KR20050118069A - Air Heating Cycle System For Composition Power Plant. - Google Patents

Abstract

The system of the present invention is a method of constructing a heat engine using a queue to attempt to generate power and to cool down the atmosphere by using a heat amount of the air or seawater in a heat cycle engine. Since the second law of thermodynamics is likely to be a rule based on experience assuming that liquefaction of permanent gas (boiling point at atmospheric pressure below -150 ℃) is impossible in the past when the thermal phenomenon at the ultra low temperature could not be handled, it has come back to the present. In many cases, power generation using queues has been attempted several times.

We tried to find a way to absorb the queue mainly using refrigerants and attempted to obtain a theoretical calculation. However, since the critical temperature of the refrigerant is much higher than the atmospheric temperature, adiabatic expansion cannot be attempted at high pressure, so it is difficult to obtain liquefaction at low pressure after expansion. Therefore, it was impossible to liquefy without a low temperature heat source, so various methods were tried to reduce the required power of the compressor, but theoretically impossible, and the system could not be repeated, so the required power of the compressor could not be reduced. Therefore, even though the construction of a heat engine using a queue has been tried many times at present, it has not been theoretically possible by the second law of thermodynamics until now. This paper attempts to solve the problem by devising a device using liquid air rather than a refrigerant, and is intended to show that the second law of thermodynamics can be realistically and theoretically solved.

Description

Heat engine using air heat {Air Heating Cycle System For Composition Power Plant}

Technology: Thermal Refrigeration Engineering.

Conventional Technology: Compresses the expanded refrigerant as a compressor at low speed to condense it, vaporizes the refrigerant using the heat of the atmosphere, and then supplements the required power of the compressor with the power generated by the expander during expansion, thereby reducing the difference between the low speed compressor and the expander. Attempts have been made to generate work using the heat of the atmosphere as the power source. (In this case, because the critical temperature of the refrigerant is high, it must be expanded at high pressure to allow the vaporized refrigerant to condense again upon expansion because it is not possible. In order to increase the adiabatic effect and to obtain liquefaction, the refrigerant must be liquefied in advance (because it is liquefied if high pressure is applied below the critical temperature) to generate power in the expander. If pressure is applied above the critical temperature, it must be much higher than the temperature of the air so that it cannot receive the heat of the air.

Therefore, in order not to be affected by these conditions, the refrigerant is expanded at low temperature and pressure to generate power, and the low-speed compression is attempted to condense the expanded refrigerant to achieve power saving effect to obtain the power of the car between the expander and the compressor. However, since the overall size of the required amount is a natural phenomenon such as low speed or high speed, the power of the car with the inflator could not be generated, and a large amount of queue cannot be injected and the reuse of unliquefied refrigerant is impossible.

Using energy from the atmosphere to cool down the air without energy generation and low temperature heat sources has proved academically impossible, but many researchers have dare to challenge it.

Many devices have been tried and configured for generating power using queues by many inventors, but this is virtually impossible since engineering theories have not been established. To date, engineering theory has been impossible to create work by using the heat of the atmosphere without a low temperature heat source, no matter what device is made and configured, it was theoretically impossible to produce a device that can bring about the effect of reducing the atmosphere.

However, the present invention is intended to prove that depending on the configuration of the thermodynamic device, it may not. It is also a theory to show that it is possible to cool down the atmosphere with very little power, even if it is impossible to generate energy using the queue. It is true that the atmosphere receives heat from the sun and heat can be converted into work.

The present invention is a research design to prove that the low temperature heat source is not necessarily required to convert heat into work, and that the temperature reduction of the atmosphere is possible.

1) Principle

1> The principle of the adiabatic inflatable air liquefaction apparatus in the air liquefaction separator which is traditionally generalized and widely used to show the basic principle of the system is as follows.

① After cooling the air by compressing it (about 60 ata), expand it adiabaticly in the expander.

(Expansion pressure 1ata)

② Heat-exchange some of the air that is adiabatic and become low pressure and low temperature.

③ The heat exchanged heats up the compressed air before expansion

(Temperature after heat exchange:-30 ~-40 ℃) The low temperature air is thermally insulated to obtain ultra low temperature (-192 ℃), and the air is liquefied. (Vacuum insulation is used for complete insulation.)

2> Basic natural phenomena for the composition of this system are as follows.

① Compression and Liquefaction of Gas

When the gas is compressed at very low temperature, the entire liquid is liquefied if the temperature does not exceed the saturation temperature point. The lower the latent heat of condensation, the easier it is to liquefy. The lower the dryness, the easier it is to liquefy. If it becomes overheated during compression, it can be cooled to take away the heat of overheating and liquefaction can be obtained.

② Adiabatic expansion and liquefaction of gas

In the case of adiabatic expansion of compressed gas, the temperature decreases due to internal energy reduction. In addition, the rapid expansion at low pressure may further lower the temperature due to the Joule-Thomson effect. Even in the case of compressors with ultra-low temperature or ultra-high temperature conditions, the same phenomenon can occur if the effect of heat insulation is perfect, and if the temperature is below the boiling point due to the effect of heat reduction by adiabatic expansion of the compressed gas in the cryogenic state Can be.

③ Compression of gas and critical temperature

When a gas is subjected to any pressure above the critical temperature, no liquefaction occurs, and it is applied regardless of the type of gas or mixed gas. In addition, if the liquid is in a liquefied state and is subjected to a pressure higher than the critical pressure, vaporization is possible without passing the latent heat of evaporation if the critical temperature is applied. On the contrary, if the superheated gas under pressure above the critical pressure is cooled to be below the critical temperature, it will liquefy without condensation latent.

④ Supercooled state and phase change

A state in which a gas or liquid does not phase change below the saturation temperature is called a supercooled state. In this case, it is unstable and changes to a stable state when a little pressure or vibration is applied. If the gas is not liquefied below the boiling point after adiabatic expansion but in a supercooled gas state, when a slight micropressure is applied, the gas immediately changes to liquefaction when the temperature after compression is kept below the boiling point. easy to do.

⑤ Phase change and utilization of air

The theoretical logic of the present invention is to liquefy a certain gas and pressurize it above the critical pressure in the state where it is easy to liquefy during adiabatic expansion, and then supply heat quantity of air to vaporize above the critical temperature, and adiabatic expansion to obtain liquefaction again. It converts calories into work and at the same time produces a thermal effect.

The adiabatic expansion and liquefaction state is repeated repeatedly to reduce the liquefaction power by replenishing only the deficiency by the initial one liquefaction. It is a thermodynamic cycle that attempts to create work as the driving force of the car.

In order to construct such a thermal cycle, a gas having favorable conditions and reasonable conditions for the cycle configuration is required as follows.

(1) The threshold temperature should be much lower than the ambient temperature.

(2) The critical pressure should be relatively high.

(Should be able to increase the effect of expansion)

(3) The boiling point should be relatively high.

(4) It should be easy to liquefy (low latent heat of condensation).

(5) The specific gravity of the liquefied gas should be relatively large.

(6) The specific heat of liquefied gas should be high.

(7) The same cycle configuration should be achieved continuously using liquefied gas.

(8) There should be no adverse effect upon leakage.

(9) It must be easy to purchase.

(10) There should be no danger of explosion.

Nitrogen is most suitable for the above conditions, but air is to be replaced. (Critical temperature of air: -140 [℃], Critical pressure: 38 [kgf / cm ^ 2]

Boiling point at atmospheric pressure:-192 [℃])

⑥ Air liquefaction device and cycle

In the present invention, since the liquefied gas must be adiabaticly expanded after vaporization using a queue, a liquid air suitable for logic is required and a device for initial air liquefaction must be provided. The apparatus for air liquefaction includes adiabatic inflatable air liquefaction apparatus in the air liquefaction separation apparatus which is traditionally widely used and most commonly used. In this logic, in constructing a cycle using liquefied air, the air condition immediately before inflation is used in the same manner as the condition just before expansion in the inflator of the adiabatic inflatable air liquefaction device. It is configured to facilitate liquefaction after inflation and to generate power in the inflation process by making it have an advantageous condition, or to have favorable conditions, and to reduce the temperature of the air deprived of heat due to ultra low temperature even above the critical temperature of air. In addition, the first cycle of the liquid liquefaction to repeat the same cycle continuously to supply a large amount of heat of the air, the liquid air supplement compressor is made to reduce the power required for the air liquefaction by liquefying only the shortage.

2) composition

① Secure liquid air using the first air liquefaction device. (1) (2) (3)

(2) Pressurize the liquid air above the critical pressure with the pump (15-1, 16-1, 17-1, 18-1, 19-1 ...). As the critical temperature of air is much lower than the atmospheric temperature, it is possible to supply the queue or seawater heat even above the critical temperature so that it can be vaporized.

③ After supplying the pressurized liquid air to the queue or seawater heat (15-2, 16-2, 17-2, 18-2, 19-2 ...), increase the temperature. Control the supply of air or seawater to the same conditions as liquefaction may occur during inflation just before the inflator of the adiabatic expansion air liquefaction device (15-9, 16-9. 17-9, 18) -9, 19-9) to supply calories.

④ Obtain the expansion power by adiabatic expansion of the vaporized air in the expanders (15-3, 16-3, 17-3, 18-3, 19-3). ＜ The power generated by the adiabatic expansion of vaporized air is supplied by the amount of heat supplied to the air or seawater rather than the pump power to pressurize the liquid air.

⑤ The liquid part which is partially liquefied in the adiabatic expanded air is separated (15-4, 16-4, 17-4, 18-4, 19-4 ...) and the others are rapid expanders (15-6, 16-6, 17-6, 18-6, 19-15 ...) to swell up to the boiling point to obtain liquefaction.

<The expansion pressure of the rapid expander is set as low as possible within the range where no liquefaction occurs before the rapid expander, and there is no power generated in the rapid expander.

⑥ Exchange the unliquefied cryogenic supercooled air with the air before the rapid expander (15-5, 16-5, 17-5, 18-5, 19-5 ...).

⑦ Collect the liquefied air (15-7, 16-7, 17-7. 18-7. 19-7 ...) and repeat the same system.

⑧ Replenishing liquid air to replenish liquid air volume by unliquefied air (15-8, 16-8, 17-8, 18-8, 19-8 ...) (13) during the same system The compressor (6) and the expander (9) are separately installed and the compressor (6) suction air is uncondensed in a continuous system configuration, including uncondensed air (14) that discharges non-condensable gas from the expander (9) itself. It becomes atmosphere as much as replenishment amount of supercooled air, noncondensing gas which had become.

⑨ In each successive configuration, the outlet line of the liquid air pump is passed through the liquefied air supplement compressor (6) and the coolers (5, 5-1) (7) at the front and rear ends so that the intake air of the compressor (6) is kept at ultra low temperatures. To reduce the required power of the compressor (6).

Is done as

3) embodiment according to the principle.

Based on the configuration of the cycle, compressed air that receives heat from the air can be virtually set to any temperature (saturation temperature or less) that can be sufficiently liquefied after adiabatic expansion to the last pressure. For example, using an approximate thermodynamic equation The result is as follows.

○ Liquid air pump outlet pressure:

60 [KGf / cm ^ 2] (Over critical pressure, Critical pressure 38 kgf / cm ^ 2) ---------- P1

(Critical pressure above, critical pressure 38 kgf / cm ^ 2)

<Can be set equal to the initial pressure of the thermal insulation inflatable air liquefaction apparatus, and can be set higher to facilitate liquefaction. Above the critical pressure, even if the pressure is increased, the temperature drop rate decreases during adiabatic expansion, but a high pressure must be set to obtain a complete cryogenic temperature>

o Temperature of compressed air vaporized by receiving queue: -50 ℃ (223 ° K) ----------- T1

(Randomly set to a temperature that is easy to liquefy during expansion in a rapid expander)

<Liquid air is quenched because the actual temperature is about -30 to 40 ° C and the critical temperature of air is -140 ° C.

o Specific weight of liquid air: 1000 KGf / m ^ 3 (specific gravity of liquid air is about 1) --------- T

o Specific heat ratio of air: 1.4 (static specific heat / static specific heat) ---------------------- k

o Liquid air supply flow rate (optional): 13 [KGf / sec] ------------- Q

(Based on air of 10 m ^ 3 at atmospheric pressure)

o Insulation after pressure (standard atmospheric pressure): 1.03 [KGf / cm ^ 2] ------------ P2

o Air temperature after expansion: T 1 ( P 1 / P 2) ^{((1-k) / k)} =-203 ℃ (70 ° K) ------------- T2

(As the boiling point of air is -192 ℃ under standard atmospheric pressure, it is mostly moist and liquefied)

o Expansion pressure before rapid expander: 4 [KGf / cm ^ 2] (optional setting) -------- P '

o Expansion temperature before rapid inflator

T 1 ( P 1 / P ') ^{((1-k) / k)} =-170 ° C (103 ° K) ----------- T'

(The air saturation temperature at 4 KGf / cm ^ 2 is about 90 ° K, so no liquefaction occurs before the rapid expander.)

o Specific atmospheric standard air specific weight: 1.3 [KGf / m ^ 3] --------------

o Gas constant in air: 29.27 [KGf. m / KG ° K] ------------------ R

o Volume of compressed air just before expansion: Q RT1 / P1 = 0.14 [m ^ 3 / sec] ----------- V1

o Air volume before rapid expansion: (( P 1 V 1 ^k ) / P ') ^{(1 / k)} = 0.98 [m ^ 3 / sec] ------ V2

o Power requirement for liquid air pump: P1 Q / γ / 102 = 76 [KW] ------------ A

o Expansion force until rapid expansion:

( P 1 V 1- P ' V 2) / (k-1) / 102 = 1120 [KW] ------------ B

(The generated power in the rapid expander is ignored.)

o Possible power in one system configuration:

Assuming 60% liquefied air pump efficiency and 40% expansion turbine efficiency, the power that can be generated in one block system is

(A * 0.4)-(B / 0.6) = 321 [KW] -------------- C

(If the liquefaction rate of the air is low, the set pressure of the rapid expander can be lowered. Therefore, the increase in the expansion power increases the power that can be generated in one system configuration and the total number of repeatable systems is reduced.) Multiple pumps are feed water pumps of the next configuration of the same system in series.)

o Power requirement for liquid air replacement compressor:

Most of the air is liquefied after adiabatic expansion and must be liquefied to compensate for the deficiency in systems that continue to be repeated.

(Assuming that the leak rate and uncondensed amount of air is 20% in one system configuration, the total system can be configured five times. In the liquid air refill device, the liquefaction power required to make up 20% of the deficiency in each configuration is required. The amount of air liquefaction power required for a system configuration is required, and the amount of uncondensation of the device itself is included. Approximately 120% of the system configuration must be liquefied.)

<In general, in the adiabatic expansion air liquefaction apparatus, the amount of unliquefied, including the loss rate in the air separation apparatus, is about 15%.>

Therefore, the liquid air replenishment air compressor power requirement (D)

Ambient temperature: 15 ℃ -------------- t1

Air mean static specific heat rate: 0.24 kcal / kgf ℃ --c1

Liquid air specific heat: 1.1 kcal / kfg ℃ --------- c2

-Liquid Air Temperature:-192 ℃ ------------- ty

Standard atmospheric pressure: 10332 [KGf / m ^ 2] ---------- p1

Compression pressure: 20000 [KGf / m ^ 2] (optional)-p2

(The compressor suction air is compressed after exchanging with the cryogenic liquid air and then cooled again as liquid air, and then liquefied after expansion by adiabatic expansion, so low pressure setting is possible.

-Weight of liquid air supplied to one system:

13 [KGf / sec] ------------ Q

Unliquefied rate in one system:

20% (arbitrary setting) = 0.2 --------- α

Number of consecutive configurable systems:

1 / α = 5 ------------ N

Unliquefied air weight: QαN = Q

Non-condensable gas emissions

5% of uncondensed liquid air weight (optional)

= Q * 0.05 = 0.65 [KGf / sec] ------ β

= Weight of air to be replenished in air

Unliquefied rate in the liquid air refill device itself:

20% (arbitrary setting) = 0.2 --------- λ

Compressor Supply Air Weight:

Q + Qλ + β = 16.25 [KGf / sec] --------- G1

(Approximately calculated values are obtained since 20% of the device's own non-condensing amount is circulated, which leads to the calculation result that the amount of intake air continues

Weight of unliquefied air entering the compressor inlet:

G1- β = 15.6 [KGf / sec] --------- δ

Unliquefied air temperature entering the front of the compressor suction air heat exchanger:

-150 ℃ ------------------ t2

(The temperature of unliquefied subcooled air after thermal expansion is -192 ℃ and heat exchange with air of -164 ℃ before rapid expansion. At 20% unliquefied rate, the thermal equilibrium temperature is -168 ℃. Further lowers the temperature.

Randomly set to -150 ℃ considering temperature rise during transfer)

Compressor suction air heat exchanger shear temperature:

(Mixed thermal equilibrium temperature between freshly introduced air and unliquefied air)

(ωt1 + δt2) / (ω + δ) = -143 ° C ---------- t3

(The static pressure specific heat generally increases as the temperature drops, so the thermal equilibrium temperature goes down, but the average static specific heat is taken into account.)

-Condensed liquid air weight after adiabatic expansion of one system: Q (1-α)

= 10.4 [KGf // sec] ----------- G2

Compressor front end heat exchanger back end temperature:

(Air temperature after heat exchange with liquid air) The thermal equilibrium temperature of supply air and liquid air is (G1 c1 t3 + G2 c2 ty)

/ (G1 c1 + G2 c2) = -179 ° C ------ ta

Therefore, the maximum amount of heat that can be delivered

G1 c1 (t3-ta) = 141 [kcal / sec] --- Qa

Assuming a heat transfer efficiency of 70%, the air temperature after heat exchange is

(G1 c1 t3- (Qa * 0.7)) / (G1 c1)

=-168 ℃ --------------- t4

-Compressor front end and second heat exchanger end temperature:

(Compressor suction air temperature)

calculated using the same method and condition as t4

= -181 ℃ ------------- t5

Compressor suction air volume:

G1 R (t5 + 273) / p1

= 4.24 [m ^ 3 / sec] ------------- v1

Temperature after compression:

(( t 5 + 273) ( p 1 / p 2) ^{((1-k) / k} ) -273

= -160 ℃ ------------------------- t6

(Typically, when compressing and cooling at the same time, the polytrope constant is calculated as 1.3, but there is no compression cooling.

Air volume after compression: G1 R (t6 + 273) / p2

= 2.7 [m ^ 3 / sec] ------------- v2

Compressor Rear Heat Exchanger Rear Temperature:

calculated using the same method and condition as t4

= -177 ℃ -------------- t7

The temperature after expansion in the liquid air replenishment expander

(( t 7 + 273) ( p 2 / p 1) ^{((1-k) / k} ) -273

= -194 ℃ <liquefied after expansion> -------------- t8

Compressor Power:

k ( p 1 v 1- p 2 v 2) / (k-1) / 102

= -338 [KW]

Assuming 40% compressor efficiency

338 / 0.4 = 845 [KW] of power is required.

-------------------------------------------------- ------------- D

O Auxiliary power required for the transfer of heat supply:

If seawater is used, the power required for transportation is -192 ℃ of cryogenic liquid air, which is vaporized by receiving the heat of seawater and becomes -50 ℃ of compressed air.

It is assumed that the maximum amount of heat supplied is negligible after the heat exchange in the liquid air replenishment compressor is ignored.

[Liquid Air Weight * Liquid Air Specific Heat * (192-140)]

+ [Evaporated air weight * Air static specific heat * (140-50)]

= [13 * 1.1 * (192-140)] + [13 * 0.24 * (140-50)]

= 1024 [Kcal / sec]

Assuming that the temperature drop of seawater is 10 ℃ after heat transfer, the required seawater transfer rate is 1024/10 (specific heat of seawater 1) = 102 [Kgf / sec]

If the outlet pressure of the transfer pump is 2 [KGf / cm ^ 2], the pumping efficiency of 60% is the required power for the transfer in one system configuration.

(102/1000) * (20000/102) / 0.6 = 33 [KW] -------------- E

(When the liquefaction rate of air is low, the amount of heat transfer decreases.)

o Power available in the overall system configuration: C N-D-E N = 625 [KW]

<Therefore, only 13 [KGf / sec] of liquid air consumes the heat of seawater, so it is possible to generate 625 [KW] of power. When working in continuous operation, seawater and air temperature are reduced by the amount of heat supplied accordingly. Can bring effect.

The formula applied assumes minimum efficiency in a general apparatus and is calculated to be as unfavorable as possible.

If the air liquefaction rate is increased, the number of successive systems can be increased continuously, and the power that can be generated becomes very large and a lot of energy can be obtained from the atmosphere. On the basis of the applied formula and efficiency, when the unliquefied air rate is 39% and the set pressure of the rapid expander is set to 20000 [KGf / m ^ 2], the generated power of the system and the required power in the liquefied air replenishment body are equal, Becomes impossible.>

If the cycle consists of only one system block without the expansion and condensation of the continuous system using liquid air, and the entire power required by the air liquefaction replenishment device is required, the cycle cannot be constructed. The heat of combustion of the fuel will increase, and the effect of reducing the temperature of the atmosphere will also be impossible.

Therefore, until now, due to the increase of air liquefaction power, it is impossible to construct a system, and it is impossible to calculate a theoretical formula that can bring about the effect of reducing the temperature of the atmosphere as well as the actual case. In addition, there have been attempts to generate the temperature and power of the atmosphere using a refrigerant, but this was theoretically impossible. However, by repeating the same cycle continuously and using low temperature air and liquid air, the power required in the liquefied air replenishment device can be greatly reduced, thus enabling the construction of the system. If in the configuration of a heat cycle engine using a queue like this paper using the heat of the atmosphere, the power available in extreme cases may be excessive due to excessive friction of equipment or excessive heat loss due to poor insulation (using vacuum insulation method). If it is difficult to generate a cycle, a small amount of fuel required for operation can be further combusted to form a cycle. In this case the loss of the cycle is the heat energy lost in the heat of the atmosphere together with the work energy generated in the expander. At this time, the external power is applied to the calorific value of fossil fuel, but most of the calorific value is converted to work energy, and the remaining calories are released to the atmosphere. The effect of increasing the temperature of the atmosphere due to the combustion of the fuel is inevitably small, and the amount of thermal heat of the atmosphere due to the operation of the system cycle is much larger.

Therefore, if the system is in a state of lowest efficiency, even if it is impossible to generate power by using the heat of the atmosphere, the effect of reducing the temperature of the air can be sufficiently brought about. Therefore, the second law of thermodynamics, which states that it is impossible to lower the temperature of a high temperature heat source without a low temperature heat source and that conversion to work energy using only a high temperature heat source may not be possible in some cases.

This is thought to be an empirical law premised on the impossibility of liquefaction of permanent gas (boiling point at atmospheric pressure-below 150 ℃) in the time when thermal phenomenon at the ultra low temperature could not be handled.

Power generation using the atmosphere or seawater heat and the effect of temperature reduction of the atmosphere.

1 is a schematic diagram of an adiabatic inflatable air liquefaction apparatus

2 is a system configuration diagram of a heat engine using a queue

<Description of the code | symbol about the principal part of drawing>

DESCRIPTION OF SYMBOLS 1 Air purifier 2 First liquid air generator 3 Liquid air storage tank

4: Liquid air supply line 5, 5-1: Compressor suction air heat exchanger

6: liquid air supplemental compressor 7: compressor after-air heat exchanger

8 non-condensed air heat exchanger 9 liquid air replenishment inflator

10, 10-1: liquid air recovery plurality device 11: liquid air supplement pump

12: Last multiple pump outlet Line 13: Liquid air regeneration line

14: non-condensing gas discharge valve

15-1, 16-1, 17-1, 18-1, 19-1 ...: Liquid air return pump

15-2, 16-2, 17-2, 18-2, 19-2 ...: Atmospheric or seawater heat exchanger

15-3, 16-3, 17-3, 18-3, 19-3 ...: expansion turbine

15-4, 16-4, 17-4, 18-4, 19-4 ...: Expansion liquid air condenser

15-5, 16-5, 17-5, 18-5, 19-5 ...: Rapid expansion uncondensed air heat exchanger

15-6, 16-6, 17-6, 18-6, 19-6 ...

15-7, 16-7, 17-7. 18-7. 19-7 ...: Rapidly expanding liquid air condenser

15-8, 16-8, 17-8, 18-8, 19-8 ...: Uncondensed air line

15-9, 16-9. 17-9, 18-9, 19-9 ...: Atmosphere or Seawater Heat Calorimeter

15-10, 16-10, 17-10, 18-10 ...: High Pressure Liquid Air Return Pump

<Brief Description of Drawings>

The drawings are the main configuration of the heat engine configuration method using the queue. The drawings are for the purpose of illustrating the system and each device is in accordance with the general device concept.

In order to increase efficiency for each device, it is configured so that the heat insulation or heat dissipation can be effective depending on the application. Each device may be configured differently from the drawings without departing from the principle and system according to the concept of the configuration and combination of the general devices.

The flow of compressed air and liquefied air is the same as the progress of the arrow in the figure.

Symbols 15-1 to 15-10 are important diagrams of the heat engine configuration method using queues, and become a system block. Blocks in the same system are 16-1 to 16-10, 17-1 to 17-10. Repeat steps 18-1 to 18-10, depending on the use and replenishment of liquid air.

The system is a combination of essential components such as expanders, heat exchangers, condensers, compressors, pumps, and the like. Listed.

Claims (1)

A heat engine using a queue based on the principle of an adiabatic expansion air liquefaction device.