machine is indicated at 90. This channel is connected to the chambers of the working fluid through a valve 50 and cylinders 54.

 A spark plug (not shown) is installed in the first flame tube.

 In FIG. 1 shows gearboxes 19 and 20 according to sections Zh-Zh and ZZ of FIG. 2 and 7. Therefore, in the lower part of the longitudinal section of the engine (Fig. 1), the air intake 30 and the gas outlet channel 34 from the corresponding cylinder of the exhaust gas valve from the working medium chamber are not shown conventionally.

 For the air compression and gas expansion machine with two chambers of the working fluid, four valves are installed on the covers 5 and 6. On the cover 5 - two air supply valves, two exhaust gas valves, on the cover 6 - two compressed air supply valves to the combustion chamber 32 and two valves for supplying combustion products to the chambers of the working fluid.

 The engine made by the proposed method and device operates as follows.

 The engine is started by spinning the rotor shaft, turning on the ignition and supplying fuel to the combustion chamber 32. At the same time, air through the air intake 30, cylinders 42 of the air supply valves at the corresponding rotor positions enters the chambers of the working fluid. In the chambers of the working fluid, the air is compressed when the rotor is turned and after that the compressed air is discharged through the cylinders 8 of the valves 10 and 50 to the combustion chamber 32 through the channel 31. In the combustion chamber, fuel is burned in compressed air when it is continuously fed through nozzles when air is supplied to the combustion chamber of compressed air from the chambers of the working fluid in portions and during the removal of combustion products to the chambers of the working fluid also in portions after the processes of supplying compressed air to the combustion chamber. In this case, when compressed air is supplied to the combustion chamber after opening the corresponding valve for supplying compressed air to the working fluid, the rotor shaft is loaded. When supplying combustion products to the chambers of the working fluid after opening the corresponding valve for supplying combustion products when filling the chamber of the working fluid, the rotor shaft is unloaded. When the combustion chamber communicates with the working fluid chamber, when the combustion products are supplied to it, the pressure in the combustion chamber drops somewhat.

After supplying a new portion of compressed air to the combustion chamber from the chamber of the working fluid, the pressure is restored to the value P $\genfrac{}{}{0ex}{}{\text{*}}{\text{Z}}$ = (P $\genfrac{}{}{0ex}{}{\text{*}}{\text{to}}$ T $\genfrac{}{}{0ex}{}{\text{*}}{\text{g}}$ ) / T $\genfrac{}{}{0ex}{}{\text{*}}{\text{to}}$ [1], where P _k * is the total air pressure after compression in the chambers of the working fluid; T _g * - the value of the total temperature of the combustion products; T _to * - conception of the full temperature of compressed air in the chambers of the working fluid.

By the values of the volumes of the chambers of the working fluid after air compression, the volume when supplying combustion products ΔV, and also by the value of the volume of the combustion chamber V _c.s. it is possible to establish the dependence of the pressure P _z ^{l *} in the combustion chamber when communicating with the chambers of the working fluid.

= (P_z ^*·v_к.сг)/(v_к.сг+Δv) = P $\genfrac{}{}{0ex}{}{\text{*}}{\text{Z}}$ /[1+Δv/v_к.сг] . [3]
Если принять V_к.сг = 20 ΔV, то P

= P $\genfrac{}{}{0ex}{}{\text{*}}{\text{z}}$ /[1+1/20] = (1·P

)/1,05 = 0,95·P $\genfrac{}{}{0ex}{}{\text{*}}{\text{z}}$ . При этом потери давления от располагаемого значения составляют 5% . По значениям Т_г* и Р₂* определяется эффективное значение работы.Fair equality
(V _c.s. + ΔV) ˙P _z ^l * = P _z * ˙ V _c.s. , [2]
P

= (P _z ^* v _v.sg ) / (v _s.sg + Δv) = P $\genfrac{}{}{0ex}{}{\text{*}}{\text{Z}}$ / [1 + Δv / v _c.sg ]. [3]
If we take V _k.sg = 20 ΔV, then P

= P $\genfrac{}{}{0ex}{}{\text{*}}{\text{z}}$ / [1 + 1/20] = (1 · P

) / 1.05 = 0.95P $\genfrac{}{}{0ex}{}{\text{*}}{\text{z}}$ . In this case, the pressure loss from the available value is 5%. The values of T _g * and P ₂ * determines the effective value of the work.

 After the expansion of gases in the chambers of the working fluid of a gas compression and expansion machine, these gases are directed to an additional gas expansion machine. In the cylinders of this machine, an additional expansion of gases occurs, since in a machine for compressing air and expanding gases (as in any internal combustion engine), complete expansion of gases does not occur. Additional expansion of gases helps to reduce specific fuel consumption.

 The effective power is removed from the rotor shaft and this power is supplied to the power take-off shaft 39.

 When performing an engine with a combustion chamber having several zones, the combustion of fuel supplied through nozzles 33, 79 and 80 is sequentially switched on. The fuel can be supplied to these nozzles depending on the position of the fuel supply pedal or gas sector. In this case, the necessary pressure in front of the nozzles can be provided both by changing the performance of the fuel pump, and by transferring fuel to the pump inlet, depending on the position of the fuel supply pedal or gas sector. At low loads, the fuel is supplied to the nozzle 33 and burned in the flame tube 70, and with a further increase in the load, the fuel is subsequently supplied to the nozzles 79 and 80. The start of the flame tube 71 is carried out from the supply of hot gases from the first flame tube 70 through the flame distributor 88, and the start of the flame pipes 72 - from the supply of hot gases from the second flame tube 71 through the flame distributor 89.

 For clarity, an example of thermal calculation of an internal combustion engine, performed by the proposed method and device, is given.

The degree of expansion of air in the chamber of the working fluid is equal to P _k * = 14. The temperature of the products in the combustion chamber T _g * = 1350 K.

The work of air compression in the chamber of the working fluid
l _to * = 288˙102.5 (14 ^0.286 -1) / 0.85 = 39140 kgm / kg.

Air temperature at the end of compression in the chambers of the working fluid
T _c * = 288 + 39 140 / 102.5 = 670 K.

The full degree of expansion in the chambers of the working fluid and an additional gas expansion machine is as follows: $\genfrac{}{}{0ex}{}{\text{*}}{\text{p}}$ = N $\genfrac{}{}{0ex}{}{\text{*}}{\text{to}}$ (T $\genfrac{}{}{0ex}{}{\text{*}}{\text{g}}$ / T $\genfrac{}{}{0ex}{}{\text{*}}{\text{to}}$ ) · Σ ₁ · σ ₂ · σ ₃ · σ ₄ · σ ₅ · σ ₆ , [4] where σ ₁ is the coefficient of pressure loss when filling air from the atmosphere into the chambers of the working fluid; σ ₂ is the pressure loss coefficient of compressed air at the exit from the chambers of the working fluid and supply to the combustion chamber; σ ₃ - coefficient of pressure loss of the working fluid associated with the supply of gases from the combustion chamber to the chamber of the working fluid; σ ₄ - coefficient of gas pressure loss during exhaust from the chambers of the working fluid; σ ₅ - coefficient of pressure loss of the working fluid associated with a drop in gas pressure in communication with the chambers of the working fluid; σ ₆ - coefficient of pressure loss of gases associated with the inlet, exhaust gases from an additional gas expansion machine. σ ₁ , σ ₂ are taken equal to 0.95; σ ₃ , σ ₄ are taken equal to 0.95 [3], [4]; σ ₅ = 0.95; σ ₆ = 0.95 ˙ 0.95 ˙ 0.95.

Coefficient σ ₆ = 0.95˙ 0.95˙ 0.95 = 0.85; σ ₁ ˙σ ₂ ˙σ ₃ ˙σ ₄ ˙σ ₅ ˙σ ₆ = 0.95˙ 0.95x x 0.95 ˙ 0.95˙ 0.95 ˙ 0.85 = 0.73.

0,73 = 20,59.P _p * = 14

0.73 = 20.59.

Total gas expansion work
l _p * = 1350-29.3 ⁴ [1-1 / 20; 59 ^0.25 ] ˙ 0.9 = 75471 kgm / kg.

Temperature at the end of gas expansion
T _p * = 1350 - 75471 / (29.3 · 4) = 706 K.

Free work
l _St * = 75471 - 39140 = 36331 kgm.

= 484 л. с. /(кг воздуха).Specific power N _beats =

= 484 l with. / (kg of air).

The amount of fuel burned in one kg of air is determined by the formula
q = (C _p T $\genfrac{}{}{0ex}{}{\text{*}}{\text{g}}$ -C _p T $\genfrac{}{}{0ex}{}{\text{*}}{\text{to}}$ ) / (H ₄ η _g -iT $\genfrac{}{}{0ex}{}{\text{*}}{\text{g}}$ + C _p T $\genfrac{}{}{0ex}{}{\text{*}}{\text{to}}$ ) [ 5 ] .

In the proposed engine, fuel is burned at a constant volume. Therefore, for the proposed engine, heat losses due to heat exchange between gases and the walls of the chambers of the working fluid are determined as follows
q = (C _p T $\genfrac{}{}{0ex}{}{\text{*}}{\text{g}}$ -C _p T $\genfrac{}{}{0ex}{}{\text{*}}{\text{to}}$ ) / [(H ₄ η _g -iT $\genfrac{}{}{0ex}{}{\text{*}}{\text{g}}$ + C _p T $\genfrac{}{}{0ex}{}{\text{*}}{\text{to}}$ ) (C _p / C _v )], [6] for combustion products, the ratio of the specific heat of C _p products at constant pressure to the specific heat of C _V products with a constant volume of C _p / C _v is 1.33.

To assess the heat loss from heat transfer between gases and walls, the fuel consumption for a D-108 diesel engine having a compression ratio of P _k * = 14 is determined when conventionally used as kerosene fuel. The air compression work of this diesel engine at a value of P _k * = 14 l _k * = 39140 kgm / kg.

The air temperature at the end of compression T _to * = 670 K.

The temperature of the combustion products T _g * = 2200 K.

T _k * = 670 K, C _r T _k * = 681.3, T _g * = 2200 K; C _p T _g * = 2502.62; iT _g * = 6775.12 [6].

H ₄ η _g = 42600 (for kerosene),
42600 - 6775 + 681 = 36506,
2502.62 - 681.3 = 1821.32,
q = 1821.32 / (36506 · 1.33) = 0.0375 kg / (kg air).

(10330·14·0,45)/(670·29,3) = 7 кг/м³ , удельную плотность воздуха до сжатия после наполнения цилиндров при коэффициенте потерь давления σ₁= 0,95
γ $\genfrac{}{}{0ex}{}{\text{*}}{\text{в}}$ _озд= (10330·0,95)/(288·29,3) = 1,16 кг/м³ отношение

/γ $\genfrac{}{}{0ex}{}{\text{*}}{\text{в}}$ _озд = 7/1,16 = 6,035.To determine the expansion work of diesel gases, it is necessary to determine the degree of expansion of gases in the cylinders. To do this, determine the specific gravity of air after compression in the cylinders

(10330 · 14 · 0.45) / (670 · 29.3) = 7 kg / m ³ , specific air density before compression after filling the cylinders with a pressure loss coefficient σ ₁ = 0.95
γ $\genfrac{}{}{0ex}{}{\text{*}}{\text{at}}$ _ozd = (10330 · 0.95) / (288 · 29.3) = 1.16 kg / m ³ ratio

/ γ $\genfrac{}{}{0ex}{}{\text{*}}{\text{at}}$ _ozd = 7 / 1.16 = 6.035.

9

3

1350/670) =
При расширении газов в цилиндрах дизеля давление в них должно быть выше, чем атмосферное давление, в

раза, при σ₂= 0,95 давление в цилиндрах в конце расширения должно быть не менее
Р_г* = 1,033/0,95 = 1,087 кг/см².The specific gravity of gases obtained after fuel combustion, γ _air ^* is the same as

9

3

1350/670) =
With the expansion of gases in diesel cylinders, the pressure in them must be higher than atmospheric pressure, in

times, with σ ₂ = 0.95, the pressure in the cylinders at the end of the expansion should be at least
P _g * = 1.033 / 0.95 = 1.087 kg / cm ² .

Available degree of expansion at the same time
P $\genfrac{}{}{0ex}{}{\text{*}}{\text{p}}$ = N $\genfrac{}{}{0ex}{}{\text{*}}{\text{to}}$ Σ ₁ σ ₂ (T $\genfrac{}{}{0ex}{}{\text{*}}{\text{g}}$ / T $\genfrac{}{}{0ex}{}{\text{*}}{\text{to}}$ ) = 14 · 0.95 · 0.95 (2200/670 = 41.5.

 The actual degree of expansion of a diesel engine is determined by the method of successive approximation.

The expansion temperature T _g * of gases in the cylinders is determined at the expansion degree P _p * = 14.

Expansion work without efficiency
l _p * = 2200˙29.3˙4˙ [1-1 / 14 ^0.25 ] = 124536 kgf.

T _p * = 2200 - 124536 / 29.3 · 4 = 1137 K.

0,95 = 0,967 кг/м³;

= 0,967, Р_р* = 0,967 ˙1137 x29,3 = 32214 кг/м³ = 3,2214 кг/см² ,
0,967 ˙6,035 = 5,83 < 7.The specific density of gases in the cylinders
γ $\genfrac{}{}{0ex}{}{\text{*}}{\text{p}}$ =

0.95 = 0.967 kg / m ³ ;

= 0.967, P _p * = 0.967 ˙1137 x29.3 = 32214 kg / m ³ = 3.2214 kg / cm ² ,
0.967 ˙ 6.035 = 5.83 <7.

1) Considered
P _p * = 11.5; l _p * = 2200˙23.3 ˙ 4 x [1-1 / 11.5 ^0.25 ] = 117755 kgm / kg,
T _p * = 2200 - 117755 / (29.3 · 4) = 1195 K,
γ $\genfrac{}{}{0ex}{}{\text{*}}{\text{p}}$ = [(10330 · 14 · (288/670) · 0.95] / (11.5 · 1195 · 29.3) = 1.12,
1.12 ˙6.035 = 6.76.

2) Considered
P _p * = 11; l _p * = 2200˙29.3 ˙4 x
x [1-1 / 11 ⁰²⁵ ] = 116234 kgm / kg;
T _p * = 2200 - 116234 / 29.3 · 4 = 1208 K;
γ $\genfrac{}{}{0ex}{}{\text{*}}{\text{p}}$ = [(10330 · 14 (288/670) · 0.95] / (115 · 1208 · 29.3) = 1.158,
1.158 ˙6.035 = 6.99.

The degree of expansion of the diesel P _p * is determined equal to 11.

Diesel expansion work
l _p * = 2200 ˙29.3 ˙4 x
x [1-1 / 11 ^0.25 ] ˙0.9 = 104610 kgm / kg.

Free diesel operation
l _St * = 104610 - 39140 = 65471 kgm / kg.

Specific power N _beats = 65471/75 = 872.9 liters. with. / (kg unit).

The amount of fuel burned in one kg of air for a diesel engine under given conditions is determined
q = 0.0375 kg / (kg weight.).

Fuel specific impulse
I _beats = 872.9 / 0.375 = 22277 l. s / kg of fuel.

Specific fuel consumption C _l = 3600/23277 = 0.154659 kg / (hp / h).

The known diesel D-108 has a specific fuel consumption value C _l = 0.175 kg / (l.s. / h) when using diesel fuel with a calorific value of N ₄ = 10500 kcal / kg.

The specific consumption of this diesel engine according to the proposed method
With _l = 0.154659 · (11000/10500) = 0.162 kg / (hp / h)
Correction factor for determining the specific fuel consumption of the proposed engine
K = 0.175 / 0.162 = 1.08.

The formula for determining the fuel consumption burned in one kg of air for the proposed engine is determined
q = [(C _p T $\genfrac{}{}{0ex}{}{\text{to}}{\text{g}}$ -C _p T $\genfrac{}{}{0ex}{}{\text{*}}{\text{to}}$ ) · 1.08] / [(H ₄ η _g -iT $\genfrac{}{}{0ex}{}{\text{*}}{\text{g}}$ + C _p T _k ) · (C _p / Cv)],
T _to * = 760 K; With _p T _k * = 681.3; T _g * = 1350 K;
C _p T _g * = 1455.5; iT _g * = 3488.65 [6].

H ₄ η _g = 42600 (for kerosene),
42600 - 3488.65 + 681.3 = 38792,
1455.5 - 681.3 = 774.2,
q = (774.2 · 1.08) / (39792 · 1.33) = 0.0158 kg / (kg air).

Fuel specific impulse
I _beats = 484 / 0.0158 = 30632.9 l. with. / (kg of fuel).

Specific fuel consumption
C _l = 3600 / 30632.9 = 0.118 kg / (l.s. / h).

 The values of the degree of expansion of gases in the chambers of the working fluid and an additional gas expansion machine are determined.

Specific air density after filling the chambers of the working fluid
γ $\genfrac{}{}{0ex}{}{\text{*}}{\text{at}}$ _ozd = (10330 · 1 · 0.95) / (288 · 29.3) = 1.16 kg / m ³ .

= (10330·14·0,95)/(670·29,3) = 7,00 кг/м³,
отношение 7/1,16 = 6,035.Specific air density after compression in the chambers of the working fluid

= (10330 · 14 · 0.95) / (670 · 29.3) = 7.00 kg / m ³ ,
ratio 7 / 1.16 = 6.035.

In the chambers of the working fluid after compression of air with a compression ratio P _k * = 14, its volume decreases by 6.035 times.

Given the additional pressure loss of the combustion products supplied to the chambers of the working fluid, the increase in the volume of expanded gases in the chambers of the working fluid will be 6.035 times less due to a decrease in density from the pressure loss coefficients σ _{2 and} σ ₃ (see above).

When filling the air, the deviation of V _to ΔV will be 6.035, where V _to is the volume of the chambers of the working fluid; ΔV is the volume of compressed air in the filling chamber. When filled with gases, the volume occupied by gases will increase by 1 / (0.95 · 0.95) = 1.1 times.

The ratio of the volume of gas after expansion in the working fluid chambers (chamber volume of working fluid) to the volume of gases in the working fluid chamber to expand _to V ΔV decreases to 1.1 times
v _c / Δv = 6.033 / 1.1 = 5.4845.

 The degree of expansion of gases in the chambers of the working fluid is also determined by the method of successive approximation.

The degree of expansion of gases in the chambers of the working fluid P _p * = 11 is considered.

Expansion work without efficiency
l _p * = 1350 ˙29.3 ˙4 [1-1 / 11 ^0.25 ] = 71325 kgm / kg,
T _p * = 1350 - 71325 / (29.3 · 4) = 741.4 K.

95·0,95·0,95(1350/670)] /[11·741,4·29, ] 3 =
Удельная плотность газов до расширения

0

9

5

/

[

350·29,3] =
Рассматривается П_р* = 10 без учета КПД
l_р* = 1350 ˙29,3 ˙4 1-(1/10^0,25) = 69237 кгм/кг,
Т_р* = 1350 - (69237/29,3·4) = 759 К,

0

9

5·0,95·(1350/670)] /[10·759·29,3] =
Рассматривается П_р* = 9,8 без учета КПД
l_p* = 1350˙29,3 ˙4 [1-(1/9,8^0,25)] =
= 68825 кгм/кг,
Т_р* = 1350 - 68825/(29,3·4) = 762,7 К;

[

14·0,95·0,95·0,95·(1350/670)] /[9,8·762,7·29,3] =
6,313/1,14 = 5,53; П_р* = 9,7, без учета КПД
l_р* = 1350 - 29,3 - 4 [1-1/9,7^0,25] =
= 68572 кгм/кг,
Т_р* = 1350 - 68572,5/(29,3·4) = 764,9 К, γ $\genfrac{}{}{0ex}{}{\text{*}}{\text{p}}$ = [10330·14·0,95·0,95·0,95(1350/670)] /[9,7·764,9·29,3] = 1,1487,
6,313/1,1487 = 5,49 близко к значению 5,48.The specific gravity of the expanded gas

95 · 0.95 · 0.95 (1350/670)] / [11 · 741.4 · 29,] 3 =
Specific gas density before expansion

0

9

5

/

[

350 · 29.3] =
Considered P _p * = 10 excluding efficiency
l _p * = 1350 ˙29.3 ˙4 1- (1/10 ^0.25 ) = 69237 kgm / kg,
T _p * = 1350 - (69237 / 29.3 · 4) = 759 K,

0

9

5 · 0.95 · (1350/670)] / [10 · 759 · 29.3] =
Considered P _p * = 9.8 excluding efficiency
l _p * = 1350˙29.3 ˙4 [1- (1 / 9.8 ^0.25 )] =
= 68825 kgm / kg,
T _p * = 1350 - 68825 / (29.3 · 4) = 762.7 K;

[

14 · 0.95 · 0.95 · 0.95 · (1350/670)] / [9.8 · 762.7 · 29.3] =
6.313 / 1.14 = 5.53; P _p * = 9.7, excluding efficiency
l _p * = 1350 - 29.3 - 4 [1-1 / 9.7 ^0.25 ] =
= 68572 kgm / kg,
T _p * = 1350 - 68572.5 / (29.3 · 4) = 764.9 K, γ $\genfrac{}{}{0ex}{}{\text{*}}{\text{p}}$ = [10330 · 14 · 0.95 · 0.95 · 0.95 (1350/670)] / [9.7 · 764.9 · 29.3] = 1.1487,
6.313 / 1.1487 = 5.49 is close to the value of 5.48.

= П $\genfrac{}{}{0ex}{}{\text{*}}{\text{p}}$ /5,48 = 20,59/5,48 = 3,757.The degree of expansion of gases in an additional expansion machine is determined
P

= N $\genfrac{}{}{0ex}{}{\text{*}}{\text{p}}$ / 5.48 = 20.59 / 5.48 = 3.777.

For example, we consider an internal combustion engine made by the proposed method and device, the value of the effective power is N _eff = 80 l. with. , with two chambers of the working fluid, two rows of pairs of opposed cylinders of an additional expansion machine at values of P _k * = 14, T _g * = 1350 K.

= 80/484 = 0,16528 кг/с.The air flow through the combustion chamber

= 80/484 = 0.16528 kg / s.

The volumetric air flow rate when filling with air from the chamber of the working fluid Q ₁ = 0.16528 / 1.16 = 0.14248 m ³ / s.

The volume of the chamber of the working fluid at a rotor speed of P _p = 6000 rpm in an amount of 2 is determined by v _k = 0.14248 / [(6000/60) · (2/2)] = 0.14248 / 100 = 0.0014248 m ³ = 1424.8 cm ³ .

If the inner diameter D body of working fluid chamber taken equal to 250 mm and the diameter d of the rotor liner taken equal to 180 mm, the working fluid chamber length is equal to v _to ≈ [(π · 25 ^2/4) - (π · 18 ^2/4) / 2] - [(25-18 / 2) · b _inflection. ] · L; with the width of the partitions b _over = 2.5 cm,
101.9 ˙ l ≈1424.8; l ≈1424.8 / 101.9 ≈13.98 cm ≈140 mm.

= 0,9852 кг/м³.The specific surface area of the gases in the cylinders of an additional gas expansion machine before expansion
γ $\genfrac{}{}{0ex}{}{\text{*}}{\text{s}}$ _d.m =

= 0.9852 kg / m ³ .

The volumetric gas flow through the cylinders Q _g = 0.16528 / 0.9852 = 0.1678 m ³ / s = 167800 cm ³ / s.

With a crankshaft speed of _n.s. = = 6000 rpm when cooled by atmospheric air with a total number of cylinders 4 the volume of one cylinder ΔV is determined
Δv = [(167800/6000) / 60] · 2 = 839 cm ³ = 839 cm ³ .

= 3,757 (см. выше).The degree of expansion of gases in the cylinders of an additional gas expansion machine is determined by P

= 3.777 (see above).

In this case, the expansion work without taking into account the efficiency l _p * = 764.9 ˙29.3 ˙4 [1-1 / 3.757 ^0.25 ] =
= 25280.25 kgm / kg;
T _p * = 764.9 - 25280.25 / (29.3 · 4) = 549.2 K;
γ $\genfrac{}{}{0ex}{}{\text{*}}{\text{p}}$ = 10330 / (σ ₆ · 549 · 29.3) = 0.7555 kg / m ³ .

The volumetric flow rate of gases
Q _g = 0.16528 / 0.7555 = 0.2188 m ³ / s,
γ $\genfrac{}{}{0ex}{}{\text{*}}{\text{g}}$ _.a.m / γ $\genfrac{}{}{0ex}{}{\text{*}}{\text{p}}$ = 0.9852 / 0.2188 = 4.502,
V _c = 839 ˙ 4.502 = 3788 cm ³ .

=

= 16,9 см
Для уменьшения диаметра поршней цилиндров количество оппозитно расположенных цилиндров можно увеличить. При общем количестве цилиндров z = 8 рабочий объем одного цилиндра V_ц = 3788/4;
D =

=

= 10,6 см.When the piston stroke H = D, the diameter of the cylinder pistons is determined
(π · D ^2/4) D = 3788; D =

=

= 16.9 cm
To reduce the diameter of the pistons, the number of opposed cylinders can be increased. With a total number of cylinders z = 8, the working volume of one cylinder is V _c = 3788/4;
D =

=

= 10.6 cm.

=

= 8,45 cм. (56) Патент США N 4245597, кл. F 02 B 53/00, опубл. 1981. When performing an additional expansion machine without cooling, the diameter of the piston cylinders with a total of 8 is the value of the crankshaft speed
n _sq = 6000 rpm, the diameter of the pistons of the cylinders is determined
D =

=

= 8.45 cm. (56) U.S. Patent No. 4,245,597, cl. F 02 B 53/00, publ. 1981.

Claims (3)

 1. The method of operation of an internal combustion engine, carried out by admitting a fresh charge to a rotary volumetric machine, compressing, transferring a compressed charge to a constant-volume combustion chamber, supplying fuel to the latter through at least one nozzle, igniting and burning a fuel-air mixture, bypassing burning gases from the combustion chamber and two-stage expansion of exhaust gases with the conversion of the expansion work into rotation of the output shaft and their subsequent release into the atmosphere, characterized in that the fuel supply in the chamber in the case of combustion, it is carried out continuously, burning gases are transferred from the combustion chamber back to the rotary volumetric machine with the exhaust gases expanding therein, and the latter are expanded by transferring them from the rotary volumetric machine to the piston expander, and the amount of fuel supplied to the combustion chamber is controlled by changing the amount connected nozzles.  2. An internal combustion engine comprising a housing, a rotary supercharger and an expander mounted in it on the output shaft, made in the form of a cylinder with partitions and a rotating piston installed in it, and a continuous expansion machine and a constant volume combustion chamber connected to the supercharger and expander using gas channels with installed valves with actuator and equipped with at least one nozzle and igniter, characterized in that the rotary supercharger and expander are made in one piece, n an elastic ring seal is located on the working surface of the cylinder, the rotating piston is made in the form of a rolling bearing mounted eccentrically on the output shaft relative to the axis of the cylinder and in contact with the cylinder seal, partitions are mounted on cylindrical guides mounted in the cylinder, the continuous expansion machine is made of a piston and equipped with a mechanism gas distribution and a crankshaft connected to the output shaft, and the valve actuator is made in the form of cam discs, mounted coaxially with the output shaft and kinematically connected with it using gearboxes with a gear ratio i = 2, the gas distribution mechanism made in the form of a spool mounted around a continuous expansion machine, kinematically connected to a cam disk and equipped with an annular gas intake connected to the expander of the rotary machine .  3. The engine according to claim 2, characterized in that the valve spool is equipped with an annular intake for supplying cooling air.

Images