JPS63285273A - Liquid pneumatic power generating method - Google Patents

Abstract

PURPOSE:To improve the extent of energy conversion efficiency by letting supply heat out of an external heat source pass through an open type gas turbine cycle, a closed type gas turbine cycle and an auxiliary closed type gas turbine cycle. CONSTITUTION:A heat exchanger cycle is formed by a liquid air pump P, isothermal compressors C3-C1 for thermal recovery, isothermal expanders SE, ME and heat exchangers HEit-3, HEit-2 and HEit-1. With this formation, compressive heat energy of cold air is absorbed by an open type gas turbine cycle, making isothermal compression possible to be done. And, it is subjected to isothermal expansion with both closed type and auxiliary closed type gas turbine cycles. With this constitution, supply heat out of an external heat source is efficiently convertible into energy.

Description

DETAILED DESCRIPTION OF THE INVENTION ((Industrial Application Field)) The present invention is based on a jointly filed invention "liquid air manufacturing method" (hereinafter referred to as "jointly filed invention") of the applicant, which is closely related to the present invention. According to the method described, a heat engine is operated using the produced and stored liquid air at the expense of a large amount of power (electricity) to maximize the amount of heat supplied from an external heat source into useful mechanical work. This article relates to a converting power generation method.

((Prior Art)) In recent years, in Japan, with the active construction of high-efficiency large-capacity power plants, there is an urgent need to quickly establish an optimal storage and regeneration method for late-night electricity when demand for electricity is drastically reduced. There is.

However, in the past, the general methods devised for power storage and regeneration were to first convert and store power into mechanical, scientific, physical energy, etc., and then convert the stored energy itself into mechanical work as needed. The only type of system that has been put into practical use for storing and regenerating large-capacity power (electricity) is the typical pump-turbine system, which is limited to application to small-capacity power. do not have. This method converts and stores electrical energy into water potential energy during the pump stroke, and converts the potential energy itself into mechanical work during the water wheel stroke.

((Problem that the invention seeks to solve)) However,
In the conventional pump-turbine system that stores and regenerates large-capacity electric power as described above, a comprehensive evaluation including the power generation source of the power plant will be deferred to the section ((Effects of the invention)) below. Even assuming that the exchange efficiency of the round trip process of electric energy, storage medium (water) and potential energy is 85%, only 72% of the power consumption is recovered during regeneration. In reality, if we take into account the electrical, mechanical, and hydraulic losses of various devices during round-trip conversion, it is expected that this value will be considerably lower, and this type of power storage and regeneration method will be extremely unproductive. I have to say that it is accurate. Nevertheless, since other high-performance methods suitable for large-capacity power have not yet been developed, the present method still has no choice but to be adopted. No matter how much you improve the efficiency of equipment and reduce various losses, as long as you rely on the old method of converting the physical energy of the storage medium itself into power, you will not be able to regain the power consumed. It is impossible in principle, and it can be said that it is fateful.

The present invention attempts to solve these conventional problems from a completely new perspective, and aims to generate power that greatly exceeds the power consumed during power storage from the amount of heat supplied to the power regenerative heat engine. The object of the present invention is to provide an excellent method for generating liquid air power that can be extracted extremely efficiently.

<<Means for Solving the Problem>> In order to achieve the above object, the present invention provides high temperature An open gas turbine cycle in which liquid air itself is used as a working substance in the interval between P20 and atmospheric pressure P■, normal temperature T0 (lower/higher heat source temperature), lower temperature T3 (T0>T3>T00), and given pressure P10 (P20>P10>P0) and atmospheric pressure P■. Applied pressure■0(P
In a hybrid cycle that combines an auxiliary closed gas turbine cycle using circulating air as a working material in the section of 10■0>P0) and atmospheric pressure P0, a. The open cycle consists of adiabatic compression (P
0→P20), constant pressure expansion (P=P20), isothermal expansion (P
20→P0), constant pressure compression (P=P0), and exhaust into the atmosphere.
The liquid main air supplied in the state of 0 has a given high pressure P20
In the constant pressure expansion stroke after being adiabatically compressed to The air is evaporated and heated to reach the room temperature T0, and then is heated to a high temperature ■0 while recovering exhaust heat through countercurrent heat exchange with the exhaust air, becoming high-temperature, high-pressure air, and b. The high-temperature, high-pressure air that has reached the state of high temperature ■0 and pressure P20 undergoes isothermal expansion to atmospheric pressure P0 while receiving expansion heat energy from the upper high-temperature heat source in the isothermal expansion stroke of the subsequent open cycle, In the next constant-pressure compression stroke, the air is cooled while expelling waste heat through countercurrent heat exchange with the high-pressure air that is expanding at constant pressure from room temperature T0 to high temperature ■0, and is discharged into the atmosphere at room temperature T0 and pressure P0. C. A closed cycle is a constant pressure compression of circulating air (P=P
0)・Isothermal compression (P0→P10)・Constant pressure expansion (P=P1
0)・Isothermal expansion (P10=P0), etc. In the isothermal compression process from atmospheric pressure P0 at low temperature to a given pressure P10, the compression heat energy added to the circulating air is The total cooling heat of the liquid air expanded at constant pressure in the cycle and a part of the cold heat of the circulating air itself are absorbed, and the cooling of the circulating air is achieved by countercurrent heat exchange between the constant pressure compression and constant pressure expansion strokes of the cycle. Heating proceeds at the same time, d. In the isothermal expansion process of the closed cycle from normal temperature T0 and pressure P10 to atmospheric pressure P0, expansion heat energy is supplied to the circulating air from a low-temperature, high-temperature heat source below normal temperature T0, e. The auxiliary closed cycle uses constant pressure compression of circulating air (P=P
0)・Adiabatic compression (P0→P0)・Isothermal expansion (P0→P0
), etc. In the constant pressure compression stroke, the circulating air is cooled by countercurrent heat exchange with the constant pressure expanded air of the open type and closed type cycles, and from the state of normal temperature T0 and pressure ■0 In the isothermal expansion process leading to atmospheric pressure P0, expansion heat energy is supplied to the circulating air from a high temperature heat source below room temperature T0, and this cycle proceeds roughly in the order of the above steps, T-
■On the (temperature-entropy) diagram, open type, closed type,
All of the auxiliary closed cycles have a unique cycle structure so that the working substance (air) flows clockwise, in the same direction as the clock rotates.

<<Operation>> As described above, the present invention does not convert the thermal energy of liquid air stored at atmospheric pressure itself into power, but instead converts the thermal property of liquid air, which is cold, and the physical property, which is non-conductive. Utilizing its compressibility, a heat engine is operated using liquid air itself as a working substance, receiving paid (fuel combustion) and free (normal temperature) thermal energy from external upper and lower high-temperature heat sources. It converts work into mechanical work extremely efficiently.

That is, first, by utilizing the incompressibility of liquid air, the high-pressure adiabatic compression work of open cycle liquid air is drastically reduced.
Furthermore, as a means of utilizing low-temperature heat sources, the compressed heat energy of atmospheric pressure low-temperature air is absorbed by the cold energy of open cycle high-pressure liquid air at a temperature close to the cryogenic temperature T00.
Closed cycle at low temperature Enables isothermal compression of atmospheric pressure low temperature air to reduce compression work, while at room temperature (lower and lower temperature)
Under high-temperature heat sources), the closed type, auxiliary closed-circuit cycle generates expansion work through isothermal expansion of compressed air while receiving free heat supply, and under high temperatures (upper/high-temperature heat sources), it generates expansion work while receiving free heat supply. The synergistic effect of these actions, such as the isothermal expansion of open cycle highly compressed air that progresses while receiving heat, produces large expansion work, making it possible to maximize the amount of paid and unpaid heat supplied from the upper and lower high temperature heat sources. It is a conversion to mechanical work.

<<Example>> FIG. 1 is a T-■ diagram of a hybrid cycle in which air is used as a working substance and an open type gas turbine cycle is combined with a closed type and an auxiliary closed type gas turbine cycle. FIG. 2 shows the equipment configuration of this cycle, and the numbers attached to each circuit correspond to the numbers of each state in FIG.

Ve is liquid main air storage tank, P is liquid main air pump, C3, 2,
1 is an isothermal compressor for cold heat recovery, C'1 is an auxiliary adiabatic compressor, SE is an isothermal compressor that operates at room temperature, E'1 is also an auxiliary isothermal compressor, ME is an isothermal compressor that operates at high temperature, SH is a room temperature heating machine, H'1 is also an auxiliary superheater,
MH is a high-temperature heater, HEit-1, HEit-2, and HEit-3 are heat exchangers that absorb the heat discharged from the isothermal compressor with cold heat, HE'cf-1 is also an auxiliary countercurrent heat exchanger, and M
HEcf is a countercurrent heat exchanger for exhaust heat recovery, and MG is a drive motor/generator.

In the open cycle 0-20'-20-■■-0 of FIG. 1, first consider the recovery of cold energy from liquid main air at a temperature close to the cryogenic temperature T00. The liquid air G0 supplied from the liquid air storage tank Ve is adiabatically compressed from state 2 of temperature T00 and pressure P0 to state 20' of pressure P20 by the liquid air pump P, and enters the heat exchanger HEit-3. On the other hand, temperature section T0
■ In a closed cycle 0-3-13-10-0 that operates in T3 and pressure section P0 ■ P10, circulating air G3 is moved from state 3 of temperature T3 and pressure P0 to state of pressure P0 along isothermal line 3-13. The amount of heat Q3 discharged during isothermal compression to 13 is absorbed by the aforementioned air G0 in the heat exchanger HEit-3, and the air G0 is heated along the isobar line 20-23 to reach the state 23 of temperature T3 (Q3 =Q'20
). Next, the above-mentioned circulating air G3, which is isobarically cooled from state 2 of temperature T2 and pressure P0 to state 3, is
By part ■3 of the circulating air G3 to be heated isobarically from state 13 to state 12 at temperature T2 along
+■G3), heat quantity ■23 in heat exchanger HEcf-3
is taken away (P23=Q13). Air G in state 23
0 and the part of air remaining in state 13 ■G3 is in the temperature range T0
■ Circulating air G2 of the closed cycle 0-2-12-10-0 operating in T2 and pressure section P0 ■ P10 is the isothermal line 2
The heat Q2 discharged when being isothermally compressed from state 2 to state 12 along -12 is received in heat exchanger HEit-2, and air G0 is isobarically heated to state 22 along isobar line 23-22. ■G3 is isobar line 13-1
2 to state 12 (Q2=Q23
+■Q13). Next, the air (G3+
G2) changes from state 12 to state 1 with temperature T1 and pressure P10.
The heat amount ■12 is taken away in the heat exchanger HEcf-2 by the air G3 heated along the isobars 12-11 to 1 and the part ■2 of G2 (G2=■2+■G2) (P
12=■12). The air G0 in state 22 and the air G2 remaining in state 12 are in a closed cycle 0-1-11 that operates in temperature range T0 *T1 and pressure range P0 *P10.
-10-0 circulating air G1 is isothermally compressed from state 1 to state 11 along the isobar line 1-11, and the heat exchanger HEit-1 receives the amount of heat Q12, and as a result, G0 and ■G2 are isobar lines 22-21, respectively;
12-11 and reaches state 21, 11 (
Q1=Q22+■Q12). Next, air (G3+G2+G1) is cooled from atmospheric state 0 at temperature T0 and pressure P2 to state 1 along the isobar line 0-1, from state 11 to temperature t.
By the air (G3 + G2) heated along the isobar line 11-10 and the part of G1 ■1 (G1 = ■1 + ■G1) to the state 10 of 0・pressure P10, the heat exchanger HEcf-1
The amount of heat ■01 is taken away at (P01=■11). Finally, the air G0 in state 21 and the part of the air G1 remaining in state 11 have a temperature zone T0■T1 and a pressure zone P0■■
In the auxiliary closed cycle 0-1-1-0 operating at 0, an amount of heat Q01 is transferred in the auxiliary heat exchanger HEcf-1 from the circulating air G1 cooled from state 0 to 1 along the isobars 0-1, G0 and ■G1 are each equal pressure line 2
Heated along 1-20, 11-10 to state 20, 1
It reaches 0 (Q01=Q21+■Q11). Air G1 in state 1 is adiabatically compressed along the isentropic line 1-0 and reaches state 0 at temperature T0 and pressure P0. In this way, the circulating air (G3+G2+G1) that has finally gathered in state 10 and the circulating air G1 that has reached state 0 are placed in the room temperature heater S.
It receives heat quantities Q10 and Q0 from room temperature water (lower/high temperature heat source) through H and auxiliary heater H1', performs isophonic expansion along isothermal lines 10-0 and 0-0, and returns to atmospheric state 0. The cold recovery of the liquid main air G0 is completed.

In the open cycle, all the cold energy is recovered and the state is 20.
The high pressure air G0 in the heat exchanger MHEcf is
Countercurrent heat exchange is performed with the exhaust air G0 (described later) which is in a state of 0 at a pressure P0 after completing iso-sonic expansion along the isothermal line 20-0,
The exhaust air G0 is cooled by removing the amount of heat Q0 along the isobar line 0-0, while the air G0 in state 20 is cooled along the isobar line 20-2.
Receives heat amount Q20 along 0, temperature T0, pressure P20
is heated to state 20 (Q20=Q0). condition 20
The air G0 that entered the iso-sonic expander ME is supplied with heat Q20 from the upper high-temperature heat source via the heater MH, and continues iso-sonic expansion along the isotherm line 20-0, reaching state 0. The exhaust air becomes G0, and the state 0 follows the process described above.
is discharged into the atmosphere, completing the hybrid cycle.

Here, the following analytical example proves that the cycle of the present invention is thermodynamically established without any problem.

Now consider the steady operating state in Figure 1, and the preconditions are P0 = 1kg/cm2, P10 = 20kg/cm2, P
20=200kg/cm2T0=300°K=27℃,
T0=773°K=500°CT1=240°K, T2=
Given 180°K, T3 = 120°K, from the psychrometric diagram of m-crawling Zen and Tanishita, where T≦300°K) P=P0:i0
=122.2l/kg, i1=107.5, i2=93
．． 1i3=78.6, i0'=22.7 s0=0.900kcal/Kkg, s1=0.828
, s2=0.787s2=0.683 P=P10:i10=121.2,i11=106.2
, i12=90.0, i13=70.6s10=0.7
00, s11=0.646, s12=0.572, s1
3=0.442P=P20:i20=113.3,i2
1=93.3, i22=70.0, i23=41.7i
20' = 26.4 (From the psychrometric diagram of Tanishita, however, T≧300°K) P = P
0:i0=37.8,i0=165.1P=P20:i
20=37.8, i0=165.1, s0-s10=0
．． 34896 is obtained. Furthermore, from states 1 to 11, when 1 kg of air is compressed isotonically, the amount of heat q1 is discharged to the outside.
It is. Therefore, the work required for isophone compression l1-11
Hato becomes. Here, A is the reciprocal of the work equivalent of heat. Similarly, q20-l2-12: Amount of heat and compression work released when 1 kg of air is isotonically compressed from states 2 to 12 q30-l3-13: Amount of heat released when 1 kg of air is isotonically compressed from states 3 to 13 and compression work q10-l10-0: Amount of heat and expansion work supplied when 1 kg of air expands isotonically from state 10 to 0 q00-l0-0: When 1 kg of air expands isotonically from state 0 to 0 Amount of heat supplied and work of expansion q20-l20-0: Assuming the amount of heat and expansion work supplied when 1 kg of air expands isotonically from state 20 to state 0, q2=38.700 and al2-12=35. 600
q3=28.920, al3-13=20.920
q10=60.000, al0-0=59.000q
0=21.600, al0-0=21.600q2
0=269.746, al20-0=271.146 are obtained.

Next, in the closed cycle 0-3-13-10-0, the relationship of heat exchange transfer Q3 = Q20', G3 x q3 = G0 x (i23-i20')∴G0 = 1k
g, we get G3=0.52905kg. Similarly, the relationship of heat exchange Q23=Q13, however, Q13=Q13+
■From Q13 G3×(i2-i3)=G3×(i12-i13)∴G
3=0.39542kg ∴■G3=G3-G3=0.13363kg.

In the closed cycle 0-2-12-10-0, the relationship of heat exchange Q2=Q23+■Q13 to G2×q2=G
0×(i22-i23)+■G3(i12-i13)∴
We obtain G2=0.79825kg ∴G3+G2=1.32729kg. Similarly, the relationship of heat exchange Q12 = Q12, Dashi Q12 = Q12 + ■ From Q12, (G3 + G2) x (i1 - i2) = (G3 + G2) x (
i11-i12) ∴G3+G2=0.88889kg ∴■G2=(G3+G2)-(G3+G2)=0.43
840 kg is obtained.

In the closed cycle 0-1-11-10-0, the relationship of heat exchange Q1=Q22+■Q12 to G1×p1=G
0×(i21-i22)+■G2×(i11-i22)
Obtain ∴G1=0.69602kg, ∴G3+G2+G1=2.02332kg. Similarly, the relationship of heat exchange Q01=Q11, dashi Q11=Q1
1+■Q11 to (G3+G2+G1)×(i0-i1)=(G3+G2
+G1)×(i10-i11)∴G3+G2+G1=1
．． 98285kg∴■G1=(G3+G2+G1)-(
G3+G2+G1)=0.04047kg is obtained.

Furthermore, in the auxiliary closed cycle 0-1-1-0, from the relationship of heat exchange Q01=Q21+■Q11, G1×(i
0-i1)=G2×(i20-i21)+■G1×(i
10-i11) ∴G3=1.40184kg is obtained.

From the above results, the supplied liquid main air G0 (=1 kg)
The amount of heat supplied from the low-temperature/high-temperature heat source at room temperature T0 is recovered as power by the amount of cooling energy of
If I, AL'I, then ALIII=AL(3)10-0-AL3-13=G3
×(Al10-0-Al3-13)=20.146kc
alALII=AL(2)10-0-AL2-12=G
2×(Al10-0-Al2-1)=18.679kc
alALI=AL(1)10-0-AL1-11=G1
×(Al10-0-Al1-11)=13.712kc
alAL'I=AL0-0-AL1-0=G1×(Al
0-0-(i0-i1))=9.673 kcal is obtained.

Furthermore, in the open cycle 0'-20'-20-0, the amount of heat Q2 supplied from the high temperature heat source above the high temperature T0
When calculating the recovered power ALM out of 0, ALM=AL
20-0-AL0'-20'=G0×(Al20-0-
(i'20-i'0))=267.446kcal, so the total generated power ΣAL of the cycle of the present invention is ΣAL=ALIII+ALII+ALI+AL'I+A
LM=329.656kcal. Therefore, 1
If kg of liquid air converts the amount of heat supplied from the upper and lower high temperature heat sources into effective mechanical work, that is, the non-generated power is written as Ale, then Ale = ΣAL / G0 = 329.65
It becomes 6kcal/kg. However, in this case, the amount of paid heat Q20 supplied from the upper high-temperature heat source due to fuel combustion
is Q20=G0×q20=267.7kcal.

Now, FIG. 1 shows a cycle that is mainly composed of ideal isothermal change processes and operates with air as the working substance. However, the isothermal change can be replaced by an adiabatic change. FIG. 3 shows a T--diagram of the hybrid cycle thus substituted and modified from FIG. FIG. 4 shows the equipment configuration of this cycle, and the numbers attached to each circuit correspond to the numbers of each state in FIG. Ve is a liquid air storage tank, P is a liquid air pump, C3, 2, and 1 are adiabatic compressors, respectively.
HPE, MPE, and LPE are high-pressure, medium-pressure, and low-pressure adiabatic expanders, respectively; SE is an auxiliary adiabatic expander; MG is a drive motor/generator; H3, 2, and 1 are high-pressure, medium-pressure, and low-pressure heaters, respectively; H4 is an auxiliary heater, HEcf-0 is a countercurrent heat exchanger for exhaust heat recovery, and HEcf-3, HEcf-2, and HEcf-1 are countercurrent heat exchangers for cold heat recovery.

Open type cycle 0'-3'-3-3-23-2 in Figure 3
-12-1-01-0, first, the liquid main air storage tank Ve
The liquid main air G0 supplied from is at a temperature T00 and an atmospheric pressure P0.
is adiabatically compressed by the liquid main air pump P and reaches the state 3' of high pressure P3, and immediately the heat exchanger HEcf
-3 (described later). On the other hand, a closed cycle 0-08-7-4-0 for cold recovery that operates in the pressure section P4←→P0
The circulating air G3 enters the above-mentioned heat exchanger HEcf-3 from the opposite direction, and enters the state 07 of temperature T07 and pressure P3.
From isobar line 07- to state 08 of temperature T08 and pressure P0
The amount of heat Q'08 is taken away along the line 08 and is cooled, and the air G receives the amount of heat Q'3 along the isobar line 3'-37 and reaches the state 37 where the temperature is T07 and the pressure is P3 (Q08=
Q'3). The circulating air G3 that has reached state 08 has a temperature T0
7. Adiabatic compression is performed by compressor C3 along isentropic line 08-7 up to state 7 at pressure P4. Also, pressure section P
4 ■ Closed cycle 0-07- similar to before operating at P0
The circulating air G2 of 6-4-0 and the circulator G3 have a temperature T
06・Heat exchanger HEcf- together in state 06 of pressure P0
2 and transfers the amount of heat Q07 to the air G0 in state 37 entering from the opposite direction and the circulating air G3 in state 7, and the isobar line 0
6-07, while air G0 in state 37 and air G3 in state 7 are cooled along isobars 37-36.7-6, respectively.
It receives heat amounts Q37 and Q9 along the line and is heated, reaching state 36 and 6 (Q09=Q37+Q7). Status 07
The circulating air G2 is adiabatically compressed by the compressor C2 along the isentropic line 07-6 to a state 6 of temperature T07 and pressure P4. Furthermore, the circulating air G of the same closed type cycle 0-06-5-4-0 before operating in the pressure section P4■P0
1 and the above-mentioned circulating air G3, G1 enter the heat exchanger HEcf-1 together in state 0 with temperature T0 and pressure P0, and air G0 in state 36 and circulating air G in state 6 enter from the opposite direction.
3, G2 is cooled along the isobar line 0-06 by transferring the amount of heat Q08, while the air G0 in state 36 and the circulating air G3, G2 in state 6 are cooled along the isobar line 36-3, 6-4, respectively.
It receives heat amounts Q36 and Q6 along the line and is heated, reaching states 3 and 4 (Q06=Q36+Q6). Circulating air G1 in state 06 is adiabatically compressed by compressor C1 along isentropic line 06-5 to state 5 at temperature T5 and pressure P4. Finally, the circulating air G3, G2 in state 4 and the circulating air G1 in state 5 are supplied with heat amount Q4 from the lower high temperature heat source in the auxiliary heater H4, and the isobars 4-4,
5-4, state 4 of temperature T4 and pressure P4
At the same time, it is guided by the auxiliary adiabatic expander SE and continues adiabatic expansion along the isentropic line 4-0, returns to the atmospheric state of 0 with temperature T0 and pressure P0, completes each closed cycle, and returns to the liquid level. Cooling and heat recovery of the air is converged.

On the other hand, the air G that has reached state 3 in the open cycle
After completing adiabatic expansion in state 01 of temperature T01 and pressure P0 in heat exchanger HEcf-3 for exhaust heat recovery (described later), air G0 in state 3 undergoes heat exchange with air G0 (described later). is heated by receiving the amount of heat Q3 along the isobar line 3-301, and the air G0 in state 01 is cooled by taking away the amount of heat Q0 along the isobar line 01-0, and becomes in the states 301 and 301, respectively.
reaches 0 (Q0=Q3). Air G0 in a state 301 with a temperature T301 and a pressure P3 is guided to a high-pressure heater H3, receives a supply of heat Q3 from an upper high-temperature heat source, and is heated along an isobar line 301-3 to a temperature T0 and a pressure P3. state 3 is reached.

Then, immediately adiabatic expansion is carried out along the isentropic line 3-23 in the isobaric expander HPE, and the state 23 of pressure P2 is reached.
leading to. Similarly, the air G0 in state 23 is heated along the isobar line 23-2 by receiving heat Q2 from the upper high temperature heat source in the intermediate pressure heater H2, and is heated at a temperature T0 and a pressure P.
Immediately after reaching the state 2 of 2, it is guided to the medium pressure expander MPE and performs adiabatic expansion from the pressure P2 to P1 along the isentropic line 2-12, and reaches the state 12. Finally state 12
In the low-pressure heater H1, the air G0 is heated along the isobar line 12-1 by receiving heat Q1 from the upper high-temperature heat source, and when it reaches state 1 of temperature T0 and pressure P1, it is immediately introduced to the low-pressure expander LPE. He performs adiabatic expansion from pressure P1 to P0 along isentropic line 1-01 and reaches state 01. The air G0 that has reached state 01 discharges the amount of heat Q■ in the heat exchanger HEcf-0 for exhaust heat recovery as described above, reaches state 0, is discharged into the atmosphere, and completes the entire cycle. finish.

Here, the following analytical example proves that the cycle of the present invention is thermodynamically established without any problem.

Now consider the steady operating state in Figure 3, and the preconditions are P0 = 1 kg/cm2, P1 = kg/cm2, P2 = 5.
0kg/cm2, P3=200kg/cm2P4=4k
g/cm2, T0=300°K=27°C, T06=20
8゜KT07=142゜K, T08=98゜K, T0=
Given 773°K = 500°C, and reading the enthalpy of each state from the Hausen and Tanishita psychrometric diagram (from the Hausen psychrometric diagram), P = P0: i0 = 122.2 kcal/kg, i06 =
99.8, i07=83.9 i08=73.
2, i0'=22.7P=P3:i3=113.3,i
36=80.7, i57=52.4 i3'=
26.4 P=P4:i5=123.6,i5=99.3,i7=
83.2 (from Tanishita's psychrometric diagram) P=P0:i01=72.9,i0=46.4P=P1
:i1=164.1,i12=95.3P=P2:i2
=164.1, i23=102.4P=P3:i3=1
65.1, i3=37.8P=P4:i4=80.0,
i5=50.0 is obtained.

In the closed cycle 0-08-7-4-0, the relationship of heat transfer and reception is Q0■=Q■', so G3×(i07-i08)=G3×(i39-i■')
∴If G0=1kg, G3=2.42990kg, closed cycle Q07=Q37+Q7 (G3+G2)
×(i06-i07)=G0×(i38-i37)+G
3×(i8-i7) ∴G3+G2=4.24
035 kg, closed cycle 0-06-5-4-0, the relationship of heat exchange Q06 = Q3■ + Q■ (G3 + G2 + G1) × (i0-i06) = G■ × (i
3-i36) +(G3
+G2)×(i1-i5) ∴G3+G2+G
1=5.80928kg etc. are obtained. From these results, G1=1.56894, G2=18.1044, G3=
2.42990 is found.

Furthermore, open type cycle 0'-3'-3-...-1-01
−0, the relationship between heat transfer and reception for exhaust heat recovery Q0=
Q3, but from T01≧T301 G0×(i301-i3)=G0×(i01
-i0) ∴i301=i01-i■+i3=6
We get 4.3.

Therefore, states 08 to 7, 07 to 6, 0
The work of adiabatic compression of air from 6 to 5 is L06-, respectively.
7, L07-8, L08-5, If the adiabatic compression work of liquid air from state 0' to 3' is L0'-3', then AL0
8-7=G3×(i7-i08)=24.299kca
lAL07-8=G2×(i8-i07)=27.88
1kcalAL08-5=G1×(i5-i06)=3
7.341kcalAL0'3'=G0×(i3'-i
0') = 3.700 kcal Total adiabatic compression work = 93.921 kcal is obtained. Also, from state 3 to 23, from 2 to 12, from 1 to 01,
The work of adiabatic expansion of air from 4 to 0 is L3-2, respectively.
3, L2-12, L1-01, L4-0, then AL3
-23=G0×(i5-i23)=62.700kca
lAL2-12=G0×(i2-i12)=68.80
0kcalAL1-01=G0×(i1-i01)=9
1.200kcalAL4-0=(G1+G2+G3)
×(i4-i0)
= 195.192 kcal Total adiabatic expansion work = 417.892 kcal is obtained. Therefore, the total generated power ΣAL in the cycle of the present invention is ΣAL = total adiabatic expansion work - total adiabatic compression work = 32
It becomes 3.971kcal. Thus, the specific generated power Al■ is Al■ = ΣAL/G0 = 323.971kcal/kg
becomes. However, in this case, if the total amount of paid heat supplied by the fuel of the upper and lower high temperature heat sources is written as ΣQ, then ΣQ=Q3+Q2+Q1+Q■1 =G0×{(i1-i301)+(i2-i23)
+(i1-i12)}+{(G3+G2)×(i
4-i4) +G1×(i4-i5)} =231.300+189.544=420.84
It is 4kcal.

((Effects of the invention)) In order to more clearly evaluate the effects of the present invention, it is necessary to go back to the thermal power plant, which is the original source of electricity, and start with the thermal power generation equipment, power storage equipment, and power regeneration equipment. It is necessary to devise an overall system that includes the above, and consider what percentage of the total amount of paid heat generated by combustion of fuel supplied to the entire system can be ultimately converted into useful electricity.

Therefore, this section will introduce the so-called "thermal power plant/pump/water turbine system" (hereinafter referred to as "PT system"), which is directly connected to a thermal power generation system and introduces a representative pump-turbine system as a large power storage and regeneration method, and the thermal power generation system. ``Thermal power plant/air liquefaction engine/liquid air engine system'' (hereinafter referred to as the ``LA system''), which is directly connected to the series and jointly introduces the parallel invention, air liquefaction power storage system, and the claimed invention, liquid air power regeneration system. )
will be compared and studied based on the above analysis results.

Figure 5 shows a conceptual diagram of the PT system, where PS is the thermal power plant, ■ is its generating efficiency, P is the pump, ■ P is the pump efficiency, WT is the water turbine, ■ T is the efficiency of the water turbine, G is the generator, KPS
indicates the pump rotating shaft connection/release device on the input side, KT indicates the water turbine rotation shaft connection/release device on the output side, and VI and II represent the water flow shutoff and release valves, respectively.The operations of KPS, KT, VI, and II are as follows: 1) During power storage: (KPS connection/VI open)
+ (KT open/VII closed) (2)
During power regeneration: (KPS open/VI closed)
Switching is performed according to purpose, such as + (KT connection/VII release).

Figure 6 shows a conceptual diagram of the LA system, where PS is a thermal power plant, ■ is its generating efficiency, EGI is a co-private invention/air liquefaction engine, GII is the main generator, and KPS is the engine rotation shaft connection on the input side. The openers, KI and II respectively represent the auxiliary connection/opener and the main connection/opener of the engine rotating shaft on the output side, VI and II respectively represent the liquid main air amount closing/opening valves, and KPS, K
The operations of I, II, VI, and II are as follows: (1) When storing electricity: (
KPS connection/KI release/VI release)
+ (KII open/VII closed) (2) During power regeneration: (KPS open/KI open/VI closed)
+ (KII connection/VII release) (3) Power generation: (KPS release/KI connection/VI release)
Switching is performed according to purpose, such as always + (KII connected/VII opened), but the feature of this system is that power is always generated in operation (3) (described later).

Now, the effective generated power Leff and Leff are respectively P
In the T system and LA system, it is defined as the power that is finally taken out to the outside of the system as active power, and the active power conversion rate ■■ and ■■ are respectively PT
In the system and LA system, if it is defined as the ratio of the effective generated power to the amount of paid heat supplied from the high-temperature heat source through fuel combustion, then [A] For the PT system, Leff=Q×η×ηP×ηT η*=Leff/Q= η×ηP×ηT [B] For LA system, Leff=Ale, but when Alc>0, Leff
=Ale+(-Alc), however, when Alc<0 (Note) Alc is the specific power consumption (electric power), and in the joint invention, the air liquefaction engine EGI is the required power to produce 1 kg of liquid air. (electricity).

(i) When Alc > 0, Q(q) = Alc/η, so (ii) When Alc <, Q(q) = 0, so we obtain, and [A] In the PT system, the power generation of a thermal power plant End efficiency η = 40%, pump efficiency ηP = 85%, water turbine efficiency ηT =
Assuming 85%, the difference between (1) power storage and (
2) If power regeneration is continued, η*=0.4×0.8
5×0.85=0.289 [B] In the LA system, (1) When the analysis example of the present invention in Figure 1 and the analysis example of the concurrent invention in Figure 1 are introduced in conjunction, Ale = 329.656, Alc = -58. 327<0
Since Q20=q20=267.7, this corresponds to (3) in FIG. 6 when power is always generated. (2) When the analysis example of the claimed invention in FIG. 3 and the analysis example of the concurrent invention in FIG. 7 are introduced in conjunction, Ale= 323.971, Alc=-113.239<
Since 0ΣQ=Σq=420.844, this case also corresponds to (3) when power is always generated in FIG. 6, and the following is obtained. Therefore, in the end, the comparison coefficient value of the active power conversion rate of the PT system and LA system is (1) η*=5.
013η*, (2) η*=3.595η*.

In other words, the LA system in which the claimed invention and the co-filed invention are introduced in combination can constantly generate power from both the air liquefaction engine EGI and the liquid air engine EGII under appropriate operating conditions.
It provides an active power conversion rate well over 3.5 times that of conventional PT systems. In other words, this LA system uses more than 3.5 times the total amount of paid heat (fuel combustion heat) supplied to the entire system, including the thermal power plant, which is the original power generation source, compared to conventional systems. The fact that Ale is one of the dominant factors in the η* equation makes it obvious that the present invention is an essential and important component for that system. Probably.

Taking the discussion one step further, the invention proposed in conjunction with the patent application could replace the conventional simple gas turbine power generation system, which compresses atmospheric air to high pressure and then provides paid heat while consuming most of the generated power internally, by liquefying the air once. If we then omit individual power storage and immediately convert to a new gas turbine power generation system that uses the present invention to generate high-pressure liquid air and supply paid heat to it, the power consumption for air liquefaction will be reduced. Regardless of the presence or absence of this, a dramatic increase in output and high efficiency can be expected.

This can be said to be a typical application example of FIG.

It should be noted that the closed cycle of the cycle of the present invention can be replaced with an open cycle.

[Brief explanation of drawings]

Figure 1 is a T-s diagram of a hybrid cycle that combines open, closed, and auxiliary closed gas turbine cycles consisting of various processes such as isothermal compression, isothermal expansion, adiabatic compression, and countercurrent heat exchange; The figure is the equipment configuration diagram of the cycle in Figure 1, and the diagram in Figure 3.
Figure 1 is a T-s diagram of an open and closed gas turbine cycle in which all isothermal changes in the cycle are replaced with adiabatic changes, and Figure 4 is an equipment configuration diagram of the cycle in Figure 3. Figure 5 is.
A conceptual diagram of the PT system, FIG. 6 is a conceptual diagram of the LA system.

Claims (2)

[Claims] (1) Open type in which liquid air itself is used as the working material in the interval between high temperature ■_0 (upper/high temperature heat source temperature), atmospheric pressure air liquefaction temperature T_0_0 (low temperature heat source temperature), and given high pressure P_2_0 and atmospheric pressure P_0. gas turbine cycle,
Normal temperature T_0 (lower/high temperature heat source temperature) and low temperature T_3 (T
_0>T_3>T_0_0) and given pressure P_1
_0 (P_2_0>P_1_0>P_0) and atmospheric pressure P_
A closed gas turbine cycle with circulating air as the working substance in the section 0, normal temperature T_0 (lower/higher heat source temperature), lower temperature T_1 (T_0>T_1>T_3), and given pressure @P@_0 (P_1_0>@ P@_0>P
In a hybrid cycle that combines an auxiliary closed gas turbine cycle that uses circulating air as the working material in the section between
P_0→P_2_0)・Constant pressure expansion (P=P_2_0)・
Isothermal expansion (P_2_0→P_0)/constant pressure compression (P=P_
0) and other processes up to release into the atmosphere,
Compression thermal energy added to circulating air during isothermal compression in a closed cycle in the constant pressure expansion stroke after liquid air supplied at extremely low temperature T_0_0 and pressure P_0 is adiabatically compressed to a given high pressure P_2_0. The liquid air is evaporated and heated to reach room temperature T_0, and then the exhaust heat is recovered by countercurrent heat exchange with the exhaust air. The high-temperature, high-pressure air that has reached the state of high temperature ■_0 and pressure P_2_0 is expanded from the upper high-temperature heat source in the isothermal expansion stroke of the subsequent open cycle. It expands isothermally to atmospheric pressure P_0 while receiving thermal energy, and in the next constant-pressure compression process, waste heat is removed by countercurrent heat exchange with the high-pressure air that is expanding at constant pressure from normal temperature T_0 to high temperature ■_0. While exhaling, it is cooled down to room temperature T_0 and pressure P_0.
The closed cycle is a constant pressure compression of circulating air (P=P_
0)・Isothermal compression (P_0→P_1_0)・Constant pressure expansion (P
=P_1_0) and isothermal expansion (P_1_0→P_0), and in the isothermal compression process from atmospheric pressure P_0 at low temperature to a given pressure P_1_0, the compression heat energy added to the circulating air is It is absorbed by the total cold heat of the liquid air expanded at constant pressure in the mold cycle and a part of the cold heat of the circulating air itself, and by countercurrent heat exchange between the constant pressure compression stroke and constant pressure expansion stroke of the cycle. Cooling and heating of the circulating air proceed at the same time, and 2. In the isothermal expansion process from normal temperature T_0 and pressure P_1_0 to atmospheric pressure P_0 in a closed cycle, expansion heat is transferred to the circulating air from a low-temperature/high-temperature heat source below normal temperature T_0. The energy is supplied, e. The auxiliary closed cycle is a constant pressure accommodation of circulating air (P=
It is composed of various processes such as P_0), adiabatic compression (P_0→@P@_0), and isothermal expansion (@P@_0→P_0),
Cooling of the circulating air in the constant pressure compression stroke is performed by countercurrent heat exchange with the constant pressure expanded air of the open type cycle and the closed type cycle, and the temperature is normal temperature T_0 and pressure @P@_0.
In the isothermal expansion process from the state to atmospheric pressure P_0,
Expansion thermal energy is supplied to the circulating air from a low-temperature, high-temperature heat source at room temperature T_0, and this cycle proceeds roughly in the order of the above processes, and on the temperature-entropy diagram, the working material (air) is rotated by the rotation of a clock. A liquid air power generation method characterized by flowing clockwise in the same direction as the liquid air power generation method. (2) The method for generating liquid air power according to claim 1, wherein part or all of isothermal compression and isothermal expansion are replaced with adiabatic compression and adiabatic expansion, respectively.