JP2002318027A - Refrigerating system - Google Patents

Abstract

PROBLEM TO BE SOLVED: To provide a refrigerating system, capable of realizing energy-reducing effect, even in a factory or the like where a heat demand is small by a method where a cogeneration system employing a gas turbine is effectively utilized by combining the same with a refrigerating machine. SOLUTION: The refrigerating machine 2, constituting an air refrigeration cycle, obtains refrigerated air, compressed by compression means 121, 232 and cooled by cooling means 22, 24, by expanding the same through an expansion turbine 231, and the output of a steam turbine 211, driven by superheated steam generated by a boiler 4 heated by the heat of exhaust gas of a gas turbine 1, is employed for the compression of the refrigerant air.

Description

DETAILED DESCRIPTION OF THE INVENTION

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a refrigeration system for cooling refrigerant air using exhaust heat of a gas turbine.

[0002]

2. Description of the Related Art For example, in a food processing factory where food is processed and cooked, and furthermore, the food is rapidly frozen at the time of shipment and shipped while maintaining the quality of the food, it has been conventionally required that: Fuel is burned for heat source for heat treatment, etc.
Electric power was consumed for driving various devices for freezing processing and the like.

[0003] In response to recent demands for reduction of energy consumption, cogeneration (combined heat and power) systems for extracting electric energy from a gas turbine that operates by burning fuel and cooking a boiler or the like with the exhaust heat of the gas turbine have become widespread. It is getting. Particularly in a food processing plant, there is a large demand for heat such as sterilization, boiling, cooking, and washing of foods and dishes with hot water, and it is expected that a cogeneration system using a gas turbine will improve the energy consumption reduction effect. Furthermore, with the practical use of micro gas turbines in recent years, it is expected that such cogeneration will be used in small factories.

[0004] On the other hand, in the food processing field and the like, attempts have been made to use an air refrigeration cycle using air as a refrigerant to blow cryogenic air at a very low temperature and rapidly freeze the food. In conventional vapor cycle refrigerators that use conventional chlorofluorocarbons or alternative fluorocarbons as refrigerants and perform refrigeration with latent heat of vaporization, the coefficient of performance is very low in the freezing range, for example, pumping heat from -40 ° C or lower and radiating it to room temperature. Decrease. An air refrigeration cycle refrigerator can be expected to have a relatively high coefficient of performance as compared with such a vapor cycle refrigerator. In addition, the air cycle refrigerator can directly apply the refrigerant air to the food, and there is no need to exchange heat via a heat transfer member such as a panel in the freezing section, so that a process such as defrosting the heat transfer member is unnecessary. The merit of becoming it is also expected. As such an air refrigeration cycle, for example, JP-A-2-97850 and JP-A-2000-12184 are described.
Air is compressed by a first-stage compressor driven by an electric motor or an internal combustion engine, the heated air is cooled, and then compressed by a second-stage centrifugal compressor driven by an expansion turbine, and then the heated air is cooled. Is cooled again and then expanded by an expansion turbine to obtain low-temperature air.

[0005]

It is considered that a cogeneration system using a gas turbine is suitable in the field of food processing or the like because, for example, a large amount of steam is generated by a boiling pot and the like, and heat is utilized to generate electricity. 2 of quantity
This is because a heat load three times as much is expected, and effective use of high-temperature exhaust gas from the gas turbine is expected.

However, when observing the processing steps in such a food processing plant, boiling pots and the like are often subjected to batch processing, and the heat load is different between when the boiling pot is cooked and when it is not. Large differences occur. For this reason,
In a large-scale factory in which a plurality of boiling pots are sequentially processed, the heat load becomes uniform to some extent, and the cogeneration system can be easily used. However, in a small-scale factory where a micro gas turbine is suitable, since a heat load is generated only intermittently, it is necessary to start and stop the gas turbine. On the other hand, power demand in a factory exists independently of changes in heat load. Then, even if the cogeneration system is introduced, if the cogeneration system is stopped while the heat load does not occur, there is a problem that opportunities for cogeneration can be reduced and the cogeneration system cannot be fully utilized. In addition, there is also a problem that when a peak cut of power supplied from a power company is required in summer or the like, power generation capacity cannot be used. If the power demand in the factory fluctuates, it can be dealt with in cooperation with a power system for selling power, etc., but it has not been possible to cope with the change in heat load in the past.

On the other hand, in a refrigerator used in a food factory or the like, an electric motor driven by electric power supplied from an electric power company is set apart from an absorption refrigerator using lithium bromide which is used at a temperature above the freezing point. Also, it has been proposed to use a compressor driven by shaft power of a gas turbine constituting a cogeneration system. However, when electric power is consumed to drive the electric motor, there is a problem in that only about 35% of the energy of fuel is used on a fuel energy consumption basis in a thermal power plant. In addition, when the shaft power of the gas turbine is used, valuable power generation capacity of the cogeneration system is reduced, and thus the balance between the heat load and the power load is deteriorated. As described above, it is difficult to introduce a cogeneration system on a micro gas turbine scale, and in combination with a refrigerator, it is more difficult to achieve an energy reduction effect by utilizing the cogeneration system.

[0008]

A refrigeration system according to the present invention includes a gas turbine, a boiler for generating superheated steam by exhaust heat of the gas turbine, and a refrigerator constituting an air refrigeration cycle. The refrigerator has a steam turbine driven by superheated steam generated by the boiler, a compressor for compressing the refrigerant air, a cooling unit for the compressed refrigerant air, and a low temperature by expanding the cooled refrigerant air. And an expansion turbine for air. The output of the steam turbine is used to compress the refrigerant air. According to the configuration of the present invention, the steam turbine is driven by superheated steam generated by the boiler by the exhaust heat of the gas turbine, and the output of the steam turbine is used for compressing the refrigerant air in the air refrigeration cycle. The high temperature exhaust is used for the heat demand of the refrigerator. Thereby, the electric energy is taken out from the generator driven by the gas turbine,
In addition, by combining a cogeneration system that extracts heat energy from the exhaust gas of the gas turbine with a refrigerator, it becomes possible to reduce fluctuations in heat load and to effectively use energy. After the high-temperature exhaust heat of the gas turbine is used for generating superheated steam by the boiler, the exhaust heat can be effectively used in a cascade downstream of the boiler, so that a highly efficient cogeneration system can be constructed. By employing a micro gas turbine as the gas turbine, it can be used in small-scale food processing factories and the like, and contribute to society by reducing energy consumption by the cogeneration system.

Preferably, the output of the expansion turbine is used to compress the refrigerant air. Thereby, not only the output of the steam turbine but also the output of the expansion turbine can be used for compressing the refrigerant air, and the cooling capacity of the refrigerator can be increased to obtain lower-temperature air. In this case, the compressor has a first compression device and a second compression device as its compression means, and has a first cooling device and a second cooling device as its cooling means, and the refrigerant air compressed by the first compression device. Is cooled by the first cooling device, the refrigerant air cooled by the first cooling device is compressed by the second compression device, and the refrigerant air compressed by the second compression device is cooled by the second cooling device. The refrigerant air cooled by the second cooling device may be expanded by the expansion turbine.
Thereby, compression and cooling of the refrigerant air are performed in two stages, and the cooling capacity can be further improved. When the compression and cooling of the refrigerant air are performed in two stages, one of the first compression device and the second compression device is driven by the steam turbine and the first compression device and the second compression device are driven by the steam turbine. On the other hand, it may be driven by the expansion turbine, or the first compression device and the second compression device may be driven by the steam turbine and the expansion turbine. By driving the first compression device and the second compression device by the steam turbine and the expansion turbine, the compression ratio of the two compression devices is optimized without being restricted by the output ratio of the steam turbine and the expansion turbine. can do.

[0010] A heat exchanger is provided for cooling the compressed refrigerant air by performing heat exchange between the pressurized water and the compressed refrigerant air, and the boiler is provided with the refrigerant air in the heat exchanger. Preferably, the superheated steam is generated by heating pressurized water heated by heat exchange with the exhaust heat. Thereby, energy efficiency can be further improved. Further, having a heat exchanger for performing heat exchange between the compressed refrigerant air before being expanded by the expansion turbine and the return air after the low-temperature air has cooled the refrigeration target increases energy efficiency. It is preferable for improvement.

[0011]

DESCRIPTION OF THE PREFERRED EMBODIMENTS A refrigeration system according to a first embodiment shown in FIG. 1 includes a micro gas turbine 1, a boiler 4 for generating superheated steam by exhaust heat of the gas turbine 1, and a refrigeration system constituting an air refrigeration cycle. Machine 2.

The gas turbine 1 has an intake filter 1
The air sucked through the compressor 0 is compressed by a centrifugal compressor 11, heated by exchanging heat with exhaust gas by a recuperator 12, mixed with the fuel blown in a combustion device 13, burned, and discharged from the combustion device 13. The combustion gas is expanded by the turbine 14 and the recuperator 12
Drain through. The exhaust temperature of such a gas turbine is usually 250 to 300 ° C., and has considerable heat energy. The rotating parts of the compressor 11 and the turbine 14 are connected by a rotating shaft 15. The power recovered from the turbine 14 causes the compressor 11
Is driven. The shaft 15 forms a rotor of a generator 16 which also serves as a starter motor. The generator 16
Is connected to a controller 17 having a built-in inverter circuit, and generates electric power except at the time of start-up. As a result, the electric power is linked to the electric power system via the controller 17 so that electric power can be exchanged with the electric power company. Is consumed by the power-using equipment in the facility where it is located. The surplus is also used by other facilities via power lines.

The exhaust gas from the gas turbine 1 is supplied to a boiler 4
Supplied to The boiler 4, as shown in FIG.
An economizer 41, an evaporator 42, and a superheated steam generator 43 are arranged in this order from the upstream side of the flow of the heating water to be heated. The supplied pressurized water is warmed in the economizer 41 by the exhaust heat of the gas turbine 1, the heated water is turned into saturated steam in the evaporator 42, and the saturated steam is turned into superheated steam in the superheated steam generator 43. You. A large number of smoke tubes are incorporated into the evaporating section 42 in order to increase the amount of heat taken from the exhaust B of the gas turbine 1. The pressurized water W supplied to the boiler 4 is, for example, approximately 4 atm (absolute pressure) by a pump 222.
The temperature is increased to 90 ° C. or more in the economizer 41, boiled at about 143 ° C. in the evaporator 42 to become saturated steam, and heated to about 200 ° C. in the superheated steam generator 43 to become superheated steam.
It is supplied to the refrigerator 2. Note that a valve 44 is provided between the boiler 4 and the refrigerator 2 so that the superheated steam is supplied to the refrigerator 2 after reaching the specified pressure. The valve 44 can be constituted by a regulator, an electromagnetic valve whose opening degree changes according to the detection value of the pressure sensor, or the like. Although a general boiler has a water pipe structure to secure a large heat transfer coefficient, the exhaust temperature of the gas turbine 1 serving as a heating source of the boiler 4 of the present embodiment usually rises only up to about 300 ° C. For example, the superheated steam generator 43 can be made small and compact by using a plate fin type heat exchanger.

The refrigerator 2 includes a first compression device 212, a first cooling device 22, a second compression device 232, and a second cooling device 2.
4. An air refrigeration cycle is constituted by the expansion turbine 231 and low-temperature air is supplied to the refrigeration chamber 3.

In the present embodiment, the first compressor 212 is constituted by a centrifugal blower, and is driven by a steam turbine 211 driven by superheated steam generated by the boiler 4 to compress the refrigerant air D. . That is, the output of the steam turbine 211 is used for compressing the refrigerant air. Therefore, the rotating part of the first compression device 212 and the rotating part of the steam turbine 211 are mechanically directly connected by the rotating shaft 213, so that the structure is simple and small. It is preferable that the rotating shaft 213 be supported in a non-contact manner by a dynamic pressure gas bearing or a magnetic bearing because it is possible to avoid the use of lubricating oil which has an adverse effect on food. The dynamic pressure gas bearing may be a foil-shaped member that supports the rotating shaft 213, and generates dynamic pressure by entraining air on the foil surface to support the rotating member 213. The superheated steam supplied from the boiler 4 expands in the steam turbine 211 from, for example, about 4 atm (absolute pressure) to about 1 atm (absolute pressure). 1 that contains
It becomes saturated steam of 00 ° C, for processing such as sterilization, boiling and steaming of food, fermentation heat source of food waste, sterilization system by steam and high temperature of facilities and equipment, heat source for drying of tableware, and odor. It is used as a heat source for absorption refrigerators using lithium chloride. The first compression device 212 which operates by transmitting the expansion work obtained by the steam turbine 211 via the shaft 213 compresses the refrigerant air.
The refrigerant air compressed by the first compression device 212 is
For example, about 1 atmosphere (absolute pressure) to about 1.4 atmospheres (absolute pressure)
And the temperature is raised to about 55 ° C to 75 ° C.

The refrigerant air compressed by the first compression device 212 is cooled by the first cooling device 22 to near normal temperature. The first cooling device 22 includes the first compression device 21
The first heat exchanger 221 performs heat exchange between the refrigerant air compressed by the pump 2 and pressurized water pressurized by the pump 222 to about 4 atm (absolute pressure).
The boiler 4 generates superheated steam by heating the pressurized water heated by the heat exchange with the refrigerant air in the first heat exchanger 221 by the exhaust gas from the gas turbine 1.

The refrigerant air cooled by the first cooling device 22 is compressed by the second compression device 232. In the present embodiment, the second compression device 232 is constituted by a centrifugal blower, and is driven by the expansion turbine 231.
In order to drive the second compression device 232, the rotating portion of the second compression device 232 and the rotating portion of the expansion turbine 231 are mechanically directly connected by a rotating shaft 233, so that the structure is simple and small. The rotating shaft 233 is preferably supported in a non-contact manner by a dynamic pressure gas bearing or a magnetic bearing similarly to the rotating shaft 213. The first compression device 212 which operates by transmitting the expansion work obtained by the steam turbine 211 via the shaft 213 compresses the refrigerant air. The refrigerant air compressed by the second compression device 232 is raised in pressure from, for example, about 1.4 atm (absolute pressure) to about 2 atm (absolute pressure) and at 70 ° C to 9 ° C.
The temperature is raised to about 0 ° C.

The refrigerant air compressed by the second compression device 232 is cooled by the second cooling device 24. The second cooling device 24 includes a second heat exchanger 241 and a regenerative heat exchanger 242. The second heat exchanger 24
1 performs heat exchange between the refrigerant air and the ambient air sent by the fan 243. The regenerative heat exchanger 242
Performs heat exchange between the refrigerant air and the low-temperature air discharged after being sent from the refrigerator 2 to the freezing chamber 3. By being cooled by the second cooling device 24, the refrigerant air is cooled to, for example, about -10 ° C.

The refrigerant air cooled by the second cooling device 24 expands in the expansion turbine 231 to become low-temperature air E. In the expansion turbine 231, the refrigerant air expands from about 2 atm (absolute pressure) to about 1 atm (absolute pressure), and the temperature becomes close to, for example, -50 ° C. This low-temperature air is supplied to the freezing chamber 3. That is, the refrigerator 2
Is a very low temperature air, which can be directly applied to the object F to be frozen, such as food, in the freezing chamber 3 as an air jet, so that cooling is easy and no treatment such as defrosting is required. In the refrigeration chamber 3, the low-temperature air flowing out of the expansion turbine 231 is blown out from the nozzle 31, and the overflowing low-temperature air is cooled around the chamber 3 by the chamber cooling pipe 32, and then supplied to the regenerative heat exchanger 242. The temperature of the regenerative heat exchanger 242 is increased to near normal temperature and supplied to the first compressor 212 as refrigerant air. In addition, the refrigerant air immediately after expansion, for example,-
Although it is about 50 ° C., it is also used to block the inflow of heat from the surroundings of the freezing chamber 3. As a result, when returning to the regenerative heat exchanger 242, the temperature rises to about −20 ° C. Since the return air from the refrigeration chamber 3 contains little water vapor, the expansion turbine 23
Since only fine particles of mist ice come out at the outlet 1, the continuous removal of water from the refrigerant air is not particularly required.

In the above embodiment, when the power output of the gas turbine 1 is 60 kW, the exhaust flow rate of the gas turbine 1 introduced into the boiler 4 is about 0.6 kg / sec, and the exhaust temperature is about 250 ° C. 4 is supplied to the steam turbine 211 at a temperature of 200 ° C. and 4 atm (absolute pressure) of about 120 kg / hr.
The power of No. 11 is about 8.5 kw, the refrigerant air flow rate in the air refrigeration cycle is about 10.7 kg / min, the refrigerant air pressure after compression by the first compressor 212 is about 1.4 atm (absolute pressure), and the second compressor is 232, the refrigerant air pressure after compression is about 2.0 atm (absolute pressure), and the expansion turbine 231
The refrigerant air temperature at the inlet is about −10 ° C., and the expansion turbine 2
The refrigerant air temperature at the outlet of the outlet 31 is about -52 ° C, and the cooling capacity until the expansion air rises to -30 ° C is 3.9 kw.
(56 kcal / min). Gas turbine 1
If the output of the electric power is set to 120 kW, the refrigerant air flow rate in the air refrigeration cycle is set to twice that in the case of 60 kW, and the compression ratio by each of the compression devices 212 and 232 is the same as that in the case of 60 kW, compared to the case of 60 kW , The exhaust flow rate of the gas turbine 1 introduced into the boiler 4, the steam flow rate supplied from the boiler 4 to the steam turbine 211, the power of the steam turbine 211, and the cooling capacity are doubled, and the others are the same. The power output of the gas turbine 1 is set to 120 kw, the refrigerant air flow rate in the air refrigeration cycle is set to 60 kw, the refrigerant air pressure after compression by the first compressor 212 is about 1.9 atm (absolute pressure), and the second Compression device 232
If the refrigerant air pressure after compression is about 3.5 atm (absolute pressure), the flow rate of the exhaust gas of the gas turbine 1 introduced into the boiler 4 and the flow rate of the exhaust gas from the boiler 4 to the steam turbine 211 are smaller than the case of 60 kW. Steam flow, steam turbine 2
11 is doubled, and even if the refrigerant air temperature at the inlet of the expansion turbine 231 is about 20 ° C. which is room temperature, the expansion turbine 2
The refrigerant air temperature at the outlet 31 is about -63 ° C, and the cooling capacity until the expanded air rises to -30 ° C is about 5.9 kw (84 kcal / min). In this case, it can be said that cooling to room temperature or lower by the return air is unnecessary. The power output of the gas turbine 1 is set to 120 kW.
In this case, two gas turbines each having an output of 60 Kw may be connected and used. In addition, the first compression device 212 and the second
The compression device 232 is constituted by a blower in the above embodiment, but may be constituted by a compressor when the compression ratio of the refrigerant air is made to be twice or more.

According to the above configuration, the steam turbine 211 is driven by the superheated steam generated by the boiler 4 by the exhaust heat of the gas turbine 1, and the first compression device 212 is driven by the steam turbine 211, so that the gas turbine 1 The high-temperature exhaust gas from the refrigerator is used for the heat demand of the refrigerator 2. Accordingly, a cogeneration system that extracts electric energy from the gas turbine 1 via the generator 16 and extracts heat energy from the exhaust gas of the gas turbine 1
Combination with the refrigerator 2 makes it possible to reduce fluctuations in the heat load and effectively use energy. Furthermore, since the high-temperature exhaust heat of the gas turbine 1 is used for generating superheated steam by the boiler 4, the exhaust heat can be effectively used in a cascade downstream of the boiler 4, so that a highly efficient cogeneration system is constructed. Can be. By adopting a micro gas turbine as the gas turbine 1, it can be used in a small-scale food processing plant or the like, and can contribute to society by reducing energy consumption by the cogeneration system. In the boiler 4, pressurized water heated by heat exchange with the refrigerant air in the first heat exchanger 221 is heated by exhaust heat from the gas turbine 1 to generate superheated steam, thereby improving energy efficiency. Can be. Further, by performing heat exchange between the refrigerant air and the low-temperature air in the regenerative heat exchanger 242, the energy efficiency can be further improved.

FIG. 3 shows a refrigeration system according to a second embodiment of the present invention. The difference from the first embodiment is that the rotating part of the first compressor 212, the rotating part of the second compressor 232, the rotating part of the steam turbine 211, and the rotating part of the expansion turbine 231 are formed by a single rotating shaft 250. The first compression device 212 and the second compression device 2
32 is driven by the steam turbine 211 and the expansion turbine 231. Thereby, the first compression device 2
12 and the compression ratio of the second compression device 232
11 and the expansion turbine 231 can be freely selected and optimized without being limited. Other parts are the same as those in the first embodiment, and the same parts are denoted by the same reference numerals.

The present invention is not limited to the above embodiments.
For example, in the first embodiment, the first compression device may be driven by an expansion turbine, and the second compression device may be driven by a steam turbine. In each of the above embodiments, the second cooling device, or both the first cooling device and the second cooling device, may include a heat exchanger that exchanges heat between the pressurized water and the refrigerant air. Further, before the exhaust gas from the gas turbine 1 is introduced into the boiler 4, FIGS.
As shown by the broken line in FIG.
Alternatively, an auxiliary burner may be provided to reheat the exhaust gas. Since the exhaust of the gas turbine 1 contains about 15 to 16% of oxygen, the amount of steam generated in the boiler 4 can be increased by reheating. Thereby, it is possible to cope with a case where a large amount of steam is required for heating the boiling pot while the refrigerator 2 is operating.
In each of the above embodiments, the compression and cooling of the refrigerant air is performed by 2 times.
However, the compression and cooling of the refrigerant air may be performed in a single stage by using a single compression device and cooling device in the refrigerator. In this case, the compression device is used in both the steam turbine and the expansion turbine. It may be driven, or when a large refrigeration capacity is not required, it may be driven only by the steam turbine, and the output of the expansion turbine may be used for, for example, power generation.

[0024]

According to the present invention, a cogeneration system using a gas turbine can be effectively used even in a food processing plant or the like where the heat demand is small, in combination with a refrigerator capable of performing a refrigeration process using a cryogenic air flow. In addition, it is possible to provide a refrigeration system capable of achieving an energy reduction effect.

[Brief description of the drawings]

FIG. 1 is a configuration explanatory view of a refrigeration system according to a first embodiment of the present invention.

FIG. 2 is a perspective view of a main part of the refrigeration system according to the first embodiment of the present invention.

FIG. 3 is a configuration explanatory view of a refrigeration system according to a second embodiment of the present invention.

[Explanation of symbols]

 DESCRIPTION OF SYMBOLS 1 Gas turbine 2 Refrigerator 211 Steam turbine 212 First compression device 22 First cooling device 221 First heat exchanger 231 Expansion turbine 232 Second compression device 24 Second cooling device 4 Boiler

──────────────────────────────────────────────────続 き Continued on the front page (51) Int.Cl. ⁷ Identification symbol FI Theme coat ゛ (Reference) F02G 5/04 F02G 5/04 CGH F22B 1/18 F22B 1/18 R F25B 9/00 301 F25B 9 / 00 301

Claims (5)

[Claims] A gas turbine, a boiler that generates superheated steam by exhaust heat of the gas turbine, and a refrigerator that constitutes an air refrigeration cycle, wherein the refrigerator is driven by the superheated steam generated by the boiler. A steam turbine to be cooled, a refrigerant air compression unit, a compressed refrigerant air cooling unit, and an expansion turbine that expands the cooled refrigerant air to produce low-temperature air. A refrigeration system whose output is used to compress the refrigerant air. 2. The refrigeration system according to claim 1, wherein the output of the expansion turbine is used for compressing the refrigerant air. 3. The apparatus has a first compression device and a second compression device as its compression means, and has a first cooling device and a second cooling device as its cooling means, and is compressed by the first compression device. The refrigerant air is cooled by the first cooling device, the refrigerant air cooled by the first cooling device is compressed by the second compression device, and the refrigerant air compressed by the second compression device is cooled by the second cooling device. The refrigerant air cooled by the second cooling device is expanded by the expansion turbine, and one of the first compression device and the second compression device is driven by the steam turbine, and the first compression device and the second compression device are driven by the steam turbine. The refrigeration system according to claim 2, wherein the other of the two compression devices is driven by the expansion turbine. 4. A compression means having a first compression device and a second compression device, and a cooling device having a first cooling device and a second cooling device, and compressed by the first compression device. The refrigerant air is cooled by the first cooling device, the refrigerant air cooled by the first cooling device is compressed by the second compression device, and the refrigerant air compressed by the second compression device is cooled by the second cooling device. The refrigerant air cooled by the second cooling device is expanded by the expansion turbine, and the first compression device and the second compression device are driven by the steam turbine and the expansion turbine. Refrigeration system. 5. A heat exchanger for cooling the compressed refrigerant air by performing heat exchange between the pressurized water and the compressed refrigerant air, wherein the boiler has a heat exchanger. The superheated steam is generated by heating pressurized water heated by heat exchange with refrigerant air by the exhaust heat.
The refrigeration system according to any one of the above-mentioned items.