KR102095572B1 - Liquefied gas re-gasification and power generation system - Google Patents

Abstract

Liquefied gas regasification and cold heat power generation systems are disclosed. A liquefied gas regasification and cold heat power generation system according to an embodiment of the present invention includes a liquefied gas transfer line for vaporizing liquefied gas and sending it to a demand destination; A heating medium circulation line in which a heating medium for vaporizing liquefied gas is circulated; A pump installed in the heating medium circulation line and circulating the heating medium in the heating medium circulation line; An evaporator installed in the heating medium circulation line and vaporizing the heating medium by heat exchange with the heating medium; A vaporizer installed on the heating medium circulation line and re-evaporating the liquefied gas of the liquefied gas transfer line using the thermal energy and latent heat of the vaporized heating medium; A heater that heats the liquefied gas regasified by the vaporizer to a temperature required by the customer; And a turbine installed between the evaporator and the vaporizer in the heat medium circulation line, and generated by the power of the heat medium vaporized by the evaporator.

Description

Liquefied gas regasification and cold / heat power generation system {LIQUEFIED GAS RE-GASIFICATION AND POWER GENERATION SYSTEM}

The present invention relates to a liquefied gas regasification and cold heat power generation system, and more particularly, to a liquefied gas regasification and cold heat power generation system that generates power by using cold heat of a heat medium heat exchanged with liquefied gas in the regasification process of liquefied gas. .

2. Description of the Related Art In recent years, demand for fuels, such as natural gas, which has less emission of environmental pollutants, is increasing due to the trend of strengthening environmental regulations. In order to supply natural gas to the consumer, a system for regasifying liquefied natural gas stored in a liquefied state in a liquefied gas storage tank is required. Conventional liquefied gas regasification system exchanges heat sources such as sea water and cryogenic liquefied natural gas (LNG) to re-liquefy liquefied natural gas into high temperature and high pressure natural gas. The large amount of cold heat absorbed through the high-temperature heat source is not recovered and is discarded as a source of water or heat source.

The present invention provides a liquefied gas regasification and cold heat power generation system that efficiently generates power using cold heat absorbed as a heat source during regasification of liquefied gas.

The problems to be solved by the present invention are not limited to the problems mentioned above. Other technical problems not mentioned will be clearly understood by those skilled in the art from the following description.

A liquefied gas regasification and cold heat power generation system according to an aspect of the present invention, a liquefied gas transfer line for vaporizing the liquefied gas and sending it to the customer; A heating medium circulation line through which a heating medium for vaporizing the liquefied gas is circulated; A pump installed in the heat medium circulation line and circulating the heat medium in the heat medium circulation line; An evaporator installed on the heat medium circulation line and vaporizing the heat medium by heat exchange with the heat medium; A vaporizer installed on the heat medium circulation line and regasifying liquefied gas of the liquefied gas transfer line using heat energy and latent heat of vaporized heat medium; A heater that heats the liquefied gas regasified by the vaporizer to a temperature required by the customer; And a turbine installed between the evaporator and the vaporizer in the heat medium circulation line, and generated by the power of the heat medium vaporized by the evaporator.

Liquefied gas regasification and cold heat power generation system according to an embodiment of the present invention, so that the heating medium flowing into the turbine does not deviate from the gas-liquid mixing section in which the turbine can be operated normally, and the heating medium discharged from the vaporizer becomes liquid, It may further include a controller for controlling at least one of the flow rate and pressure of the heat medium flowing into the turbine.

A liquefied gas regasification and cold heat power generation system according to an embodiment of the present invention includes: a bypass line connected in parallel with the turbine between the evaporator and the vaporizer, and allowing the heat medium to bypass the turbine and flow into the vaporizer; And a bypass valve installed on the bypass line.

The controller may open the bypass valve when the turbine is damaged, the function of the turbine is restricted, or the flow rate of the heat medium exceeds the allowable capacity of the turbine.

Liquefied gas regasification and cold heat power generation system according to an embodiment of the present invention, a temperature sensor for measuring the temperature of the heat medium discharged from the evaporator; And a pressure sensor for measuring the pressure of the heat medium discharged from the evaporator, wherein the controller controls the opening degree of the bypass valve according to the temperature and pressure of the heat medium measured by the temperature sensor and the pressure sensor. can do.

Liquefied gas regasification and cold heat power generation system according to an embodiment of the present invention, a heat source supply line for supplying the heat medium vaporized by the evaporator to the heater; And a heat medium transfer line that supplies the heat medium liquefied by heat exchange in the heater to a rear end of the vaporizer.

Liquefied gas regasification and cold heat power generation system according to an embodiment of the present invention is installed in the heat medium circulation line, the heat medium tank for storing the heat medium discharged from the vaporizer and the heat medium transferred from the heater through the heat medium transfer line; It may further include.

Liquefied gas regasification and cold heat power generation system according to an embodiment of the present invention, a generator that generates power using the pressure of the vaporized liquefied gas discharged from the heater; And a heating unit for heating the liquefied liquefied gas discharged from the generator to a temperature required by the customer may further include.

According to an embodiment of the present invention, a liquefied gas regasification and cold heat power generation system that efficiently generates power using cold heat absorbed as a heat source during regasification of a liquefied gas is provided.

The effects of the present invention are not limited to the effects described above. Effects not mentioned will be clearly understood by those skilled in the art from the present specification and the accompanying drawings.

1 is a block diagram of a liquefied gas regasification and cold heat power generation system according to an embodiment of the present invention.
2 is a graph illustrating a refrigerant characteristic curve showing a state of a heat medium according to enthalpy and pressure of a heat medium.
3 is a block diagram of a liquefied gas regasification and cold heat power generation system according to another embodiment of the present invention.
4 is a block diagram of a liquefied gas regasification and cold heat power generation system according to another embodiment of the present invention.
5 is a graph showing a state of a heating medium in a refrigerant characteristic curve (PH diagram) under control of a bypass valve constituting a liquefied gas regasification and cold heat power generation system according to an embodiment of the present invention.
6 is a block diagram of a liquefied gas regasification and cold heat power generation system according to another embodiment of the present invention.

Other advantages and features of the present invention, and methods for achieving them will be clarified with reference to embodiments described below in detail together with the accompanying drawings. However, the present invention is not limited to the embodiments disclosed below, and the present invention is only defined by the scope of the claims. If not defined, all terms (including technical or scientific terms) used herein have the same meaning as generally accepted by universal technology in the prior art to which this invention belongs. The general description of known configurations may be omitted so as not to obscure the subject matter of the present invention. In the drawings of the present invention, the same reference numerals are used wherever possible. In order to facilitate understanding of the present invention, some components in the drawings may be somewhat exaggerated or reduced.

Terms used in the present application are only used to describe specific embodiments, and are not intended to limit the present invention. Singular expressions include plural expressions unless the context clearly indicates otherwise. In this application, the terms “include”, “have” or “have” are intended to indicate that there are features, numbers, steps, actions, components, parts or combinations thereof described in the specification, but one Or further features or numbers, steps, actions, components, parts, or combinations thereof, should not be excluded in advance.

1 is a block diagram of a liquefied gas regasification and cold heat power generation system according to an embodiment of the present invention. Referring to FIG. 1, the liquefied gas regasification and cold heat power generation system 100 according to the present embodiment recovers liquefied gas such as liquefied natural gas (LNG) and liquefied petroleum gas (LPG). In order to improve power generation efficiency by supplying fuel gas such as natural gas (NG), petroleum gas (Petroleum Gas) to customers, and generating power by using cold heat of liquefied gas in the heat exchange process to regasify the liquefied gas Can be provided.

In one embodiment, the liquefied gas regasification and cold heat power generation system 100 is a liquefied gas transfer line (112, 114, 116), vaporizer 120, heat medium circulation line 130, pump 140, the first flow rate control It includes a valve 150, an evaporator 160, a turbine 170, a heater 180, a first heat source line 190, a second flow control valve 200 and a second heat source line 210.

The liquefied gas transfer lines 112, 114, and 116 may be provided to receive liquefied gas and vaporize the supplied liquefied gas to transmit it to a customer. The consumer may be, for example, a gas turbine, but is not limited thereto.

The high pressure booster pump 110 may pressurize and supply cryogenic liquefied gas from the liquefied gas storage tank or buffer tank to the liquefied gas transfer line 112, 114, 116 in consideration of the pressure required at the place of use. The liquefied gas pressurized by the high-pressure booster pump 110 is vaporized and heated through the vaporizer 120 and the heater 180 to be supplied to the customer.

The heating medium circulation line 130 circulates the heating medium for vaporizing the liquefied gas. The heat medium may be provided, for example, by sea water, steam, or waste heat of an engine in a ship. For the heat medium, for example, the fluids and / or mixtures indicated in Table 1 below may be used.

ethane Propane I-butane N-butane R13B1 R143a R134a R152a R22 R12 R13 R125 R500 R502 R507 R114 R14 R23 R744

The heat medium circulates through the heat medium circulation line 130 sequentially through the pump 140, the first flow control valve 150, the evaporator 160, the turbine 170, and the vaporizer 120.

The vaporizer 120 re-vaporizes the liquefied gas of the liquefied gas transfer line using the thermal energy and latent heat of the heat medium.

The heater 180 heats the liquefied gas regasified by the vaporizer 120 to a temperature required by the customer.

The pump 140 pressurizes the heat medium discharged from the vaporizer 120 and circulates it in the heat medium circulation line 130. The pump 140 is installed at the rear end of the vaporizer 120 and the front end of the evaporator 160, and may be configured to pressurize the heating medium and supply it to the evaporator 160.

The first pressure sensor P1 and the first temperature sensor T1 are installed in the heat medium circulation line 130 between the carburetor 120 and the pump 140. The first pressure sensor P1 and the first temperature sensor T1 measure the pressure and temperature of the liquid heat medium discharged from the vaporizer 120.

The evaporator 160 vaporizes the liquid heat medium discharged from the vaporizer 120 and circulating by heat exchange with a heat source. The heat source may be provided by sea water, steam, waste heat of the engine in the ship, and the like. The evaporator 160 may evaporate the heat medium by heat exchange with a heat source supplied through the second heat source line 210.

The turbine 170 is installed between the evaporator 160 and the vaporizer 120. The turbine 170 is generated by the power of the heat medium vaporized by the evaporator 160.

A second pressure sensor P2 and a second temperature sensor T2 are installed between the evaporator 160 and the turbine 170. The second pressure sensor P2 and the second temperature sensor T2 measure the pressure and temperature of the heat medium vaporized in the evaporator 160.

A third temperature sensor T3 is installed between the vaporizer 120 and the heater 180. The third temperature sensor T3 measures the temperature of the liquefied gas vaporized by the vaporizer 120.

The flow rate of the heating medium can be controlled according to the measured values of the first temperature sensor T1, the first pressure sensor P1, the second temperature sensor T2, the second pressure sensor P2, and the third temperature sensor T3. You can.

A fourth temperature sensor T4 is installed at the rear end of the heater 180. The fourth temperature sensor T4 measures the temperature of the vaporized liquefied gas discharged from the heater 180.

The heater 180 heats the liquefied gas vaporized by heat exchange with a heat source supplied through the first heat source line 190. The first heat source line 190 is provided with a second flow control valve 200 for adjusting the flow rate of the heat source. The second flow control valve 200 may be controlled according to the temperature measurement values of the third temperature sensor T3 and the fourth temperature sensor T4.

In the illustrated example, the evaporator 160 and the heater 180 are configured to vaporize the heat medium using the same heat source and heat the vaporized liquefied gas, but different heat sources may be used.

The Rankine cycle is applied to the cycle for recovering the cold heat of liquefied gas. That is, the low-temperature liquid state heat medium is pressurized through the pump 140, and then evaporated and heated through a heat source in the evaporator 160. Thereafter, a pressure drop occurs through the turbine 170 for power generation, and then the low-pressure refrigerant is liquefied again through the vaporizer 120 and circulated.

When applying the Rankine cycle, there are constraints that must satisfy the gas temperature and pressure conditions required by the customer, so the cold heat recoverable from the liquefied gas may drop significantly. Since the efficiency of cold and heat generation depends on the type, pressure, and flow rate of the heat medium, it is necessary to optimize the pressure and flow rate of the heat medium that is pressurized to maximize the efficiency of heat and heat generation.

The flow rate and pressure of the heating medium may be determined based on the temperature and pressure of the heating medium discharged from the vaporizer 120, the temperature of the heat source used in the evaporator 160, the pressurization point of the heating medium, and the temperature of the gas sent to the customer.

2 is a graph illustrating a refrigerant characteristic curve showing a state of a heat medium according to enthalpy and pressure of a heat medium. 1 and 2, the flow rate and pressure of the heat medium flowing into the turbine 170 is such that the heat medium flowing into the turbine 170 does not deviate from the gas-liquid mixing section in which the turbine 170 can operate normally, and also the vaporizer The heat medium discharged from the 120 may be controlled to become a liquid phase. That is, when the heat medium introduced into the turbine 170 is discharged, it is possible to limit the pressure to pressurize the turbine 170 so that it does not fall beyond the operable gas-liquid mixing section.

On the other hand, it is necessary to raise the heat medium to the maximum pressure in consideration of the characteristic that the higher the temperature of the heat medium, the higher the pressure that can be operated while maintaining the gas state. However, there is a limitation in that the temperature of the liquefied gas vaporized by heat exchange with the heat medium in the vaporizer 120 should be set to a temperature required by the customer.

For this reason, the pressure condition of the heating medium may be restricted, and by providing the heater 180 to solve such limitations, the pressure drop of the heating medium is changed to the maximum to increase the amount of cold and heat generation, and at the same time, the gas temperature required by the customer is required. Can match.

3 is a block diagram of a liquefied gas regasification and cold heat power generation system according to another embodiment of the present invention. In describing the embodiment of FIG. 3, a duplicate description of the same or corresponding components as the above-described embodiment may be omitted.

The liquefied gas regasification and cold heat power generation system 100 according to the embodiment of FIG. 3 further includes a heat medium tank 220, and the evaporator 160 and the heater 180 are configured to exchange heat using different heat sources. There is a difference from the embodiment described above.

The heater 180 is configured to receive the heat medium vaporized by the evaporator 160 through the heat source supply line 230 and heat the vaporized liquefied gas by exchanging heat with the liquefied gas vaporized by the vaporizer 120.

The heat medium supplied through the heat source supply line 230 is liquefied by heat exchange with the liquefied gas vaporized in the heater 180 and is designed to be supplied to the rear end of the carburetor 120 through the heat medium transfer line 240.

A fifth pressure sensor P5 and a fifth temperature sensor T5 are installed in the heat source supply line 230, and a sixth pressure sensor P6 and a sixth temperature sensor T6 are installed in the heat medium transfer line 240. do. The flow rate and pressure of the heating medium supplied to the heater 180 are the third temperature sensor (T3), the fourth temperature sensor (T4), the fifth pressure sensor (P5), the fifth temperature sensor (T5), and the sixth pressure sensor ( P6) and the sixth temperature sensor T6 may be controlled according to the measured values.

The heating medium tank 220 is installed in the heating medium circulation line, and stores the heating medium discharged from the vaporizer 120 and the heating medium transferred from the heater 180 through the heating medium transfer line 240.

The heat medium tank 220 absorbs the pressure change of the heat medium according to the operating conditions, and allows the heat medium to maintain a set temperature range so that it can operate in a predetermined pressure range. The heat medium tank 220 may be provided as an expansion tank.

The flow rate ratio of the heat medium passing through the vaporizer 120 and the heater 180 is determined in consideration of the maximum temperature at which the heat medium discharged from the heater 180 can be changed into a liquid phase. The pump 140 or the first flow control valve 150 may be controlled according to the pressure and flow rate of the heat medium determined through this process.

According to the embodiment of FIG. 3, heat is exchanged by utilizing the heat medium heated by the heat source of the evaporator 160 as a heat source of the heater 180 without generating a separate heat source due to sea water, steam, air, and waste heat in the ship. The size of the device can be reduced and the heat source line can be simplified.

4 is a block diagram of a liquefied gas regasification and cold heat power generation system according to another embodiment of the present invention. In describing the embodiment of FIG. 4, a duplicate description of the same or corresponding components as the above-described embodiments may be omitted.

The liquefied gas regasification and cold heat power generation system 100 according to the embodiment of FIG. 4 further includes a bypass line 250, a bypass valve 260, a flow control valve 270, and a controller 280 There is a difference from the above-described embodiments.

The bypass line 250 is connected in parallel with the turbine 170 between the evaporator 160 and the vaporizer 120. The bypass line 250 may allow the heat medium to bypass the turbine 170 and enter the vaporizer 120.

The bypass valve 260 is installed on the bypass line 250 and can control the flow rate of the heat medium bypassing the turbine 170.

The flow control valve 270 is installed at the front of the turbine 170 to control the flow rate of the heat medium flowing into the turbine 170.

The controller 280 prevents the heating medium flowing into the turbine 170 from leaving the gas-liquid mixing section in which the turbine 170 can operate normally, and also, the bypass valve 260 so that the heating medium discharged from the vaporizer 120 becomes liquid. And the flow control valve 270 to control the flow rate and pressure of the heat medium flowing into the turbine 170.

The controller 280 includes a first temperature sensor T1, a first pressure sensor P1, a second temperature sensor T2, a second pressure sensor P2, a third temperature sensor T3, and a seventh temperature sensor ( Based on the measured value of T7), the pump 140, the first flow control valve 150, the bypass valve 260 and the flow control valve 270 can be controlled.

In one embodiment, the controller 280 may open the bypass valve 260 in the event that the turbine 170 is damaged, the function of the turbine 170 is restricted, or the flow rate of the heating medium exceeds the allowable capacity of the turbine. You can.

The controller 280 optimizes the vaporization performance of the vaporizer 120 and the power generation efficiency of the turbine 170 by considering the heat medium discharge temperature of the vaporizer 120, for example, based on the refrigerant characteristic curve as shown in FIG. 2. Calculate and set the pressurized pressure value of the heating medium for the purpose. At this time, the controller 280 limits the pressure optimum point of the heat medium so that the heat medium that is pressure-dropped in the turbine 170 satisfies the allowable range of phase change of the turbine 170.

In order to optimize the refrigerant flow rate, it is necessary to consider the amount of NG gas required by the consumer, and increase the recovery rate of cold heat in the vaporizer 120. For this, the amount of heat supplied to the vaporizer 120, which is a section for vaporizing and heating LNG, must be maximized. . However, since the heat medium passing through the vaporizer 120 is discharged from the vaporizer 120 and then introduced into the pump 140, it must be liquid. Therefore, the controller 280 detects the temperature of the heat medium at the rear end of the carburetor 120 and adjusts the flow rate of the heat medium to be a temperature that becomes a liquid phase under the pressure condition of the carburetor 120.

In the controller 280, the pressure and flow rate of the heat exchanger of the heat medium / heat source optimally calculated through the calculation process by the combination of the characteristics of the fluid, the temperature of each point, and the pressure is a variable frequency drive (VFD) connected to the pump 140 ) Or the first flow control valve 150 installed at the rear end of the pump 140.

When the flow rate of the heat medium circulated for regasification of the liquefied gas exceeds the capacity of the turbine 170, the flow rate of the heat medium is limited due to the allowable capacity of the turbine 170 to not supply a sufficient heat source for regasification of the liquefied gas. I can't. To prevent this, when the turbine 170 is installed in a large capacity, power generation efficiency is deteriorated because the main use point of operation always exceeds the proper circulation amount.

According to the embodiment of FIG. 4, the carburetor, such as when the turbine 170 is damaged, when the turbine 170 is only capable of some limited function, or when a heat medium exceeding the capacity of the turbine 170 is to be supplied, etc. When the flow rate of the heat medium to be supplied to the 120 needs to be temporarily increased, the heat medium can be additionally supplied through the bypass line 250, so that the regasification operation can be smoothly performed.

In the case of the heating medium flowing into the vaporizer 120 through the bypass line 250, the energy state is higher than the outlet of the turbine 170 that recovered kinetic energy, so only a relatively small flow rate is used to vaporize the vaporizer through the bypass line 250. Regasification can also be achieved by supplying it to the (120) side.

When bypassing the heat medium through the bypass line 250, an energy transfer amount and a difference used in cold and heat power generation may occur. In this case, the controller 280 detects the heat medium temperature at the rear end of the carburetor 120, , Adjust the flow rate of the heat medium passing through the flow control valve 270 and the bypass valve 260 so that the heat medium at the rear end of the vaporizer 120 maintains the liquid phase. Even when the operation of the turbine 170 is impossible, regasification operation is possible through the bypass line 250.

5 is a graph showing a state of a heating medium in a refrigerant characteristic curve (P-H diagram) under control of a bypass valve constituting a liquefied gas regasification and cold heat power generation system according to an embodiment of the present invention.

Referring to FIG. 5, the heat medium energy at the outlet side of the turbine 170 undergoes an adiabatic process indicated by a red arrow in the PH diagram, and when operation of the turbine 170 is impossible, blue through the bypass line 250 The energy state is higher due to the throttling process indicated by the arrow.

Therefore, when the heat medium is supplied to the vaporizer 120 through the bypass line 250, since it is possible to supply heat even at a smaller flow rate, it is necessary to reduce the total circulating refrigerant flow rate.

When the heat medium having a high energy state undergoes re-vaporization, the heat medium in the gas-liquid state may cause damage to the pump 140 because liquefaction of the heat medium does not occur. Accordingly, when the heat medium is bypassed to the bypass line 250 and supplied to the vaporizer 120, the controller 280 checks the temperature of the heat medium passing through the vaporizer 120 to open or pump the bypass valve 260. By adjusting the frequency of 140, the flow rate of the circulating heating medium is adjusted.

If the temperature of the heating medium (seawater) increases due to summer or environmental factors, the temperature of the heating medium passing through the turbine 170 increases, so the controller 280 closes or reduces the bypass valve 260, and the flow control valve The amount of heat medium passing through the turbine 170 through 270 can also be reduced.

6 is a block diagram of a liquefied gas regasification and cold heat power generation system according to another embodiment of the present invention. In describing the embodiment of FIG. 6, a duplicate description of the same or corresponding components as the above-described embodiments may be omitted.

The liquefied gas regasification and cold heat power generation system 100 according to the embodiment of FIG. 6 is different from the above-described embodiments in that it further includes a generator 290 and a heating unit 300.

The generator 290 further generates power by using the pressure of the vaporized liquefied gas discharged from the heater 180.

The heating unit 300 heats the liquefied liquefied gas discharged from the generator 290 to a temperature required by the customer.

According to the embodiment of FIG. 6, additional power generation is possible by using the gas pressure at the rear end of the heater 180 according to the pressure required by the customer. At this time, since the temperature drop also occurs in accordance with the pressure drop of the gas in the generator 290, the heating unit 300 heats NG using seawater, steam, air, and waste heat in the ship to supply it to the customer. The turbine of the generator 290 may be connected coaxially with the turbine 170 used for cold and heat generation of liquefied gas.

It is to be understood that the above embodiments are provided to help the understanding of the present invention, and do not limit the scope of the present invention, and various modified examples from this also belong to the scope of the present invention. The technical protection scope of the present invention should be determined by the technical spirit of the claims, and the technical protection scope of the present invention is not limited to the literary description of the claims, but is a category in which technical value is substantially equal. It should be understood that it extends to the invention.

100: liquefied gas regasification and cold heat power generation system
110: high pressure booster pump 112, 114, 116: liquefied gas transfer line
120: vaporizer 130: heat medium circulation line
140: pump 150: first flow control valve
160: evaporator 170: turbine
180: heater 190: first heat source line
200: second flow control valve 210: second heat source line
220: heat medium tank 230: heat source supply line
240: heat medium transfer line 250: bypass line
260: bypass valve 270: flow control valve
280: controller 290: generator
300: heating unit T1 ~ T8: temperature sensor
P1 ~ P8: Pressure sensor

Claims (8)

A liquefied gas transfer line for vaporizing the liquefied gas and sending it to a consumer;
A heating medium circulation line through which a heating medium for vaporizing the liquefied gas is circulated;
A pump installed in the heat medium circulation line and circulating the heat medium in the heat medium circulation line;
An evaporator installed on the heat medium circulation line and vaporizing the heat medium by heat exchange with the heat medium;
A vaporizer installed on the heat medium circulation line and regasifying liquefied gas of the liquefied gas transfer line using heat energy and latent heat of vaporized heat medium;
A heater that heats the liquefied gas regasified by the vaporizer to a temperature required by the customer;
A turbine installed between the evaporator and the vaporizer in the heat medium circulation line, and generated by the power of the heat medium vaporized by the evaporator;
A controller that controls at least one of the flow rate and pressure of the heat medium flowing into the turbine so that the heat medium flowing into the turbine does not deviate from the gas-liquid mixing section in which the turbine can operate normally, and the heat medium discharged from the vaporizer becomes liquid. ;
A bypass line connected in parallel with the turbine between the evaporator and the vaporizer, and allowing the heat medium to bypass the turbine and flow into the vaporizer;
A bypass valve installed on the bypass line;
A temperature sensor that measures the temperature of the heat medium discharged from the evaporator; And
It includes a pressure sensor for measuring the pressure of the heating medium discharged from the evaporator,
The controller is configured to control the opening degree of the bypass valve according to the temperature and pressure of the heat medium measured by the temperature sensor and the pressure sensor liquefied gas regasification and cold heat power generation system. delete delete According to claim 1,
The controller is a liquefied gas regasification and cold heat power generation system that opens the bypass valve when the turbine is damaged, the function of the turbine is restricted, or the flow rate of the heat medium exceeds the allowable capacity of the turbine. delete The method according to claim 1 or 4,
A heat source supply line supplying the heat medium vaporized by the evaporator to the heater; And
A liquefied gas regasification and cold heat power generation system further comprising; a heating medium transfer line for supplying the heat medium liquefied by the heat exchange in the heater to a rear end of the vaporizer. The method of claim 6,
Liquefied gas regasification and cold heat power generation system further comprising; a heat medium tank that is installed on the heat medium circulation line and stores heat medium discharged from the vaporizer and heat medium conveyed from the heater through the heat medium delivery line. The method according to claim 1 or 4,
A generator that generates power using the pressure of the vaporized liquefied gas discharged from the heater; And
Further comprising: a heating unit for heating the vaporized liquefied gas discharged from the generator to a temperature required by the demand source.

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