JP5305099B2 - Water cooling equipment - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To effectively utilize heat of a condenser in a water cooling device using a refrigerating machine. <P>SOLUTION: A steam compressor 4 sucks/exhausts gas in a water storage tank 8 to decompress inside the water storage tank 8 and compresses water vapor sucked from the water storage tank 8 to discharge it. A heat pump 6 is composed of a coolant compressor 5, the condenser 7, an expansion valve 25, and an evaporator 26 sequentially connected in a circular pattern. The condenser 7 is configured to be an indirect heat exchanger for heat-exchanging between coolant of the heat pump 6 and water in the water storage tank 8. The evaporator 26 is configured to be an indirect heat exchanger for heat-exchanging between the coolant of the heat pump 6 and water to an air conditioner. <P>COPYRIGHT: (C)2011,JPO&amp;INPIT

Description

  The present invention relates to a water cooling apparatus that obtains cold water for cooling an engine or cooling waste water from a factory or the like in addition to air conditioning and food cooling.

  Conventionally, as disclosed in Patent Document 1 below, a water cooling device that obtains cold water using a refrigerator is known. However, since the condenser of the refrigerator disposes a large amount of heat in the atmosphere, there is room for improvement in this respect. Even if it is attempted to obtain steam using heat radiation from the condenser of the refrigerator, in the case of a refrigerator using a refrigerant other than water, the critical temperature of the refrigerant is in a low temperature region, so the obtained steam temperature is limited. .

JP 2007-292351 A

  The problem to be solved by the present invention is to improve the energy efficiency by effectively utilizing the heat of the condenser in a water cooling device using a refrigerator. It is another object of the present invention to obtain steam in a wide temperature range while preventing the apparatus from becoming large.

The present invention has been made to solve the above-mentioned problems, and the invention according to claim 1 is characterized in that the gas in the water storage section is sucked and discharged to depressurize the water storage section and the water vapor sucked from the water storage section. And a heat pump configured by sequentially connecting a refrigerant compressor, a condenser, an expansion valve, and an evaporator in an annular shape, and the condenser includes the refrigerant of the heat pump and the water of the water storage section. The evaporator is an indirect heat exchanger between the refrigerant of the heat pump and the water to be cooled, and the steam from the steam compressor is supplied to a water supply tank to the boiler. a water cooler, characterized in that that.
The invention according to claim 2 is a vapor compressor that sucks and discharges the gas in the water storage unit and depressurizes the water storage unit and compresses water vapor sucked from the water storage unit, a refrigerant compressor, a condenser, and an expansion A heat pump configured such that a valve and an evaporator are sequentially connected in an annular manner, the condenser being an indirect heat exchanger between the refrigerant of the heat pump and the water of the water storage unit, and the evaporator being the heat pump Indirect heat exchanger between the refrigerant and water to be cooled, the steam from the steam compressor is indirectly heat exchanged with make-up water and supplied to the water storage unit, and the make-up water is supplied to the steam compressor It is the water cooling device characterized by being vaporized by indirect heat exchange with the steam from.
The invention according to claim 3 is a vapor compressor that sucks and discharges the gas in the water storage unit and depressurizes the water storage unit and compresses the water vapor sucked from the water storage unit, a refrigerant compressor, a condenser, and an expansion A heat pump configured such that a valve and an evaporator are sequentially connected in an annular manner, the condenser being an indirect heat exchanger between the refrigerant of the heat pump and the water of the water storage unit, and the evaporator being the heat pump Indirect heat exchanger between the refrigerant and water to be cooled, the steam from the steam compressor is indirectly heat exchanged with make-up water and supplied to the water storage unit, and the make-up water is supplied to the steam compressor The water cooling device is characterized by being heated by indirect heat exchange with steam from and supplied to a water supply tank to a boiler.
According to a fourth aspect of the present invention, there is provided a steam compressor, a refrigerant compressor, a condenser, and an expansion unit that sucks and discharges the gas in the water storage unit and depressurizes the water storage unit and compresses the water vapor sucked from the water storage unit. A heat pump configured such that a valve and an evaporator are sequentially connected in an annular manner, the condenser being an indirect heat exchanger between the refrigerant of the heat pump and the water of the water storage unit, and the evaporator being the heat pump An indirect heat exchanger between the refrigerant and water to be cooled, and one or both of the steam compressor and the refrigerant compressor are driven by a steam engine that generates power using steam, and the steam compressor The steam from is supplied to the water storage part through indirect heat exchange with make-up water, and the make-up water is vaporized by indirect heat exchange with steam from the steam compressor and used in the steam engine. The steam It is supplied to a supply point or heated by indirect heat exchange with steam from the steam compressor and supplied to a water supply tank to a boiler that supplies steam to the steam engine. Water cooling device.

According to invention of Claims 1-4 , water (factory waste water etc.) can be cooled using the evaporator of a heat pump. On the other hand, the water in the water storage section can be heated using the condenser of the heat pump, and the water in the water storage section can be vaporized by the steam compressor . The water in the water storage section is heated by heat exchange with the refrigerant of the heat pump, but is also cooled by decompression by the steam compressor, so heat exchange between the water and the refrigerant in the condenser is effective.
According to the first aspect of the present invention, steam obtained by the steam compressor can be blown into the feed water tank to preheat boiler feed water.
According to invention of Claim 2, makeup water can be vaporized using the steam obtained by a steam compressor, and the steam can be utilized in various steam utilization apparatuses. Compared with the case where the steam from the steam compressor is sent directly to the steam utilization equipment, it is easier to maintain the quality of the steam sent to the steam utilization equipment.
According to the third aspect of the present invention, the boiler feed water can be preheated using the steam obtained by the steam compressor. Compared with the case where the steam from the steam compressor is sent directly to the water supply tank, the water quality can be easily managed.
According to the fourth aspect of the present invention, the driving cost of the steam compressor can be reduced by using the steam engine as compared with the case of using only the electric motor. In addition, makeup water that is indirectly heat-exchanged with steam from the steam compressor is either vaporized and supplied to a location where steam after use is supplied by the steam engine, or heated to supply steam to the steam engine. Since it is supplied to the water supply tank to the boiler to be supplied, it is more efficient. In addition, it is easier to manage steam or water than when steam from the steam compressor is sent directly to the steam utilization device or steam from the steam compressor is sent directly to the water supply tank.

The invention according to claim 5 further includes a water storage tank in which water is stored, the water storage tank being the water storage section, and the condenser is an indirect heat exchanger having a refrigerant flow path and a water flow path. They are, wherein the refrigerant passage, the refrigerant of the heat pump is passed, between the water storage tank and the water flow path, of claims 1 to 4, water in the water storage tank is characterized in that it is circulated It is a water cooling device given in any 1 paragraph .

According to invention of Claim 5 , a water storage tank is provided separately from a condenser. The saturated steam temperature in the water tank can be adjusted by a steam compressor, but if the temperature of the water heated by the condenser is higher than the saturated steam temperature in the water tank, flash steam is generated in the water tank. And the generation of steam can be promoted.

Invention of Claim 6 is comprised from the hollow tank and the pipe line provided in the inside of the said condenser, The refrigerant | coolant of the said heat pump is let through one side of the said hollow tank and the said pipe line, The water cooling device according to any one of claims 1 to 4, wherein water is stored on the other side to serve as the water storage section.

According to the sixth aspect of the present invention, a water cooling device can be realized with a simple configuration without separately providing a water storage tank.

In the invention according to claim 7 , water is stored in the hollow tank, while the refrigerant of the heat pump is passed through the conduit, and water is stored halfway in the hollow tank, The pipe line is divided into a gas phase part, and at least a part of the pipe line is disposed in the gas phase part in the hollow tank. The water cooling device according to claim 6 , wherein water is sprayed.

According to invention of Claim 7 , generation | occurrence | production of a vapor | steam can be further accelerated | stimulated by spraying water toward the pipe line through which a refrigerant | coolant passes.

In the invention according to claim 8 , the condenser is an indirect heat exchanger having a refrigerant flow path and a water flow path, the refrigerant of the heat pump is passed through the refrigerant flow path, and the water flow path is passed through the water flow path. The water cooling device according to any one of claims 1 to 4, wherein water is stored to serve as the water storage section.

According to invention of Claim 8 , a water cooling device is realizable with a simple structure, without providing a water storage tank separately.

The invention according to claim 9 further includes one or a plurality of additional heat pumps in addition to the first heat pump as the heat pump, and the evaporator of the first heat pump attempts to cool with the refrigerant of the first heat pump. Instead of being an indirect heat exchanger with water, it is also an indirect heat exchanger between the refrigerant of the first heat pump and the refrigerant of the uppermost additional heat pump, and is also a condenser of the uppermost additional heat pump. , evaporator of the additional heat pump lowest stage, any one of the preceding claims, characterized in that the indirect heat exchanger with water to be cooled and refrigerant of the additional heat pump of the lowermost It is a water cooling device as described in above.

According to invention of Claim 9 , a compression ratio can be suppressed by making a heat pump into multiple steps | paragraphs, and structures, such as a compressor and an evaporator of a heat pump of each step | paragraph, can be reduced in size.

Invention of claim 10, the vapor is compressed by the vapor compressor may be any of claims 1 to 9, characterized in that the water injection in the steam compressor itself or front or rear stage part 1 It is a water cooling device as described in the paragraph.

According to invention of Claim 10 , desired steam can be obtained by adjusting the amount of water injection in a steam compressor or its front | former stage or back | latter stage.

Furthermore, in the invention described in claim 11 , the steam compressor sucks and discharges the gas in the water storage section through the steam separator, and the water separated by the steam separator is supplied to the boiler. The water cooling device according to any one of claims 1 to 10 , wherein the water cooling device is supplied to a water supply tank or indirectly exchanged with water supplied to a boiler and returned to the water storage section.

According to the eleventh aspect of the present invention, steam and hot water can be obtained from the condenser of the heat pump, and the hot water can be used to preheat water to the boiler.

  ADVANTAGE OF THE INVENTION According to this invention, in the water cooling apparatus using a refrigerator, the effective use of the heat of a condenser can be aimed at and energy efficiency can be improved. Moreover, by vaporizing water after preheating with a heat pump with a steam compressor, steam in a wide temperature range can be obtained, and an increase in size of the apparatus can be prevented.

It is the schematic which shows an example of the vapor | steam utilization system to which Example 1 of the water cooling device of this invention was applied. It is the schematic which shows an example of the vapor | steam utilization system to which Example 2 of the water cooling device of this invention was applied. It is the schematic which shows an example of the vapor | steam utilization system to which Example 3 of the water cooling device of this invention was applied. It is the schematic which shows an example of the vapor | steam utilization system to which Example 4 of the water cooling device of this invention was applied. It is the schematic which shows an example of the vapor | steam utilization system to which Example 5 of the water cooling device of this invention was applied. It is the schematic which shows an example of the steam utilization system to which Example 6 of the water cooling device of this invention was applied, and one part is abbreviate | omitted and shown. It is the schematic which shows an example of the steam utilization system to which Example 7 of the water cooling device of this invention was applied, and one part is abbreviate | omitted and shown. It is the schematic which shows an example of the steam utilization system to which Example 8 of the water cooling device of this invention was applied, and one part is abbreviate | omitted and shown. It is the schematic which shows an example of the vapor | steam utilization system to which Example 9 of the water cooling device of this invention was applied, and one part is abbreviate | omitted and shown. It is the schematic which shows an example of the vapor | steam utilization system to which Example 10 of the water cooling device of this invention was applied, and one part is abbreviate | omitted and shown. It is the schematic which shows an example of the steam utilization system to which Example 11 of the water cooling device of this invention was applied, and one part is abbreviate | omitted and shown. It is the schematic which shows an example of the steam utilization system to which Example 12 of the water cooling device of this invention was applied, and one part is abbreviate | omitted and shown. It is a figure which shows the modification of the water cooling device of FIG. 1, and one part is abbreviate | omitted and shown. It is a figure which shows the other modification of the water cooling apparatus of FIG. 1, and one part is abbreviate | omitted and shown. It is a figure which shows another modification of the water-cooling apparatus of FIG. 1, and one part is abbreviate | omitted and shown.

  Hereinafter, specific embodiments of the present invention will be described in detail with reference to the drawings.

  FIG. 1 is a schematic diagram showing an example of a steam utilization system to which the first embodiment of the water cooling device of the present invention is applied. The steam utilization system 1 includes a boiler 2, a steam engine 3 that generates power using steam from the boiler 2, a steam compressor 4 and a refrigerant compressor 5 that are driven by the steam engine 3, and refrigerant compression A heat pump 6 including the machine 5 and a water storage tank 8 capable of circulating water between the condenser 7 of the heat pump 6 are provided.

  If the boiler 2 is a steam boiler, the structure in particular will not be ask | required. The boiler 2 is supplied with water from the water supply tank 9 via the water supply channel 10. A water supply pump 11 is provided in the water supply path 10, and the presence or absence of water supply to the boiler 2 is switched depending on whether or not the water supply pump 11 is activated. The water supply tank 9 is appropriately supplied with water from the make-up water channel 12 and maintained at a desired water level. The replenishment water channel 12 to the water supply tank 9 is provided with a pure water device or a soft water device (not shown), and pure water or soft water is supplied to the water supply tank 9. In addition, you may collect | recover drains from the steam utilization apparatus in the water supply tank 9. FIG.

  The water supplied to the boiler 2 is vaporized by the boiler 2. The steam from the boiler 2 is sent to one or a plurality of various steam utilization devices (not shown) via a steam header (not shown) as desired.

  One type of steam utilization equipment is a steam engine 3. The steam engine 3 is not particularly limited in configuration as long as it is a prime mover that generates power using steam, and is, for example, a screw steam engine. A screw-type steam engine is configured by providing a screw rotor in a hollow casing so as to mesh with each other. Steam is introduced between the screw rotors to rotate the screw rotors. And rotation power is output by rotation of this screw rotor. During this time, the steam is expanded and depressurized by passing through the steam engine 3.

  Steam from the boiler 2 is supplied to the steam engine 3 through a steam supply path 13. A steam supply valve 14 is provided in the steam supply path 13 to the steam engine 3. By adjusting the opening / closing or opening of the steam supply valve 14, the presence or absence of the operation of the steam engine 3 or the output can be adjusted.

  The steam engine 3 is a device that obtains a rotational driving force by the supplied steam. In the steam engine 3, the steam is expanded and decompressed. Therefore, the steam engine 3 functions not only as a drive source for the compressors 4 and 5 but also as a pressure reducing valve. Thereby, the steam after being used in the steam engine 3 can be used as it is in various steam utilizing devices as the steam after passing through the pressure reducing valve. Therefore, the steam after use in the steam engine 3 is sent to the steam utilization device via the exhaust steam path 15.

  The steam supply path 13 to the steam engine 3 and the exhaust steam path 15 from the steam engine 3 are connected by a bypass path 16. The bypass passage 16 is provided with a bypass valve 17. The bypass valve 17 is preferably a self-reducing pressure reducing valve, and mechanically adjusts the opening degree by itself so as to maintain the secondary side (steam downstream side) steam pressure at a predetermined level. If such a bypass path 16 is provided, steam can be stably supplied to the steam utilization device on the secondary side of the bypass valve 17. For example, even when the steam supply valve 14 is closed and the steam engine 3 is stopped, the steam can be supplied to the steam utilization device via the bypass 16.

  The vapor compressor 4 is not particularly limited in its configuration, and the number of stages is not limited. For example, an impeller type (for example, axial flow type or centrifugal type) compressor and a positive displacement type (for example, screw type) compressor may be provided at the subsequent stage. The steam compressor 4 sucks and discharges the gas in the water storage tank 8 through the suction path 18 to reduce the pressure in the water storage tank 8. By reducing the pressure in the water storage tank 8, the water in the water storage tank 8 is boiled. The steam compressor 4 sucks and compresses the water vapor resulting from the boiling and flash steam described later and discharges the steam. The steam discharged from the steam compressor 4 is sent to various steam utilizing devices (steam utilizing devices other than the steam engine 3 that drives the steam compressor 4) via the discharge path 19 and used. In the illustrated example, the discharge passage 19 joins the exhaust steam passage 15 from the steam engine 3 and supplies steam to the steam utilization device. That is, it can be said that the discharge path 19 from the steam compressor 4 is a steam supply path to the steam utilization equipment.

  The water vapor from the water storage tank 8 is compressed by the steam compressor 4 and is essentially superheated steam. Accordingly, superheated steam may be obtained from the steam compressor 4, but water injection is appropriately performed in the steam compressor 4 itself or in the preceding stage (the suction side to the steam compressor 4) or the subsequent stage (the discharge side from the steam compressor 4). Then, saturated steam may be obtained. Similarly, superheated steam having a desired superheat degree may be obtained by appropriately injecting water in the steam compressor 4 itself or in the preceding stage or the subsequent stage thereof. That is, desired steam can be obtained by adjusting the water injection amount. However, typically, it is set as the structure which obtains saturated steam by the water injection to the steam compressor 4 or its front | former stage or back | latter stage. At this time, it is preferable to pour water before the steam compressor 4, but here, for convenience of explanation, it is assumed that water is poured into the steam compressor 4 as shown as a water filling channel 20 in FIG. 1. A water injection valve 21 is provided in the water injection channel 20, and the water injection amount to the steam compressor 4 can be adjusted by the water injection valve 21.

  By the way, the water storage tank 8 is a hollow container that can withstand the decompression of the internal space, and functions as a water storage section. The water storage tank 8 is appropriately supplied with water from the replenishment channel 22 and is maintained at a desired water level. For example, the water level sensor 23 provided in the water storage tank 8 controls the refill valve 24 so that the water level in the water storage tank 8 is maintained as desired. In this case, considering that the water in the water storage tank 8 can be vaporized by the steam compressor 4 and used in steam utilization equipment, then returned to the water supply tank 9 as drain and supplied to the boiler 2. The water in the water storage tank 8 is preferably pure water or soft water. For the same reason, it is preferable that the water poured in the steam compressor 4 is also pure water or soft water.

  The water storage tank 8 stores water until midway, and is divided into a gas phase portion and a liquid phase portion. The gas phase portion of the water storage tank 8 is connected to the suction port of the steam compressor 4 through the suction path 18 as described above. Thereby, the gas in the water storage tank 8 can be sucked and discharged by the vapor compressor 4, and the pressure in the water storage tank 8 can be reduced. When the inside of the water storage tank 8 is depressurized, the water stored in the water storage tank 8 is promoted to evaporate, and the stored water is cooled by the latent heat of vaporization. Therefore, as will be described later, heat exchange between the water in the water storage tank 8 and the refrigerant in the heat pump 6 is effectively performed in the condenser 7.

  The steam compressor 4 and the refrigerant compressor 5 are driven by the steam engine 3. In the drawing, the output shaft of the steam engine 3 and the input shafts of the compressors 4 and 5 are shown as a common shaft, but it goes without saying that they may be separate shafts via a reduction gear or the like. The compressors 4 and 5 may be driven by an electric motor instead of or in addition to the steam engine 3.

  The heat pump 6 is configured by sequentially connecting the refrigerant compressor 5, the condenser 7, the expansion valve 25, and the evaporator 26 in an annular shape. The refrigerant compressor 5 compresses the refrigerant into a high-temperature and high-pressure gas. The vaporized refrigerant from the refrigerant compressor 5 is sent to the condenser 7. The condenser 7 condenses and liquefies the vaporized refrigerant from the refrigerant compressor 5. The liquefied refrigerant from the condenser 7 is sent to the expansion valve 25. The expansion valve 25 decreases the pressure and temperature of the refrigerant by allowing the liquefied refrigerant from the condenser 7 to pass therethrough. The evaporator 26 evaporates the refrigerant from the expansion valve 25.

  The heat pump 6 uses water other than water as a refrigerant. The refrigerant of the heat pump 6 has a lower critical temperature than water, and is a natural refrigerant such as a chlorofluorocarbon refrigerant, a hydrocarbon refrigerant, ammonia or carbon dioxide.

  The condenser 7 will be described in more detail. The condenser 7 is an indirect heat exchanger that has a refrigerant flow path and a water flow path and exchanges heat without mixing the refrigerant and water. The refrigerant from the refrigerant compressor 5 passes through the refrigerant flow path of the condenser 7 and is sent to the expansion valve 25. On the other hand, the water in the water storage tank 8 is returned to the water storage tank 8 through the water flow path of the condenser 7.

  Specifically, the water storage tank 8 and the condenser 7 are connected via a tank water supply path 27 and a tank water return path 28. A tank water supply pump 29 is provided in the tank water supply path 27. Accordingly, the water in the water storage tank 8 is supplied to the condenser 7 through the tank water supply path 27, passes through the water flow path of the condenser 7, and is returned to the water storage tank 8 through the tank water return path 28. . Thus, in the condenser 7, while cooling a refrigerant | coolant, water heating can be aimed at.

  By the way, the water tank 8 is depressurized by a steam compressor, while the water heated in the condenser 7 is returned to the water tank 8, so-called flash steam is generated in the water tank 8. At this time, if a pressure loss part such as a nozzle tip is provided in the middle of the tank water return path 28 or at the opening to the water storage tank 8, flash steam can be generated only on the water storage tank 8 side. However, installation of such a pressure loss part is arbitrary. The warm water from the tank water return passage 28 may be discharged to the liquid phase part of the water storage tank 8, but is preferably discharged to the gas phase part of the water storage tank 8 in order to generate a large amount of flash vapor. At this time, if sprayed on the gas phase portion of the water storage tank 8, evaporation is further promoted.

  The evaporator 26 will be described in more detail. The evaporator 26 is also an indirect heat exchanger that has a refrigerant flow path and a water flow path and exchanges heat without mixing the refrigerant and water. The refrigerant from the expansion valve 25 passes through the refrigerant flow path of the evaporator 26 and is sent to the refrigerant compressor 5. On the other hand, water is passed through the water flow path of the evaporator 26, and the water is used in various coolers (not shown) such as an air conditioner and a food machine. For example, an indoor unit (fan coil unit) of an air conditioner is used as a cooler, and water from the evaporator 26 is supplied to the cooler via a cold water supply path 30, and water after use in the cooler is a cold water return path. It is returned to the evaporator 26 via 31. The cold water supply path 30 is provided with a cold water feed pump 32, and the presence or absence of the operation of the cold water feed pump 32 can switch the presence or absence of water circulation between the evaporator 26 and the cooler. The flow rate of water supplied from the evaporator 26 to the cooler is adjusted by controlling the inverter of the cold water feed pump 32 or by adjusting the opening of the flow rate adjusting valve provided in the cold water supply path 30 or the cold water return path 31. can do.

  By the way, in addition to circulating water between the evaporator 26 and the cooler, the cold water from the evaporator 26 may be disposable in the cooler. That is, the cold water return path 31 may be used as a water supply path from a water supply source, the water supply may be cooled by the evaporator 26 to be cold water, and the cold water may be supplied to the cooler via the cold water supply path 30. The cold water is used for cooling the food, but the used water does not have to be returned to the evaporator 26.

  The water cooling device further includes a controller (not shown). In this embodiment, the controller includes a steam supply valve 14, a water injection valve 21, a supplementary water valve 24, a heat pump 6 (particularly, the refrigerant compressor 5 and the expansion valve 25), a tank water feed pump 29, a cold water feed pump 32, and the like. It is connected to various sensors and controls each means based on detection signals from the sensors. For example, the controller controls the temperature and / or flow rate of the chilled water supplied from the evaporator 26 to the cooler while performing inverter control on the chilled water feed pump 32, thereby making the temperature and flow rate of the chilled water supplied to the cooler desired maintain.

  The detection target by the sensor includes the flow rate of the steam supplied from the water storage tank (water storage unit) 8 to the steam compressor 4, the pressure or temperature of the steam discharged from the steam compressor 4, and the supply from the evaporator 26 to the cooler. The temperature of the chilled water, the flow rate of the chilled water supplied from the evaporator 26 to the cooler, the temperature in the water storage tank 8 (the water temperature in the water storage tank 8 may be the pressure, not the temperature in the water storage tank 8). Any one or more of a flow rate of makeup water supplied to the water storage tank 8 and a water level in the water storage tank 8 are employed.

  On the other hand, control targets include a steam compressor 4 (specifically, the amount of water injected into the steam compressor 4), a refrigerant compressor 5 (specifically, the capacity of the refrigerant compressor 5), an expansion valve 25, and a cold water feed pump. 32, one or more of the tank water feed pump 29, the refill valve 24, and the like are employed.

  According to the water cooling apparatus of the present embodiment, since the compressors 4 and 5 are driven by the steam engine 3, the running cost can be reduced. Further, by using the condenser 7, the water storage tank 8, and the steam compressor 4, steam can be generated with waste heat at the time of cold water production.

  Moreover, according to the present Example, since the water after preheating with the heat pump 6 is vaporized with the steam compressor 4, the vapor | steam of a high temperature area | region can be obtained rather than the case where only a heat pump is used. That is, for example, even if an attempt is made to obtain steam by using heat radiation of a refrigerator condenser by a chlorofluorocarbon refrigerant (for example, R-245fa), since the critical temperature of the refrigerant is low (about 150 ° C.), steam in a low temperature region (Practically, about 110 to 130 ° C.) is the limit, but according to the present embodiment, water after preheating is vaporized by the steam compressor 4 by the heat pump 6, and therefore in a higher temperature region. Steam can also be obtained.

  In addition, according to the present embodiment, since the water preheated by the heat pump 6 is vaporized by the steam compressor 4, the configuration of the entire apparatus such as the steam compressor 4 is large compared to the case where there is no preheating by the heat pump 6. There is no risk of conversion. When other than water (for example, chlorofluorocarbon refrigerant) is used as the refrigerant of the heat pump 6, the density is relatively large compared to water, so the compression ratio is small, and there is no fear that the equipment such as the compressor will be enlarged. As such, steam in the high temperature region cannot be obtained. On the other hand, when water is used as the refrigerant of the heat pump 6, steam in the high temperature region can be obtained as described above. However, since the density is relatively small, the compression ratio must be increased, such as a compressor or an evaporator. There is an inconvenience that the equipment becomes larger. However, in this embodiment, a heat pump 6 using a refrigerant other than water and a steam compressor 4 that evaporates water after preheating by the heat pump 6 are used. By using a refrigerant other than water in the low temperature region and using water in the high temperature region, it is possible to obtain steam in the high temperature region while preventing an increase in the size of the apparatus.

  FIG. 2 is a schematic view showing an example of a steam utilization system to which the second embodiment of the water cooling device of the present invention is applied. The water cooling device and the steam utilization system 1 of the second embodiment are basically the same as those of the first embodiment. Therefore, in the following description, differences between the two will be mainly described, and corresponding portions will be described with the same reference numerals.

  In the said Example 1, the steam from the steam compressor 4 was sent to the steam utilization apparatus, and was used, but in this Example 2, the steam from the steam compressor 4 is in the feed water tank 9 of the boiler 2. Infused. Thereby, preheating of the feed water of the boiler 2 can be aimed at. Supplying the steam from the steam compressor 4 to the water supply tank 9 is not limited to the first embodiment, and can be similarly applied to each of the embodiments after the fifth embodiment described later. Other configurations and controls are the same as those in the first embodiment, and a description thereof will be omitted.

  FIG. 3 is a schematic view showing an example of a steam utilization system to which the third embodiment of the water cooling device of the present invention is applied. The water cooling device and the steam utilization system 1 of the third embodiment are basically the same as those of the first embodiment. Therefore, in the following description, differences between the two will be mainly described, and corresponding portions will be described with the same reference numerals.

  In the first embodiment, the steam from the steam compressor 4 is sent to a steam utilization device and used. In this third embodiment, the steam from the steam compressor 4 is an indirect heat exchanger with make-up water. Through 33, the water is supplied to a water storage tank 8 as a water storage section. In the indirect heat exchanger 33, makeup water (pure water or soft water) is heated and vaporized by the steam from the steam compressor 4. Then, the steam joins with the exhaust steam path 15 from the steam engine 3 and is sent to the steam utilization device. Compared with the case where the steam from the steam compressor 4 is sent directly to the steam utilization device, the management of the steam quality becomes easier.

  In the case of the third embodiment, the water in the water storage tank 8 flows in a closed circuit. Therefore, when water is injected in the steam compressor 4, it is preferable that water can be appropriately drained from the water storage tank 8 or the like. Conversely, the water replenishment channel 22 may be provided in the water storage tank 8 as in the first embodiment. Vaporizing the make-up water with the steam from the steam compressor 4 is not limited to the first embodiment, and can be similarly applied to each of the embodiments after the fifth embodiment described later. Other configurations and controls are the same as those in the first embodiment, and a description thereof will be omitted.

  FIG. 4 is a schematic diagram illustrating an example of a steam utilization system to which a water cooling device according to a fourth embodiment of the present invention is applied. The water cooling device and the steam utilization system 1 of the fourth embodiment are basically the same as those of the first embodiment. Therefore, in the following description, differences between the two will be mainly described, and corresponding portions will be described with the same reference numerals.

  In the first embodiment, the steam from the steam compressor 4 is sent to the steam utilization device and used. In the fourth embodiment, the steam from the steam compressor 4 is an indirect heat exchanger with make-up water. Through 33, the water is supplied to a water storage tank 8 as a water storage section. In the indirect heat exchanger 33, makeup water (pure water or soft water) is heated with the steam from the steam compressor 4. The water heated in this way is supplied to the water supply tank 9 of the boiler 2. In this way, it is possible to preheat water supplied to the boiler 2. Compared with the case where the steam from the steam compressor 4 is sent directly to the water supply tank 9, the water quality can be easily managed.

  In the case of the present Example 4, since the water in the water storage tank 8 flows through a closed circuit, when inject | pouring water in the steam compressor 4, it is good to make it possible to drain appropriately from the water storage tank 8 grade | etc.,. Conversely, the water replenishment channel 22 may be provided in the water storage tank 8 as in the first embodiment. Using the indirect heat exchanger 33 to preheat the feed water to the boiler 2 with steam from the steam compressor 4 is not limited to the first embodiment, but also in each of the embodiments after the fifth embodiment described later. Applicable. Other configurations and controls are the same as those in the first embodiment, and a description thereof will be omitted.

  By the way, when the water in the water storage tank 8 is caused to flow in a closed circuit as in the fourth embodiment and the third embodiment, the refrigerant pipe of the heat pump 6 should be cracked, and the leaked refrigerant is turned into water. Even if mixed, the water is not directly used steam, so inconvenience is avoided. In particular, it is effective when the steam supplied from the steam compressor 4 is intended to preheat the feed water of the boiler 2. This is because when a chlorofluorocarbon refrigerant is used, the chlorofluorocarbon refrigerant generally contains oil for the purpose of protecting the compressor itself, so that if oil is mixed in the boiler feed water, foaming (foaming) is likely to occur. According to the configuration of the present embodiment, such a situation can be prevented beforehand.

  FIG. 5 is a schematic diagram illustrating an example of a steam utilization system to which a water cooling device according to a fifth embodiment of the present invention is applied. The water cooling device and the steam utilization system 1 of the fifth embodiment are basically the same as those of the first embodiment. Therefore, in the following description, differences between the two will be mainly described, and corresponding portions will be described with the same reference numerals.

  In the first embodiment, the water storage tank 8 is provided separately from the condenser 7, but in the fifth embodiment, the water storage tank 8 is incorporated in the condenser 7. Specifically, the condenser 7 includes a hollow tank 34 and a pipe line 35 provided on the inside thereof. In the fifth embodiment, the hollow tank 34 is used as a water storage section similarly to the water storage tank 8 in the first embodiment. That is, the hollow tank 34 is connected to the steam compressor 4 via the suction path 18 and can be decompressed by the steam compressor 4. In addition, water can be supplied to the hollow tank 34 via the water refill channel 22. On the other hand, the refrigerant of the heat pump 6 is passed through the pipe line 35 in the hollow tank 34. The pipe 35 is immersed in water in the hollow tank 34. Therefore, the refrigerant of the heat pump 6 is cooled by exchanging heat with the water in the hollow tank 34 while passing through the pipe line 35 in the hollow tank 34. Conversely, the water in the hollow tank 34 is heated by the refrigerant of the heat pump 6. Other configurations and controls are the same as those in the first embodiment, and a description thereof will be omitted.

  FIG. 6 is a schematic diagram illustrating an example of a steam utilization system to which a sixth embodiment of the water cooling device of the present invention is applied, and a part thereof is omitted. The water cooling device and the steam utilization system of the sixth embodiment are basically the same as those of the fifth embodiment. Therefore, in the following description, differences between the two will be mainly described, and corresponding portions will be described with the same reference numerals.

  In the fifth embodiment, the condenser 7 is composed of the hollow tank 34 and the pipe 35 that passes through the hollow tank 34. Water is stored in the hollow tank 34, while the refrigerant of the heat pump 6 is passed through the pipe 35. . On the other hand, in the present Example 6, although the point which comprises the condenser 7 from the hollow tank 34 and the pipe line 35 passed through the inside is the same, while passing the refrigerant | coolant of the heat pump 6 through the hollow tank 34, Water was stored in part or all of the pipe 35 to form a water reservoir.

  In the sixth embodiment, water is directly supplied from the supplementary water channel 22 to the pipe channel 35. The water in the pipe 35 is heated by indirect heat exchange with the refrigerant in the hollow tank 34. The steam compressor 4 is connected to the upper part of the pipe line 35 through the suction path 18 in the same manner as in the above embodiments, and water vapor from the water storage section is sucked into the steam compressor 4. Other configurations and controls are the same as those in the fifth embodiment, and thus description thereof is omitted.

  FIG. 7 is a schematic view showing an example of a steam utilization system to which a water cooling device according to a seventh embodiment of the present invention is applied, and a part thereof is omitted. The water cooling device and the steam utilization system of the seventh embodiment are basically the same as those of the fifth embodiment. Therefore, in the following description, differences between the two will be mainly described, and corresponding portions will be described with the same reference numerals.

  In the fifth embodiment, the condenser 7 is composed of the hollow tank 34 and the pipe line 35 that passes through the inside of the hollow tank 34. However, in the seventh embodiment, the condenser 7 has two pipe lines 36 and 37. It is an indirect heat exchanger, and one pipe line 36 is used as a water flow path and the other pipe line 37 is used as a refrigerant flow path. The refrigerant of the heat pump is passed through the refrigerant channel as in the fifth embodiment, and water is stored in the water channel as in the sixth embodiment. The indirect heat exchanger basically includes a refrigerant flow path and a water flow path, and only needs to indirectly heat exchange between the refrigerant and water, and thus includes a plate heat exchanger.

  In the seventh embodiment, water is directly supplied from the supplementary water channel 22 to the pipeline 36 constituting the water channel. And the water in the pipe line 36 which comprises a water flow path is heated by indirect heat exchange with the refrigerant | coolant in the other pipe line 37, and is heated. Further, the steam compressor 4 is connected to the upper portion of the pipe line 36 via the suction path 18 in the same manner as in the above embodiments, and water vapor from the water storage section is sucked into the steam compressor 4. Other configurations and controls are the same as those in the fifth embodiment, and thus description thereof is omitted.

  FIG. 8 is a schematic diagram showing an example of a steam utilization system to which the eighth embodiment of the water cooling device of the present invention is applied, and a part thereof is omitted. The water cooling device and the steam utilization system of the eighth embodiment are basically the same as those of the fifth embodiment. Therefore, in the following description, differences between the two will be mainly described, and corresponding portions will be described with the same reference numerals.

  The eighth embodiment is common to the fifth embodiment in that the pipe 35 is disposed in the hollow tank 34 and the refrigerant of the heat pump 6 is passed through the pipe 35. However, in the eighth embodiment, the entire pipe line 35 (or a part of the pipe line 35 in some cases) may be disposed in the gas phase portion of the hollow tank 34 without being immersed in the stored water. The water in the hollow tank 34 is sprayed downward from the nozzle 39 above the hollow tank 34 by the circulation pump 38. That is, water is sprayed from the nozzle 39 toward the pipe line 35 disposed in the gas phase portion. Spraying promotes the evaporation of water and further promotes cooling of the refrigerant by the latent heat of evaporation. Other configurations and controls are the same as those in the fifth embodiment, and thus description thereof is omitted.

  FIG. 9 is a schematic view showing an example of a steam utilization system to which the ninth embodiment of the water cooling device of the present invention is applied, and a part of the system is omitted. The water cooling device and the steam utilization system of the ninth embodiment are basically the same as those of the fifth embodiment. Therefore, in the following description, differences between the two will be mainly described, and corresponding portions will be described with the same reference numerals.

  The ninth embodiment is different from the fifth embodiment in the configuration of the evaporator 26. That is, in the fifth embodiment, the pipe 41 is passed through the hollow tank 40, and the refrigerant of the heat pump 6 is passed through the pipe 41, while water is circulated through the hollow tank 40. The refrigerant of the heat pump 6 was passed through the hollow tank 40, and water was passed through the pipe 41. Other configurations and controls are the same as those in the fifth embodiment, and thus description thereof is omitted. Needless to say, the configuration of the evaporator 26 according to the ninth embodiment is not limited to the fifth embodiment but can be similarly applied to other embodiments.

  FIG. 10 is a schematic diagram illustrating an example of a steam utilization system to which the water cooling device according to the tenth embodiment of the present invention is applied, and a part thereof is omitted. The water cooling device and the steam utilization system of the tenth embodiment are basically the same as those of the fifth embodiment. Therefore, in the following description, differences between the two will be mainly described, and corresponding portions will be described with the same reference numerals.

  The tenth embodiment is different from the fifth embodiment in the configuration of the evaporator 26. That is, in the said Example 5, although the evaporator 26 comprised the hollow tank 40 and the pipe line 41 passed through the inside, in this Example 10, the evaporator 26 has two pipe lines 42 and 43. The indirect heat exchanger has one pipe line 42 as a water flow path and the other pipe line 43 as a refrigerant flow path. Similarly to the fifth embodiment, the refrigerant of the heat pump 6 is passed through the refrigerant flow path, and water is passed through the water flow path as in the ninth embodiment. Other configurations and controls are the same as those in the fifth embodiment, and thus description thereof is omitted. Needless to say, the configuration of the evaporator 26 according to the tenth embodiment is not limited to the fifth embodiment but can be similarly applied to other embodiments.

  FIG. 11 is a schematic view showing an example of a steam utilization system to which an embodiment 11 of the water cooling device of the present invention is applied, and a part thereof is omitted. The water cooling device and the steam utilization system according to the eleventh embodiment are basically the same as those of the fifth embodiment. Therefore, in the following description, differences between the two will be mainly described, and corresponding portions will be described with the same reference numerals.

  In the eleventh embodiment, a water supply pump 51 is provided and controlled in the supplementary water passage 22 to the hollow tank 34 instead of the supplementary water valve 24. That is, water can be supplied to the hollow tank 34 via the water pump 51. The water supply pump 51 may be on / off controlled or may be inverter controlled so that the flow rate can be adjusted. Alternatively, the water supply amount to the hollow tank 34 may be adjusted by providing a water supplement valve in addition to the water pump 51 and adjusting the opening of the water supplement valve while the water pump 51 is activated.

  In Embodiment 11, the vapor compressor 4 sucks and discharges the gas in the hollow tank 34 through the steam separator 52. In other words, the steam separator 52 is provided in the middle of the suction path 18 to the steam compressor 4, and the steam whose droplets are separated in the steam separator 52 is supplied to the steam compressor 4. . And the steam discharged from the steam compressor 4 is sent to a steam utilization apparatus.

  On the other hand, the water separated by the steam separator 52 is led out through the steam trap 53. Although the usage method in particular of the water is not ask | required, it is used for the preheating of the water supply to the boiler 2 here. Specifically, the water led out through the steam trap 53 is supplied to the water supply tank 9 to the boiler 2. Since the water from the steam separator 52 is hot water, it is possible to preheat water supplied to the boiler 2. Other configurations and controls are the same as those in the fifth embodiment, and thus description thereof is omitted.

  FIG. 12 is a schematic diagram illustrating an example of a steam utilization system to which the water cooling device according to the twelfth embodiment of the present invention is applied, and a part thereof is omitted. The water cooling device and the steam utilization system of the twelfth embodiment are basically the same as those of the fifth embodiment. Therefore, in the following description, differences between the two will be mainly described, and corresponding portions will be described with the same reference numerals. The twelfth embodiment can be said to be a modification of the eleventh embodiment.

  In the twelfth embodiment, the vapor compressor 4 sucks and discharges the gas in the hollow tank 34 via the steam separator 52. In other words, the steam separator 52 is provided in the middle of the suction path 18 to the steam compressor 4, and the steam whose droplets are separated in the steam separator 52 is supplied to the steam compressor 4. .

  The water separated by the steam separator 52 is led out through the steam trap 53. In this embodiment 11, this water is supplied as it is to the water supply tank 9 to the boiler 2, but in this embodiment 12, the water from the steam separator 52 is supplied to the indirect heat exchanger 54 with make-up water. And returned to the hollow tank 34 serving as a water storage section. A water supply pump 51 is provided in the water supply path from the indirect heat exchanger 54 to the hollow tank 34.

  In the indirect heat exchanger 54, makeup water (pure water or soft water) is heated with hot water from the steam separator 52. The water heated in this way is supplied to the water supply tank 9 of the boiler 2. In this way, it is possible to preheat water supplied to the boiler 2. Compared with the case where the water from the steam separator 52 is sent directly to the water supply tank 9, the water quality can be easily managed.

  Further, in the twelfth embodiment, the steam discharged from the steam compressor 4 is passed through an indirect heat exchanger 33 with make-up water, as in the third and fourth embodiments, and a hollow tank 34 as a water storage section. Supplied to. For example, as in the third embodiment, in the indirect heat exchanger 33, make-up water (pure water or soft water) is heated and vaporized by the steam from the steam compressor 4. Then, the steam joins with the exhaust steam path 15 from the steam engine 3 and is sent to the steam utilization device. Or in the indirect heat exchanger 33, the makeup water (pure water or soft water) is heated by the steam from the steam compressor 4 as in the fourth embodiment, and the water thus heated is used as the boiler 2. The water supply tank 9 may be supplied. In any case, the condensed water of the steam after the heat exchange in the indirect heat exchanger 33 is returned to the hollow tank 34 via the steam trap 55 and the water feed pump 51. Other configurations and controls are the same as those in the fifth embodiment, and thus description thereof is omitted.

  The water cooling device of the present invention is not limited to the configuration of each of the embodiments described above, and can be changed as appropriate. For example, in each of the above embodiments, both the steam compressor 4 and the refrigerant compressor 5 are driven by the steam engine 3, but one or both may be driven by an electric motor. For example, in the first embodiment, both the steam compressor 4 and the refrigerant compressor 5 may be driven by an electric motor. At that time, as shown in FIG. 13, both compressors 4 and 5 may be driven by a common motor 44, or as shown in FIG. 14, each compressor 4 and 5 is individually driven by motors 44 and 44. It may be driven. In FIG. 14, one or both of the electric motors 44 may be the steam engine 3. Such a change is not limited to the first embodiment, and other embodiments are also possible. 13 and 14 show only the drive units of the compressors 4 and 5, and other configurations are omitted.

  In each of the above embodiments, the heat pump 6 may have a plurality of stages. For example, as shown in FIG. 15, in addition to the first heat pump 45 as the heat pump 6, a second heat pump 46 may be further provided. The second heat pump 46 has the same configuration as the first heat pump 45, and is configured by sequentially connecting a refrigerant compressor 47, a condenser 48, an expansion valve 49, and an evaporator 50 in an annular shape. Further, the refrigerant of each heat pump 45, 46 can be appropriately selected according to the desired condensation temperature of the condenser 48 and the desired evaporation temperature of the evaporator 50.

  The condenser 7 of the first heat pump 45 is an indirect heat exchanger between the refrigerant of the first heat pump 45 and the water in the water storage tank 8. The evaporator 26 of the first heat pump 45 is also a condenser 48 of the second heat pump 46 and is an indirect heat exchanger between the refrigerant of the first heat pump 45 and the refrigerant of the second heat pump 46. The evaporator 50 of the second heat pump 46 is an indirect heat exchanger between the refrigerant of the second heat pump 46 and water to the cooler. Other configurations and controls are the same as those in the first embodiment.

  By making the heat pump into a plurality of stages, the compression ratio can be suppressed, and the configuration of the compressors and evaporators of the heat pumps in each stage can be reduced in size. That is, in a single-stage heat pump, the compression ratio becomes high and the efficiency becomes poor, but by using a plurality of stages, it becomes possible to operate at an optimal compression ratio.

  In FIG. 15, the compressors 4, 5, and 47 are driven by the electric motor 44 as in FIG. 14, but of course, they may be driven by the steam engine 3 as in FIG. 1. FIG. 15 shows an example in which the heat pump of FIG. 14 has a plurality of stages, but it can be similarly applied to other embodiments to have a plurality of stages.

  Further, in FIG. 15, only the second heat pump 46 is provided in the first heat pump 45, but the number of stages of the heat pump may be further increased. That is, in addition to the first heat pump 45, a second or third heat pump (hereinafter referred to as “additional heat pump”) may be further provided. In that case, the evaporator 26 of the first heat pump 45 is an indirect heat exchanger between the refrigerant of the first heat pump 45 and the refrigerant of the uppermost additional heat pump, and is also a condenser of the uppermost additional heat pump. Further, the evaporator of the lowermost additional heat pump is an indirect heat exchanger between the refrigerant of the lowermost additional heat pump and the water to the cooler. In addition, the heat pump sandwiched between the uppermost and lowermost heat pumps is an evaporator of one upper heat pump and a condenser of one lower heat pump.

  Finally, the water cooling device of the present invention may be used for cooling a relatively high temperature object such as an engine in addition to air conditioning and food cooling. For example, a jacket may be provided as the cooler in the gas engine, and the gas engine may be cooled through cold water obtained by the water cooling device of the present invention or a refrigerant exchanged with the jacket through the jacket.

  Furthermore, the water cooling device of the present invention can also be used to cool hot water discharged from a factory or the like. For example, there is a case where a large amount of waste water at 60 to 100 ° C. comes out from a factory. However, when water is reused, it is conventionally cooled by a large cooling tower, and when water is not reused. Because it must be cooled to less than 40 ° C. due to legal regulations, it is cooled by mixing industrial water (tap water) and then drained into rivers and the like.

  However, the water cooling device of the present invention can be used for cooling such waste warm water. Specifically, for example, in Example 11 or Example 12, high temperature waste water from the factory may be flowed to the evaporator 26 of the heat pump 6 and after cooling in the evaporator 26, it may be reused or drained to a river or the like. This eliminates the need for a cooling tower, reduces initial costs and running costs, and reduces cooling water. Moreover, steam and hot water can be obtained by the energy obtained when cooling the waste warm water.

DESCRIPTION OF SYMBOLS 1 Steam utilization system 2 Boiler 3 Steam engine 4 Steam compressor 5 Refrigerant compressor 6 Heat pump 7 Condenser 8 Water storage tank (water storage part)
9 Water supply tank 18 Suction path 19 Discharge path 20 Water injection path 21 Water injection valve 25 Expansion valve 26 Evaporator 30 Cold water supply path 33 Indirect heat exchanger 34 Hollow tank 35 Pipe line 38 Circulation pump 39 Nozzle 45 First heat pump 46 Second heat pump ( Additional heat pump)
48 (second heat pump) condenser 50 (second heat pump) evaporator 52 steam separator 54 indirect heat exchanger

Claims (11)

A vapor compressor that sucks and discharges the gas in the water storage unit, depressurizes the water storage unit, and compresses the water vapor sucked from the water storage unit;
A refrigerant compressor, a condenser, an expansion valve, and a heat pump configured by sequentially connecting an evaporator in an annular shape,
The condenser is an indirect heat exchanger between the refrigerant of the heat pump and the water of the water reservoir,
The evaporator is an indirect heat exchanger between the refrigerant of the heat pump and water to be cooled ,
Steam from the steam compressor is supplied to a water supply tank for a boiler . A vapor compressor that sucks and discharges the gas in the water storage unit, depressurizes the water storage unit, and compresses the water vapor sucked from the water storage unit;
A refrigerant compressor, a condenser, an expansion valve, and a heat pump configured by sequentially connecting an evaporator in an annular shape,
The condenser is an indirect heat exchanger between the refrigerant of the heat pump and the water of the water reservoir,
The evaporator is an indirect heat exchanger between the refrigerant of the heat pump and water to be cooled ,
The steam from the steam compressor is supplied to the water storage unit through indirect heat exchange with makeup water,
The makeup water is vaporized by indirect heat exchange with steam from the steam compressor . A vapor compressor that sucks and discharges the gas in the water storage unit, depressurizes the water storage unit, and compresses the water vapor sucked from the water storage unit;
A refrigerant compressor, a condenser, an expansion valve, and a heat pump configured by sequentially connecting an evaporator in an annular shape,
The condenser is an indirect heat exchanger between the refrigerant of the heat pump and the water of the water reservoir,
The evaporator is an indirect heat exchanger between the refrigerant of the heat pump and water to be cooled ,
The steam from the steam compressor is supplied to the water storage unit through indirect heat exchange with makeup water,
The makeup water is heated by indirect heat exchange with steam from the steam compressor and supplied to a water supply tank to a boiler . A vapor compressor that sucks and discharges the gas in the water storage unit, depressurizes the water storage unit, and compresses the water vapor sucked from the water storage unit;
A refrigerant compressor, a condenser, an expansion valve, and a heat pump configured by sequentially connecting an evaporator in an annular shape,
The condenser is an indirect heat exchanger between the refrigerant of the heat pump and the water of the water reservoir,
The evaporator is an indirect heat exchanger between the refrigerant of the heat pump and water to be cooled ,
One or both of the steam compressor and the refrigerant compressor are driven by a steam engine that generates power using steam,
The steam from the steam compressor is supplied to the water storage unit through indirect heat exchange with makeup water,
The make-up water is vaporized by indirect heat exchange with the steam from the steam compressor, and is supplied to a place where used steam is supplied by the steam engine, or the steam from the steam compressor is supplied. The water cooling device is heated by indirect heat exchange with the steam engine and supplied to a water supply tank to a boiler that supplies steam to the steam engine . A water storage tank for storing water;
This water storage tank is the water storage part,
The condenser is an indirect heat exchanger having a refrigerant channel and a water channel,
The refrigerant flow path is passed through the refrigerant of the heat pump,
The water cooling device according to any one of claims 1 to 4 , wherein water in the water storage tank is circulated between the water flow path and the water storage tank. The condenser is composed of a hollow tank and a pipe line provided inside the hollow tank,
The refrigerant of the heat pump is passed through one of the hollow tank and the conduit, and water is stored in the other to serve as the water storage section . The water cooling apparatus as described. While water is stored in the hollow tank, the refrigerant of the heat pump is passed through the pipeline,
Inside the hollow tank, water is stored halfway, and is divided into a liquid phase part and a gas phase part,
The pipe line is at least partially arranged in a gas phase part in the hollow tank,
The water cooling device according to claim 6 , wherein the water stored in the hollow tank is sprayed toward a pipe line disposed in the gas phase portion. The condenser is an indirect heat exchanger having a refrigerant channel and a water channel,
The refrigerant flow path is passed through the refrigerant of the heat pump,
The water cooling device according to any one of claims 1 to 4, wherein water is stored in the water flow path to serve as the water storage section. In addition to the first heat pump as the heat pump, further comprising one or more additional heat pumps,
The evaporator of the first heat pump is an indirect heat exchanger between the refrigerant of the first heat pump and the water to be cooled, and instead of the refrigerant of the first heat pump and the refrigerant of the uppermost additional heat pump. As an indirect heat exchanger, it is also a condenser of the uppermost additional heat pump,
Evaporator of the additional heat pump lowest stage, to any one of claims 1 to 8, characterized in that it is an indirect heat exchanger with water to be cooled and refrigerant of the additional heat pump of the lowermost The water cooling apparatus as described. The water cooling device according to any one of claims 1 to 9 , wherein the steam compressed by the steam compressor is injected with water in the steam compressor itself or in a preceding stage or a subsequent stage thereof. The steam compressor sucks and discharges the gas in the water storage section through a steam separator,
Water separated in the gas-water separator, claims 1 to 10, characterized in that either supplied to the water tank to the boiler, which is water and indirect heat exchange to a boiler back into the reservoir The water cooling device according to any one of the above.

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