RU2631849C1 - Power plant and steam generator for this power plant (two versions) - Google Patents

Abstract

FIELD: machine engineering.

SUBSTANCE: claimed plant can operate with various steam-gas plants providing constant or cyclic delivery at the outlet of the vapour-gas mixture. The steam generator can be used both in the composition of the power plants and separately. According to the second technical solution, the working medium participating in the operation of the multi-section expansion machine is formed by combusting fuel and mixing the combustion products with steam from liquid heated in the steam generator mounted in the combustion chamber. By controlling the process of forming the vapour-gas mixture by the controller, it is possible to obtain the working medium in the combustion chamber with different parameters, including with different temperature which is not lower than dew point. In the power plant, the working medium from the steam generator is continuously or cyclically discharged into the receiver of the steam-gas mixture and then supplied to the multi-section expansion machine, where it is expanded to maximum by rotating the power take-off shaft. The last section of the multi-section expansion machine functions as a vacuum pump and the remaining condensate with combustion products is collected in reservoir for collecting condensate, and the remaining combustion products of the fuel are collected at service stations.

EFFECT: increased thermodynamic efficiency of the power plant and the steam generator by reducing losses of heat energy of the burnt fuel discharged outside through the cooling system and with exhaust gases.

28 cl, 6 dwg

Description

The invention combines two independent technical solutions that are interconnected and relate to the fields of heat power engineering and mechanical engineering, in particular to power plants operating on a mixture of steam and combustion products of hydrocarbons.

The first technical solution is a power plant with a steam and gas generator, designed to convert thermal energy from burning hydrocarbon or other fuel into rotational energy of the output shaft and then transfer it to the actuator drive.

The second technical solution is a steam and gas generator, which is associated with the first, and can be used in this or other power plants, and also used to create an independent device for producing a gas-vapor mixture of high pressure and temperature in various required ranges.

In currently known installations, heat of combusted hydrocarbons is consumed:

1) the useful work of the installation;

2) to heat the mechanical parts of the installation;

3) for heating gases and combustion products emitted into the environment from this installation.

Known power plants made on the basis of gas turbine engines, or rotary engines, or internal combustion engines. Moreover, these power plants have a specific purpose, they are not inherent in universality.

For example, the technical solution of a power plant is known - patent (19) RU, (11) 2211342, (13) C2, (51) IPC F01K 21/04 (2000.01), F02C 6/00 (2000.01), F25B 30/00 (2000.01 ), (71) Applicant (s): Federal State Unitary Enterprise "Moscow Machine-Building Industrial Enterprise" Salyut ", (72) Author (s): Belyaev V.E., Kosoy A.S., Sinkevich M.V., ( 73) Patent holder (s): Federal State Unitary Enterprise "Moscow Engineering Production Enterprise" Salyut ", (54) POWER INSTALLATION.

Moreover, this technical solution has a certain application - it is intended for use in the public utilities sector.

The technical solution is aimed at reducing heat loss to the environment and simplifying the installation scheme.

This power plant contains a gas turbine engine with a turbine running on a gas-vapor mixture; the first capacitor having two inputs and two outputs. In this case, the first output of the first condenser and the gas turbine engine input are connected with the atmosphere, the turbine output connected to the power load is connected to the first input of the boiler, the first output of which is communicated with the first input of the first condenser. The structure of this installation also includes a contact-vacuum evaporator communicated at the input with the second output of the first condenser; a supercharger pump connected by an input to the first output of the contact-vacuum evaporator, and by an output to the second input of the first condenser; vacuum compressor; second capacitor and feed pump. In this case, the vacuum compressor is connected to the input and output, respectively, to the second output of the contact-vacuum evaporator and the first input of the second condenser. The feed pump is installed in the line connecting the first output of the second capacitor through the boiler with a gas turbine engine, and the second input and second output of the second capacitor are the input and output of the installation for connecting the consumer.

The disadvantages of the technical solution of this power plant are the disadvantages of a gas turbine engine, such as:

- the impossibility of using it for various purposes; (narrow application of this installation);

- incomplete combustion of fuel, which significantly affects the efficiency of the installation;

- its large weight and dimensions;

- slow start and exit to mode;

- the high cost of gas turbine engines.

The low efficiency of the above power plants is the incomplete use of energy from burnt fuel.

Closest to the claimed technical solution is the solution is RU (11), 2126490 (13), C1, (51) IPC ⁶ , F02C 3/30, (72) Author (s): J. Lyell Ginter (US), (73) Patentee (s): J. LyellGinter (US), (54) INTERNAL COMBUSTION ENGINE, METHOD FOR OPERATING THE ENGINE AND CONTINUOUS SUPPLY OF THE WORKING BODY, where this internal combustion engine operates under high pressure.

A high pressure internal combustion engine in which a working fluid is used, consisting of a mixture of compressed air components unused during combustion, combustion products of fuel and steam, and a method for operating the engine and continuous supply of the working fluid are used in steam engines. According to the inventions, the working fluid is delivered at a constant pressure and temperature. Combustion air is adiabatically supplied by one or more compression stages. Fuel is injected at the right pressure. At least about 40% of all compressed air is burned. An inert liquid is injected under high pressure to form a vapor and thereby produce an inert vapor diluent with high specific heat required for internal cooling of an internal combustion turbine or other type of system. The active use of liquid injection prevents the formation of contaminants, increases efficiency and engine power and reduces specific fuel consumption.

The technical solution presented above is taken for a close analogue also because, like the claimed installation, it does not, in contrast to power plants operating on the principle of reciprocating internal combustion engines (hereinafter referred to as ICE), reciprocating piston movements, thereby the installation there are no loads on the mechanisms caused by acceleration and braking of the reciprocating moving parts of the internal combustion engine and, accordingly, there is no need to balance the parts and details used in the inventive power plant ke. But when using a turbine in the presented analogue, all its shortcomings will manifest themselves (turbine shortcomings indicated above).

Also, a drawback of the power system (this internal combustion engine) will be incomplete combustion of air, insufficient cooling of the gas mixture entering the turbine, as a result, insufficiently high efficiency, insufficient environmental friendliness.

Technical task: to create a power plant that has an efficiency higher than that of the existing ones, in which the combustion products are completely utilized.

The technical result from the use of the inventive power plant is that its thermodynamic efficiency is significantly increased due to a decrease in the heat loss of the combusted fuel that is diverted outside through the cooling system and the absence of exhaust gases.

The effect is achieved due to the design of the power plant, which includes: an air compressor, which can have one or more sections; a circulation receiver of compressed air, which may have a cooling system; intercooler; one or more parallel gas and steam generators, which may have a different design; gas-vapor mixture receiver; an expansion machine, which can have two or more sections, the energy from which is transmitted to the power take-off shaft.

At the same time, it was possible:

- lower the temperature of the compressed air supplied to the steam and gas generator, due to two-stage cooling in the receiver and inteculer and, accordingly, increase the specific gravity of oxygen in the supplied volume of air;

- distribute this compressed air through a circulation receiver of compressed air into one or more steam and gas generators;

- burn fuel as completely as possible and obtain at the outlet of the gas-vapor mixture receiver a working fluid from the gas-vapor mixture with a temperature above the dew point (from 150 ° C) with a mass and, accordingly, a volume exceeding the mass and volume of gases from the fuel combustion products by controlling the supply process controller a para-gas generator of the required amount of components involved in combustion and the formation of a gas-vapor mixture. At the same time, a lower temperature of the working fluid allows using less heat-resistant materials for the receiver and the expansion machine;

- send a vapor-gas mixture from one or more steam-gas generators to the vapor-gas mixture receiver (depending on the required power of the power plant);

- convert the thermal energy of the vapor-gas mixture into the rotational energy of the output shaft, while cooling the vapor-gas mixture to a temperature not lower than the dew point;

- Condensate the entire spent steam-gas mixture and collect it in a separate tank (sump) for subsequent disposal or for separation and filtration of water and its reuse. Thus, the claimed power plant will work without environmental pollution.

The air compressor works due to the internal energy of the power plant (receives it from the power take-off shaft). Screw or other compressors are used as an air compressor. Using a screw compressor allows you to save the energy consumed by it on the rotation of the compressor. This is due to the fact that its mechanical efficiency is up to 95% (for comparison, the mechanical efficiency of a reciprocating compressor is 60-80%). Screw compressors have a more advanced system for regulating the productivity of the produced air. That is, they have the ability to produce just as much air as it currently needs to burn the right amount of fuel to generate the required volume of gas-vapor mixture. A screw compressor produces cleaner air. The oil content, due to the use of a more efficient oil separation system, is lower at the outlet of the screw compressor than other types of oil-filled compressors.

The claimed power plant has two toroidal circulation receivers in which the substance in it moves in a circle due to the supply of new portions through collectors installed at an angle of the air or gas mixture in them. In the circulation receiver of compressed air, this air is cooled by cooling radiators, and in the circulation receiver of the gas-vapor mixture, it is heated to maintain the necessary temperature and pressure in this mixture by supplying additional heat to the inside of this receiver.

As a result, it was possible to create a plant with high efficiency, more environmentally friendly, which does not pollute the atmosphere with exhaust fumes, because these combustion products condense, accumulate in the sump and can be disposed of, or condensed water can be separated and filtered for reuse in the power plant.

Description of the power plant

The power plant consists of collectors connected in series, or bypass openings:

- an air compressor, which may have one or more sections;

- a circulation receiver of compressed air, which has a toroidal shape with a cooling system, for example, radiator fins, tubes, etc., and is connected to sections of the air compressor and steam and gas generators by means of manifolds located at an angle to the tangent to the surface of the torus. The number of compressed air manifolds is equal to the number of sections of the air compressor plus the number of taps to the steam and gas generators. In the case of using one air compressor, the number of collectors must be at least two;

- intercoolers;

- one or several parallel-coupled gas generators of various designs (hereinafter referred to as PRGG), having compressed air collectors at the inlet, a fuel supply pipe and a water supply pipe and combined-gas mixture collectors at the outlet. The function performed by the steam and gas generator is to produce a gas mixture from steam and hydrocarbon combustion products. The valves in the PRGG can have both mechanical and electromagnetic actuators.

All electromagnetic controlled valves of steam and gas generators, as well as temperature sensors and pressure sensors are connected to the controller.

Compressor sections connected in parallel, as well as PRGG, have solenoid valves controlled by a controller in manifolds or bypass holes;

- a circulation receiver of a gas-vapor mixture of a toroidal shape, which is thermally insulated from the inside and inside has temperature and pressure sensors, while it can have a steam-gas mixture heating system and is connected to the PRGG and an expansion machine by means of collectors located at an angle to the tangent to the surface of the torus. The number of steam-gas mixture collectors corresponds to the number of PRGG, plus the number of taps to the expansion machine. If there is one PRGG, then at least two collectors are suitable from it to the receiver (to provide more intensive circulation of the vapor-gas mixture in the receiver);

- a multi-section expansion machine, where the last of its sections can act as a vacuum pump, while a pneumatic motor, a rotary vane rotor machine, or a turbine, or such as a screw or spiral expansion machine or other structures can be used as a multi-section expansion machine.

The power plant also has a power take-off shaft, a control controller connected to all temperature and pressure sensors and solenoid valves, a kinematic connection between the power take-off shaft and the expansion machine, as well as a kinematic connection between the power take-off shaft and the compressor (or its sections), mechanisms on-off and coordination of revolutions of sections.

Collectors can be thermally insulated, and if necessary, a cooling system.

In FIG. 1 presents a functional diagram of a power plant, which consists of:

1. Air compressor multisection.

2. Collector by-pass compressed air.

3. A circulation receiver of atmospheric air, with a cooling device located in it compressed air.

4. A collector of compressed air.

5. Steam and gas generator (hereinafter referred to as PRGG).

6. The manifold bypass steam-gas mixture insulated from the inside.

7. The circulation receiver of the vapor-gas mixture insulated from the inside.

8. The manifold bypass steam-gas mixture insulated from the inside.

9. Multisection expansion machine.

10. The vacuum condensation section of the expansion machine.

11. Power take-off shaft.

12. The kinematic connection of the expansion machine with the power take-off shaft (belt, chain, variator, or other connection).

13. Devices for switching on and off and matching the revolutions of the shaft of the expansion machine with the power take-off shaft (for example, an electromagnetic on-off device, devices with an oil or magnetic clutch, or some other device).

14. The kinematic connection of a multi-section compressor with a power take-off shaft (belt, chain, variator, or some other).

15. Devices for turning on and off and matching the revolutions of the shaft of a multi-section compressor with a power take-off shaft (for example, an electromagnetic on-off device, devices with an oil or magnetic clutch, or some other device).

32. Intercooler.

33. Sump for condensed waste.

34. The controller control.

35. Compressor sections.

36. Section of the expansion machine.

In FIG. 2 shows a diagram of a compressor 1 with its sections 35 of a compressed air receiver 3, supply of collectors 2 to a receiver 3 and a collector 4 from a receiver 3 and a steam-gas generator 5 supply circuit with compressed air; temperature sensors 30 and pressure 31 are shown; also shown is an electromagnetic valve 39, overlapping parallel-connected compressor sections 35; kinematic connections 14 of an air multi-section compressor 1 are shown in more detail with a power take-off shaft 11 (belt, chain, variator, or other communication), as well as devices 15 for turning on and off and matching the rotations of the air compressor multi-section 1 shaft with a power take-off shaft 11 (for example , electromagnetic on-off device, devices with an oil or magnetic clutch, or some other); also shows a section AA of the compressed air receiver, shown in detail in FIG. 5 and FIG. 6, where compressed air cooling devices or cooling fins 41 or coolant tubes 42 are shown.

In FIG. 3 shows a steam and gas generator 5, which is claimed as an independent item, its device and operation is described in a separate independent section.

In FIG. 4 shows a diagram of a receiver for a vapor-gas mixture insulated 7, a supply to it of bypass insulated manifolds of a vapor-gas mixture 6 and a drain from it for a collector of a bypass insulated vapor-gas mixture 8, temperature and pressure sensors 58 are also shown; also shown is a solenoid valve 39, overlapping steam and gas generators 5 connected in parallel; An expansion machine 9 is shown with its expansion sections 36, where the last section 10 operates as a vacuum condensing machine and the condensed spent steam-gas mixture is placed in a condensed waste sump 33; the kinematic connections 12 of the expansion machine 9 with the power take-off shaft 11 are shown in more detail (belt, chain, CVT or other communication), as well as on-off devices and adjustments of the rotations of the shaft of the expansion machine 9 with the power take-off shaft 11 (for example, an electromagnetic switch-on device) - shutdowns, devices with an oil or magnetic clutch, or some other).

In FIG. 5 shows a section through a receiver of compressed air with its cooling fins 41.

In FIG. 6 shows a section through a receiver of compressed air with its radiator cooling tubes 42, where the movement of the coolant is also shown by arrows.

The table shows the characteristics of modern diesel engines of different power and volume and their specific fuel consumption.

POWER INSTALLATION works as follows:

A multi-section air compressor 1 pumps atmospheric air through an atmospheric air collector 2 into a circulation receiver of atmospheric air 3.

The air circulating in the circulation receiver 3 passes the first cooling stage, being cooled by the cooling device installed in the receiver 3 (for example, cooling fins 41 (Fig. 5), or radiator tubes with coolant 42 (Fig. 6).

From the circulation receiver 3, compressed atmospheric air, under pressure through the compressed air collector 4, enters the intercooler 32, where the second cooling stage passes. Further, from the intercooler 32, compressed atmospheric air enters the steam and gas generator 5, where it participates in the combustion of fuel.

In the steam and gas generator 5 (Fig. 3) through the pressure, volume and quantity control devices (for air the reducer is 60, for fuel and water are not shown), controlled by the controller 34 based on the readings of temperature sensors 54, 56 and pressure sensors 55, 57, are supplied under pressure fuel, air and water. In a steam and gas generator, fuel is burned and fuel combustion products are mixed with injected water or superheated steam. The ratio of the amount of these components and the feed time depends on what parameters the working fluid — the vapor-gas mixture — will have (hereinafter referred to as PRGS).

Then, through the heat-insulated collector of the vapor-gas mixture 6, the PRGS enters the heat-insulated circulation receiver of the gas-vapor mixture 7. From the heat-insulated circulation receiver of the gas-vapor mixture 7, through the heat-insulated collector of the gas-vapor mixture 8, the PRGS is supplied to the expansion machine 9 under pressure, where it expands and performs work with a temperature above the dew point in one or more sections 36 of this expansion machine. Section 36 of the expansion machine 9 performs a stepwise expansion of the incoming PRGS. The preset PRGS parameters for operation in the expansion machine, such as temperature and pressure, are maintained in the circulation receiver 7 of the vapor-gas mixture due to the presence of the liquid injection nozzle 37 integrated in it and the operation of the heater 40 (see Fig. 4)

The power of the power plant can vary widely depending on the amount of gas-vapor mixture produced. This amount can increase due to the connection through the power take-off shaft 11 of both additional compressor sections 35, additional steam and gas generators 5, and additional sections of the expansion machine 9 (due to its additional expansion sections 36). Compressor sections are connected to the power take-off shaft 11 using an on-off device and speed matching 15 (for example, an electromagnetic on-off device, an on-off device with an oil or magnetic clutch, or another clutch), via kinematic coupling 14 (belt, chain, CVT or other). Additional sections 36 of the expansion machine 9 are connected to the power take-off shaft 11 through a kinematic connection 12 (belt, chain, CVT or other) using the device 13 (on-off device and matching the revolutions of the shaft of the expansion machine with the power take-off shaft, for example, electromagnetic inclusion switching off, switching on / off with an oil or magnetic coupling, or another coupling).

The last section 10 of the expansion machine 9 can operate as a condensation vacuum pump, where the exhausted, fully expanded, vapor-gas mixture condenses and enters the condensed waste sump 33.

The second independent solution claimed - a gas and steam generator is one of the possible options for the power unit, it can also be used as a standalone device to obtain a gas mixture.

A technical solution is known for a steam and gas generator, which relates to internal combustion engines (ICE) and can be used in automobile, tractor, ship and stationary ICE. The invention provides an increase in the rate of vaporization during the injection of water into the exhaust manifold and an increase in the enthalpy of combustion products.

(19) RU, (11) 2338914, (13) C2, (21), (22) Application: 2005137879/06, 12/05/2005, (51) IPC F02G 5/02 (2006.01), F02B 47/02 (2006.01 ) F02B 37/00 (2006.01), (72) Author (s): Egorov Alexey Vasilievich (RU), Egorov Vasily Nikolaevich (RU), Kudryavtsev Igor Arkadievich (RU), (73) Patentee (s): Egorov Alexey Vasilievich ( RU), Egorov Vasily Nikolaevich (RU), Kudryavtsev Igor Arkadievich (RU), (54) INTERNAL COMBUSTION ENGINE.

This ICE can also be considered as a steam and gas generator used in vehicles.

This invention is indicated among analogues, since this patented device has common essential features with the features found in the claimed device: this is the presence of combustible fuel and its combustion products; the presence of a water supply pipeline, which is equipped with a heat regenerator of fuel combustion products; superheated steam or water that is injected into the fuel combustion products.

The disadvantage of this engine is the low efficiency resulting from the fact that large heat losses occur in it, because ICE combustion chamber is not thermally insulated. The gas-vapor mixture has a very high temperature and is not completely utilized.

Closest to the claimed technical solution is RU (11), 2126490 (13), C1, (51) IPC ⁶ , F02C 3/30, (72) Author (s): J. Lyell Ginter (US), (73) (i): J. Lyell Ginter (US), (54) INTERNAL COMBUSTION ENGINE, METHOD OF WORKING THE ENGINE AND CONTINUOUS SUPPLY OF THE WORKING BODY, where this internal combustion engine operates under high pressure. The steam and gas generator, which is part of this engine, is a combustion chamber, which is placed in a chamber into which air is pumped, which cools the walls of the combustion chamber, into which air, fuel and water are supplied. The resulting vapor-gas mixture is a working fluid, consisting of a mixture of compressed unused components of air, combustion products of fuel and steam that are formed in the internal combustion chamber. The device uses a combustion regulator, which is configured to control the liquid supply means and the fuel supply means in the combustion process. In this case, the weight of the injected liquid is approximately two or more times the weight of the injected fuel, due to which the mass of the working fluid is increased to maintain the average temperature in accordance with the required operating temperature of the working engine, and the combustion chamber is configured to burn at least 40% compressed air. According to the inventions, the working fluid is delivered at a constant pressure and temperature.

The disadvantages of this steam and gas generator are insufficiently high efficiency due to the fact that the combustion of fuel occurs in a mixture with the vapor supplied to the combustion chamber of the evaporated liquid, as a result of which the fuel may not be completely burned and, accordingly, the fuel will not give all its internal energy, lowering the efficiency .

The technical result of the proposed technical solution for a gas and steam generator

- increasing the efficiency of the steam and gas generator due to the complete combustion of the fuel and obtaining the vapor-gas mixture of the required pressure from the products of combustion of this fuel and the liquid injected into the gas-vapor installation, as well as synchronizing the operation cycles of the steam and gas generator with the operating cycles of cyclically operating devices included in the power plant, for example, a piston expansion machine or other similar devices.

This result was obtained due to the fact that the vapor-gas mixture is formed under optimal conditions created under the control of the controller for fuel combustion and heat exchange of the combustion products of this fuel with injected liquid or injected superheated steam.

Description of the steam and gas generator

The steam and gas generator includes:

- serially connected to each other a compressed air reducer of working pressure, a working pressure chamber and a combustion chamber with a steam generator built into it.

Each of these working pressure compressed air reducers, in turn, is connected to the combustion chamber through the bypass and intake valves (bypass, if necessary).

Working pressure chamber - a container into which air is pumped under the required pressure through a working pressure compressed air reducer.

In this case, the combustion chamber with a built-in steam generator is thermally insulated from the inside and has a constant volume, made with inlet and outlet valves and an overpressure valve that open-close mechanically, or using electromagnets controlled by the controller. In this case, the combustion chamber may have a spherical shape.

At the same time, at least:

one fuel injection nozzle;

one device for igniting fuel (electric coils, candles, lasers);

one heat exchanger for the supplied fluid;

one heat exchanger for supplied fuel;

heat exchangers for the supplied liquid and the supplied fuel are installed (built in) in the housing of the combustion chamber, they will take part of the heat from the housing of the combustion chamber to increase their internal energy and will help protect the housing from overheating;

one superheated steam heat exchanger-generator with at least one liquid or superheated steam injection nozzle, with a controlled valve for superheated steam or liquid, it is preferable to install two liquid or superheated steam injection nozzles so that the injected liquid vapors are cleaned of combustion products fuel; heat exchanger of supplied liquid;

temperature and pressure sensors are installed in the working pressure chamber, as well as in the combustion chamber.

A fuel injection nozzle and a fuel ignition device are installed in the combustion chamber, which can be either a spiral of ignition, or a spark plug of a mixture, or a laser device for igniting a mixture; a steam generator, which is a heat exchanger in the form of a pipeline with a large surface area:

- the heat exchanger may have fins increasing its area for heat transfer intensity;

- the heat exchanger has a fluid channel, at least one nozzle with a valve for releasing superheated steam and is equipped with a high-pressure liquid pump, and the liquid channel supplying it is equipped with an automatic check valve.

The output collector of each of the steam and gas generators - the collector of the gas mixture is connected to at least one input collector of the receiver of the insulated gas mixture.

The steam and gas generator (see Fig. 3) consists of:

60 - Compressed air reducers working pressure.

16 - Working pressure chambers.

17 - Bypass valve (can be set - do not set).

18 - Inlet valve (if the valve has the ability to hold the reverse pressure of compressed air created in the working pressure chamber, then valve 17 can be omitted).

19 - Combustion chambers insulated from the inside, with a heat exchanger-generator of superheated steam 28.

20 - Exhaust valve.

21 - Overpressure valve.

47 - Heat exchanger for supplied fuel.

22 - Fuel injection nozzles.

23 - Fuel ignition devices (electric coils, candles, lasers).

24 - Pipeline or channel for the supply of evaporated liquid.

25 - High pressure pump for evaporated liquid.

26 - Check valve for evaporated liquid.

27 - Heat exchanger for the supplied fluid.

28 - Heat exchanger - superheated gas generator.

29 - Nozzles with a controlled valve for superheated steam or liquid.

54 - temperature sensor of the working pressure chamber 16.

55 - Pressure sensor working pressure chamber 16

56 - The temperature sensor of the combustion chamber 19.

57 - Pressure sensor of the combustion chamber 19.

38 - Manifolds for gas-vapor mixture overpressure.

Steam generator works as follows.

The air compressed by the compressor 1, through the collector 2 enters the receiver of compressed air 3, in which the first cooling stage passes;

further, passing through the intercooler 32, the air passes the second cooling stage, where at both cooling levels its specific gravity and, accordingly, the mass of oxygen in a given mass of air increases;

further, the cooled compressed air through the working pressure reducer 60, controlled by the controller 34 based on the readings of the temperature sensors 54 and pressure 55 installed in the working pressure chamber 16, enters the working pressure chamber 16 under the necessary pressure;

the required amount of air is supplied to the combustion chamber 19 directly from the working pressure chamber 16: the reducer 60 passes the necessary amount of air into the working pressure chamber 16 (taking into account the volume ratios of the combustion chamber 19 and the working pressure chamber 16) and when the required pressure in the working pressure chamber is reached 16 blocks the flow of air into this chamber;

then open the bypass valve 17 (if any) and the inlet valve 18 and the cooled compressed air under pressure from the working pressure chamber 16 enters the combustion chamber 19; the volume of the working pressure chamber 16 may significantly exceed the volume of the combustion chamber 19; while the pressure in the working pressure chambers and the combustion chamber is equalized and the valves 17, 18 are closed; the combustion chamber 19 is ready for the working cycle, and the working pressure chamber 16 draws air through the pressure reducer 60 with the working pressure for the next working cycle with the combustion chamber 19;

then a working cycle takes place in the combustion chamber 19: the fuel preheated in the heat exchanger of the supplied fuel 47 is injected under pressure through the fuel injection nozzle 22 into the combustion chamber 19, mixed with compressed air and ignited from the ignition device 23 (spark plug, ignition coil, laser device) and burns in a constant volume of the combustion chamber (isochoric process), with constantly increasing pressure and temperature, which contributes to efficient and complete combustion of fuel.

After complete combustion of the fuel and absorption by the liquid in the heat exchanger 28 of the heat from the working gas, a valve opens in the nozzle for injecting liquid or superheated steam 29 and superheated steam or atomized liquid enters the combustion chamber 19 from the heat exchanger 28, which (i) is mixed with high-temperature products of fuel combustion, cools them and, as a result, a gas-vapor mixture is formed with predetermined characteristics, for example, a temperature of 150-500 ° C and a pressure of 60-250 atmospheres or more (depending on the specified steam etrov PSRP). The amount of atmospheric air, fuel and injected steam or water in the combustion chamber will be set and controlled by the controller 34 and will provide them with the ratio necessary for the cycle. It is advisable to install more than one injection nozzle for liquid or superheated steam 29 so that the injected liquid vapors clean the fuel heat exchanger of the supplied liquid 28 from fuel combustion products, which will facilitate its more efficient heat exchange with high-temperature gases of the burnt fuel. After the heat exchange between high-temperature combustion products and injected with superheated steam or sprayed liquid, the formation of PRGS is completed, then the exhaust valve 20 opens and PRGS under pressure enters the heat-insulated receiver of the gas-vapor mixture 7. The required temperature and pressure parameters are maintained in the heat-insulated receiver 7 of the PRGS due to built-in heating devices 40 and liquid injection devices 37, (see Fig. 4) for example electric heaters and a liquid injection nozzle, where the injection fluid can be provided from the high pressure pump 25 (see Fig. 3). Next, the exhaust valve 20 closes and the overpressure valve 21 opens. The remaining PRGS leaves the combustion chamber through the overpressure valve 21 and enters the overpressure manifold 38, transferring its heat to the liquid supplied to the steam and gas generator through the heat exchanger 27. The pressure in the combustion chamber drops to atmospheric. The steam and gas generator is ready for a new duty cycle. Next, the cycle repeats.

Power plant example

The claimed technical solution of the power plant allows you to perform it in a very wide range of power with so many compressor sections that can provide compressed air to the required number of steam and gas generators.

The power plant is made according to proven technologies from well-known parts, assemblies and mechanisms that have long been used in industry.

A steam and gas generator can also have a wide range of performance.

The characteristics of the gas-vapor mixture can also be different and depend on the parameters of the gas-vapor generator, the amount of air and fuel supplied, which, in turn, will depend on the required power of the power plant.

In the same way, the number of sections of the expansion machine is selected.

Comparative calculation of the efficiency of the power plant

As stated above:

- The operation of the steam generator and power plant is as follows. Air and fuel are supplied to the combustion chamber of the steam and gas generator under pressure, the mixture is ignited from the ignition device, the mixture begins to burn in the combustion chamber, at the outlet of the combustion chamber of the high-temperature products of the burnt fuel, water heated in the heat exchanger is injected under pressure. Next, the atomized particles of water are mixed with high-temperature products of fuel combustion and evaporate. Ultimately, at the outlet of the steam and gas generator, we get a steam-gas mixture of the pressure and temperature we need. We obtain the necessary pressure, temperature of PRGS due to the proportions of the amount of fuel burned and the amount of injected water.

Further on: diesel fuel - DT, air motor - PNM, gas-vapor mixture - PRGS.

Reference data:

10300 - heating capacity of 1 kg of diesel fuel (kcal / kg),

86 is the heat capacity of vaporization (kcal / kg),

1700 - the value by which the state of aggregation of water increases, i.e. 1 cc cm of water turns 1700 cubic meters. cm steam (or 1.7 liters).

Based on the above ratios of the evaporated volume of water and fuel burned, we obtain the following results:

We get:

10300/586 = 17.6 kg of water we can evaporate, burning 1 kg of diesel fuel,

17.6 kg = 17600 g (cubic cm) ⋅1700 = 29920000 cubic cm = 29.92 cc m

We round off to facilitate calculations and take 30 cubic meters. m

Consumption 1 cubic meter m of compressed air (in our case PRGS), gives a little less than 1 kW of power (we take for 1 kW), which proves a comparative analysis of air motors. We look at an example of a pneumatic motor (for example, the DEPRAG brand, model FM-32-LLUB), which at a flow rate of 1.9 cubic meters. m of air per minute produces 1.9 kW of power, which confirms the flow rate of 1 cubic meter. m of compressed air (in our case PRGS) gives us ~ 1 kW of power on the PNM shaft.

Accordingly, instead of air, we can use the resulting vapor-gas mixture of the temperature and pressure we need. Thus, obtained from the combustion of diesel fuel 30 cubic meters. m PRGS gives ~ 1 kW of power per cubic meter. m PRGS, from here we get ~ 30 kW of power supplied by the pneumatic motors, while providing it with the required number of pneumatic motors and the required volume and the required temperature and pressure of the PRGS.

Clarification - the amount of PRGS from burning one kilogram of diesel fuel can be greater, since the calculation of the volume of gas from the burned diesel fuel has not yet been taken into account.

The volume of PRGS is calculated on the resulting temperature of the steam from the evaporation of water - 100 ° C and, accordingly, the vapor-gas mixture itself. In order to obtain the PRGS temperature required for the PNM operation, part of the heat of combustion of the diesel fuel will go to increase the temperature of the PRGS itself, since the heat capacity of the steam is not large - 0.48 kcal / g. kg, then this will not take much heat (you can neglect). Correction for the required temperature of the PRGS for the operation of the ISM is given below.

If we get about 30 cc. m of steam per hour when burning 1 kg of diesel fuel (see below), then per minute we get ~ 0.5 cubic meters. m steam (30 cubic / 60 min). To feed the PNM with a flow rate of 1.9 cubic meters. m of steam per minute and to obtain 1.9 kW / h of power, it is necessary to increase the volume of PRGS 4 (four) times (up to ~ 2 cubic meters of PRGS per minute), i.e. burn not 1 kg of diesel fuel, but 4 kg of diesel fuel (this is approximately 5 liters of diesel fuel, taking into account the weight transfer coefficient (kg) of diesel fuel in volume (liters)). Thus, we get per hour ~ 120 cubic meters. m PRGS from burning one kilogram of diesel fuel (30 cubic meters PRGS⋅ 4 kg DT = 120 cubic meters). If you take 1 cube m of PRGS equal to a power output of 1 kW of power, then when burning 4 kg of diesel fuel per hour, we get the capacity of a PRGS steam generator of 120 cubic meters. m / h and, accordingly, the power of the installation = 120 kW.

But we did not take into account the power consumption for preparing the formation of the mixture for the operation of a steam and gas generator (air compression and water injection, DT), and also did not take into account thermal and mechanical losses.

Clarification: for more powerful pneumatic motors, the coefficient of receiving power from PRGS is not one to one, but less. We look at an example from practice: PNM (for example, DEPRAG brand, model 68-0065) with a capacity of 18 kW, consumes 20 liters of air or PRGS, i.e. coefficient = 0.9 (18/20)). Thus, the resulting power when using more powerful PNMs will be 120⋅0.9 = 108 kW.

The above calculations are for steam and, PRGS, respectively, 100 ° C, and for the operation of the PNM, the temperature of the PRGS is needed - 200-300 ° C (maybe more), it is likely that we will receive 120 cu. m of steam per hour, and slightly less than about ~ 100 cubic meters. m, then, accordingly, we will obtain ~ 90 kW of energy, using the coefficient (100 ⋅ coefficient 0.9 = 90 cm, the refinement is higher in the text). If we spend part of the energy received (take, for example, 40% of the received power) for the preparation of the PRGS (air compression and injection of diesel fuel), then we will receive about 54 kW of power at the output of the shaft of the PNM (pneumatic motors) when burning 5 liters of diesel fuel.

We get ~ 10.8 kW of power at a flow rate of 1 liter of diesel fuel (54/5 = 10.8), which is two times better than existing analogues. For reference: for analogues per liter of diesel fuel consumption, the resulting power is approximately 5 kW per liter of diesel fuel burned.

For example: TSS AD-50S-T400-1RM19 diesel generator, in which the DT consumption per hour is = 10.1 l / h with the developed power = 50 kW or TSS AD-60S-T400-1RKM11 whose DT consumption per hour is = 12.1 l / h with developed power = 60 kW. Accordingly, 5 kW of developed power (50 kW / 10.1 = ~ 5 kW or 60 kW / 12.1 = ~ 5 kW) per 1 liter of burned diesel fuel.

Since the efficiency of modern diesel ICEs used in electric generators is 35-45%, if we average this value, we will get the power plant efficiency of approximately = 70-90%. That, respectively, is about two times higher than that of the existing analogues of internal combustion engines and similar power plants.

Such a significant increase in the efficiency of the power plant occurs due to an increase in the mass of the working fluid (PRGS) and, accordingly, its volume and an increase in the degree of expansion of the working fluid. If we compare the degree of expansion of the volumes of the working fluid (working gas) of the average modern ICE in one working cycle of one working cylinder and the degree of expansion of the working fluid in the steam and gas generator of the claimed power plant, then the values differ several times not in favor of modern internal combustion engines. The expansion ratio of a modern internal combustion engine is approximately equal to the compression ratio in its cylinders, the values of which are in the range of ~ 10 to ~ 20 units (with the exception of internal combustion engines using a turbine at the outlet of working gases from the cylinder). In the proposed power plant, the degree of expansion of the vapor-gas mixture can be significantly increased by making a stepwise expansion of the working fluid, thereby obtaining more work from the working fluid when using one amount of fuel and, accordingly, heat from this fuel.

Claims (28)

1. The power plant, which includes an air compressor connected to one or several steam and gas generators connected in parallel, and a multi-section expansion machine connected in series through bypass manifolds, as well as a power take-off shaft connected by kinematic connection with the air compressor and the expansion machine; a pipeline with fuel and a pipeline with liquid connected to the steam and gas generator, the steam-gas mixture obtained at the output of the steam and gas generator used to rotate the power take-off shaft, a controller connected to temperature and pressure sensors and electromagnetic valves installed in the manifolds, characterized in that the power plant further comprises a compressed air circulation receiver, a vapor-gas mixture circulation receiver and an intercooler, wherein the compressed air circulation receiver is connected an air compressor and intercooler, the intercooler is connected to the steam-gas generator, which is connected to the receiver circulating gas mixture, which is connected to an expansion machine, the last of the sections which performs the function of the vacuum pump. 2. The power plant under item 1, characterized in that the air compressor is made with a cooling system. 3. The power plant according to claim 1, characterized in that the air compressor is multi-sectional. 4. The power plant under item 1, characterized in that the air compressor is made screw. 5. The power plant under item 1, characterized in that the air compressor is made rotary. 6. The power plant under item 1, characterized in that the air compressor is made spiral. 7. The power plant according to claim 1, characterized in that a container for collecting condensate is attached to the last section of the expansion machine. 8. The power plant according to claim 1, characterized in that a pneumatic motor is used as an expansion machine. 9. The power plant according to claim 1, characterized in that a rotary expansion machine is used as an expansion machine. 10. The power plant according to claim 1, characterized in that a turbine is used as an expansion machine. 11. The power plant according to claim 1, characterized in that a piston machine is used as an expansion machine. 12. The power plant according to claim 1, characterized in that a spiral machine is used as an expansion machine. 13. The power plant according to claim 1, characterized in that the collectors in the circulation receivers are located at an angle to the tangent surface of the torus. 14. The power plant according to claim 1, characterized in that metal radiators are used as a cooling system for the circulation receiver of compressed air. 15. The power plant according to claim 1, characterized in that liquid radiators are used as a cooling system for the circulation receiver of compressed air. 16. The power plant according to claim 1, characterized in that the number of collectors connecting the sections of the air compressor to the circulation receiver of compressed air is at least two. 17. The power plant under item 1, characterized in that the circulation receiver of compressed air has temperature and pressure sensors. 18. The power plant according to claim 1, characterized in that the circulation receiver of the vapor-gas mixture has temperature and pressure sensors. 19. The power plant according to claim 1, characterized in that the circulating receiver of the vapor-gas mixture is connected to the steam and gas generators and the expansion machine by means of collectors, the number of which corresponds to the number of steam and gas generators plus the number of taps to the expansion machine. 20. The power plant according to claim 1, characterized in that the circulating receiver of the vapor-gas mixture is connected to one steam-gas generator and an expansion machine by means of at least two collectors. 21. Steam and gas generator, including a combustion chamber with air supplied to it and a fuel supply pipe, with a nozzle, with an ignition device, with a liquid supply pipe to form a gas-vapor mixture supplied to the outlet by an exhaust valve, an overpressure valve, temperature and pressure sensors connected with a controller, characterized in that the steam and gas generator additionally has a working pressure compressed air reducer, the input of which is connected to the input manifold of compressed air, and the output through the collector - with the input of the working pressure chamber, the output of which is connected to the combustion chamber through the inlet valve, and a heat exchanger-generator in the form of a pipeline for the supplied fluid, which has at least one nozzle at the end. 22. The steam and gas generator according to claim 21, characterized in that the combustion chamber of the steam and gas generator has a spherical shape. 23. Steam and gas generator according to claim 21, characterized in that the pipeline is connected to the high-pressure liquid pump through an automatic check valve. 24. The steam and gas generator according to claim 21, characterized in that the process of formation of the vapor-gas mixture occurs cyclically. 25. The steam and gas generator according to claim 21, characterized in that the heat exchanger-generator of superheated steam has fins that increase its area for the intensity of heat transfer. 26. The steam and gas generator according to claim 21, characterized in that the output of the working pressure chamber is connected to the combustion chamber through the bypass and intake valve. 27. The gas and steam generator according to p. 21, characterized in that the housing of the combustion chamber has a heat exchanger for heating the supplied fluid. 28. The steam and gas generator according to claim 21, characterized in that the housing of the combustion chamber has a heat exchanger for heating the supplied fuel.

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