WO2022138520A1 - Procédé de commande de fonctionnement et système de refroidissement - Google Patents

Procédé de commande de fonctionnement et système de refroidissement Download PDF

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Publication number
WO2022138520A1
WO2022138520A1 PCT/JP2021/046894 JP2021046894W WO2022138520A1 WO 2022138520 A1 WO2022138520 A1 WO 2022138520A1 JP 2021046894 W JP2021046894 W JP 2021046894W WO 2022138520 A1 WO2022138520 A1 WO 2022138520A1
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Prior art keywords
refrigerant
liquid refrigerant
liquid
temperature
cooler
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PCT/JP2021/046894
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English (en)
Japanese (ja)
Inventor
行介 山田
弥彦 芳野
伊朗 井筒
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株式会社Boban
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Publication of WO2022138520A1 publication Critical patent/WO2022138520A1/fr

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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B1/00—Compression machines, plants or systems with non-reversible cycle
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25C—PRODUCING, WORKING OR HANDLING ICE
    • F25C1/00—Producing ice

Definitions

  • the present invention relates to an operation control method and a cooling system.
  • a full-liquid ice maker described in Patent Document 1 is known as a cooling system for producing an ice slurry.
  • salt water is circulated in an ice maker filled with a liquid refrigerant, and the salt water is cooled by heat exchange between the liquid refrigerant and the salt water to generate an ice slurry.
  • An object of the present invention is to provide an operation control method and a cooling system capable of controlling the temperature of a liquid refrigerant and exhibiting stable cooling characteristics.
  • An operation control method for a cooling system having a cooler that cools a medium to be cooled by exchanging heat with a liquid refrigerant comprising controlling the temperature of the liquid refrigerant in the cooler by supplying a high-pressure gaseous gas refrigerant to the liquid refrigerant.
  • the gas refrigerant is generated by compressing the refrigerant with a compressor.
  • a compressor that compresses the refrigerant into a high-pressure gaseous gas refrigerant
  • a condenser that condenses the gas refrigerant into a high-pressure liquid liquid refrigerant
  • a cooler that cools the medium to be cooled by heat exchange with the liquid refrigerant
  • a cooling system comprising: a control device for controlling the temperature of the liquid refrigerant in the cooler by supplying the gas refrigerant to the liquid refrigerant.
  • the temperature of the liquid refrigerant in the cooler is stable, and stable cooling characteristics can be exhibited.
  • the temperature of the liquid refrigerant can be controlled with excellent responsiveness.
  • FIG. 1 is a diagram showing an overall configuration diagram of a cooling system according to the first embodiment.
  • FIG. 2 is a cross-sectional view showing a cooler and a liquid level measuring instrument.
  • FIG. 3 is a block diagram showing a control method of the control device.
  • FIG. 4 is a block diagram showing a control method of the control device.
  • FIG. 5 is a cross-sectional view showing a cooler and a liquid level measuring instrument included in the cooling system according to the second embodiment.
  • the upper side of the paper surface in FIGS. 2 and 5 is the upper side in the vertical direction
  • the lower side of the paper surface is the lower side in the vertical direction.
  • the cooling system 1 shown in FIG. 1 is a system that continuously produces an ice slurry S using salt water B (brine) as a raw material.
  • the ice slurry S refers to sherbet-like ice in which fine ice is turbid in salt water, and may also be referred to as slurry ice, ice slurry, slurry ice, or the like.
  • the cooling system 1 includes a compressor 21, a condenser 22, a cooler 23 (evaporator), and a liquid level measuring unit 24. Further, the cooling system 1 includes a pipe 251 connecting the compressor 21 and the condenser 22, a pipe 252 connecting the condenser 22 and the cooler 23, and a pipe 253 connecting the cooler 23 and the compressor 21. And a pipe 254 that bypasses the pipe 251 and the pipe 252 without passing through the condenser 22. Further, the cooling system 1 has a liquid level adjusting valve 26 provided in the middle of the pipe 252 and a pressure adjusting valve 27 provided in the middle of the pipe 254. Each of these elements constitutes a refrigerant circuit 2 in which the refrigerant R circulates.
  • the refrigerant R is compressed by driving the compressor 21 to form a high-temperature high-pressure gas.
  • the refrigerant R (hereinafter, also referred to as “gas refrigerant Rg”) that has become a high-temperature and high-pressure gas in the compressor 21 flows into the condenser 22 through the pipe 251 and is condensed by heat exchange with air by the operation of the blower fan 221. ⁇ It liquefies and becomes a high-pressure liquid.
  • the high-pressure liquid refrigerant R (hereinafter also referred to as “liquid refrigerant Rl”) in the condenser 22 flows into the cooler 23 through the pipe 252 and evaporates by heat exchange with the salt water B in the cooler 23.
  • the amount of the liquid refrigerant Rl flowing into the cooler 23 is adjusted by the liquid level adjusting valve 26. Further, a part of the gas refrigerant Rg (hot gas) turned into a high-temperature and high-pressure gas by the compressor 21 is supplied to the liquid refrigerant Rl flowing in the pipe 252 through the pipe 254 connected to the pipe 251.
  • the pressure (temperature) of the liquid refrigerant Rl flowing into the cooler 23 can be controlled.
  • the amount of the high gas refrigerant Rg supplied to the liquid refrigerant Rl is adjusted by the pressure adjusting valve 27.
  • the refrigerant R which has become a low-pressure gas due to heat exchange with the salt water B in the cooler 23, is returned to the compressor 21 via the pipe 253, compressed by the compressor 21, and discharged as the gas refrigerant Rg again. Will be done.
  • the refrigerant circuit 2 continuously cools the salt water B in the cooler 23 by circulating the refrigerant R in such a heat exchange cycle.
  • the amount of the liquid refrigerant Rl supplied to the cooler 23 is adjusted by the liquid level adjusting valve 26, and the amount of the liquid refrigerant Rl in the cooler 23, that is, the liquid level height Da of the liquid refrigerant Rl is adjusted.
  • the target liquid level height Dt which is the control target, is maintained.
  • the pressure (temperature) of the liquid refrigerant Rl supplied to the cooler 23 is adjusted by the pressure adjusting valve 27, and the pressure (temperature) of the liquid refrigerant Rl in the cooler 23 is the control target pressure Pt (target temperature). It is kept at Tt).
  • the amount and pressure (temperature) of the liquid refrigerant Rl in the cooler 23 can be maintained at the target values in this way. Therefore, heat exchange between the refrigerant R and the salt water B can be stably performed under desired conditions. Therefore, the salt water B can be continuously cooled stably under appropriate conditions, and the ice slurry S can be efficiently produced. In addition, the ice slurry S produced becomes more homogeneous, and high-quality ice slurry S can be produced.
  • the cooling system 1 includes a storage tank 31 for storing the salt water B and the ice slurry S generated from the salt water B, a pump 32 for circulating the salt water B, and the salt water B supplied to the cooler 23. It has a concentration sensor 33 for detecting a salt concentration, and a concentration sensor 33. Further, the cooling system 1 has a pipe 341 connecting the storage tank 31 and the cooler 23, and a pipe 342 connecting the cooler 23 and the storage tank 31, and a pump 32 is installed in the middle of the pipe 341. The concentration sensor 33 is installed in the cooler 23. Each of these elements constitutes a salt water circulation path 3 (cooled medium circulation path) through which salt water circulates. However, the location of the concentration sensor 33 is not particularly limited as long as it can detect the salt concentration of the salt water B supplied to the cooler 23.
  • the storage tank 31 is provided with a stirring blade 311 for stirring the salt water B and the ice slurry S in the tank, and a motor 312 for rotating the stirring blade 311. This makes it possible to suppress the aggregation of the ice slurry S in the storage tank 31. Further, the storage tank 31 is provided with a discharge pipe 313 for discharging the ice slurry S stored in the tank.
  • the salt water B in the storage tank 31 is supplied to the cooler 23 through the pipe 341 by driving the pump 32.
  • the salt water B supplied into the cooler 23 is cooled by heat exchange with the liquid refrigerant Rl in the cooler 23.
  • the salt water B cooled by the cooler 23 is returned to the storage tank 31 through the pipe 342, and is supplied to the cooler 23 again through the pipe 341.
  • the ice slurry S generated by cooling is stored in the storage tank 31.
  • the salt water circulation path 3 continuously produces the ice slurry S by repeating such a salt water circulation cycle.
  • the cooling system 1 has a control device 4 that controls the drive of each part of the cooling system 1.
  • the control device 4 includes, for example, a processor composed of a computer and processing information, and a memory communicably connected to the processor. Various programs necessary for operating the cooling system 1 are stored in the memory. The processor reads and executes various programs and the like stored in the memory. As a result, the operation of the cooling system 1 as described below is realized.
  • the cooler 23 includes a main evaporator 231, a sub-evaporator 235, and a pressure sensor 239 that detects the pressure of the liquid refrigerant Rl in the main evaporator 231.
  • the pipe 252 is connected to the lower end of the main evaporator 231 and the pipe 253 is connected to the upper end of the sub-evaporator 235.
  • the liquid refrigerant Rl which has become a high-pressure liquid in the condenser 22, is supplied to the main evaporator 231 through the pipe 252.
  • the low-pressure gaseous refrigerant R evaporated and vaporized by heat exchange with the salt water B in the main evaporator 231 is returned from the sub-evaporator 235 to the compressor 21 through the pipe 253.
  • the main evaporator 231 has an outer pipe 232 and an inner pipe 233 coaxially arranged inside the outer pipe 232.
  • the outer pipe 232 and the inner pipe 233 are circular pipes whose ends are closed, respectively.
  • the outer pipe 232 and the inner pipe 233 are not limited to circular pipes, respectively.
  • the outer pipe 232 and the inner pipe 233 are installed upright, and the shaft faces in the vertical direction. That is, the main evaporator 231 is a vertical double-tube evaporator.
  • the main evaporator 231 is a full-liquid evaporator, and almost the entire space between the outer pipe 232 and the inner pipe 233 is filled with the liquid refrigerant Rl.
  • the space will also be referred to as "refrigerant storage unit 234".
  • the salt water B flows in the inner pipe 233. Therefore, heat exchange between the salt water B and the liquid refrigerant Rl is performed through the wall surface of the inner pipe 233.
  • the inner pipe 233 may be made of a material having excellent mechanical strength and high thermal conductivity, such as iron, copper, aluminum, titanium, and stainless steel. preferable. Further, in order to increase the heat exchange efficiency between the liquid refrigerant Rl and the salt water B, the inner pipe 233 is preferably as thin as possible as long as the mechanical strength can be maintained.
  • the sub-evaporator 235 is installed side by side with the main evaporator 231 in the horizontal direction.
  • the sub-evaporator 235 is a circular tube with both ends closed. Further, the sub-evaporator 235 is installed upright, and its axis faces in the vertical direction.
  • Such a sub-evaporator 235 is connected to the refrigerant storage unit 234 via a pair of pipes 236. Therefore, the liquid refrigerant Rl supplied to the refrigerant storage unit 234 is also supplied to the sub-evaporator 235 through these pipes 236.
  • the pressures (internal pressures) of the sub-evaporator 235 and the refrigerant storage unit 234 are equal to each other, and the liquid level height of the liquid refrigerant Rl in the sub-evaporator 235 is the same as the liquid level height of the liquid refrigerant Rl in the refrigerant storage unit 234. equal.
  • the lower end of the sub-evaporator 235 is located above the lower end of the main evaporator 231 in the vertical direction. Therefore, for example, the amount of the liquid refrigerant Rl in the sub-evaporator 235 is higher than the case where the lower end is at the same height as the lower end of the main evaporator 231 or the lower end is located below the lower end of the main evaporator 231 in the vertical direction. Can be reduced. As a result, the amount of the refrigerant R used can be reduced.
  • the sub-evaporator 235 is vertically longer than the main evaporator 231 and its upper end is located vertically above the upper end of the main evaporator 231. Therefore, a space 237 located above the liquid refrigerant Rl is formed in the sub-evaporator 235. As will be described later, a dehumidifying member 238 is arranged in the space 237.
  • the refrigerant R evaporated and vaporized by heat exchange with the salt water B in the main evaporator 231 is returned to the compressor 21 from the upper end of the sub-evaporator 235 through the pipe 253.
  • the compressor 21 may fail due to a sudden increase in the cylinder internal pressure due to the liquid compression. Therefore, a dehumidifying member 238 for removing the liquid (humidity) contained in the vaporized refrigerant R is arranged in the space 237 of the sub-evaporator 235.
  • the dehumidifying member 238 has an umbrella shape with a large number of through holes formed.
  • the through hole serves as a passage for the refrigerant R.
  • the vaporized refrigerant R comes into contact with the dehumidifying member 238 while rising from the liquid surface toward the pipe 253, and the liquid (humidity) contained in the refrigerant R is removed by the contact, and the drier refrigerant R is compressed. It is returned to the machine 21. This makes it possible to prevent the compressor 21 from failing as described above.
  • a plurality of dehumidifying members 238 are arranged in the vertical direction to improve the dehumidifying effect.
  • the dehumidifying member 238 may be omitted when the refrigerant R is almost completely evaporated by heat exchange with the salt water B and the sufficiently dry gaseous refrigerant R returns to the compressor 21. Further, for example, when the dehumidifying member 238 is insufficiently dried, a superheater is arranged in the middle of the pipe 253 in place of or in addition to the dehumidifying member 238, and the refrigerant R is heated by the superheater before the compressor. It may be configured to return to 21.
  • the liquid level measuring unit 24 includes a refrigerant storage pipe 241 and a liquid level detection sensor 242.
  • the refrigerant storage pipe 241 is installed side by side with the sub-evaporator 235 in the horizontal direction. Further, the refrigerant storage pipe 241 is installed upright, and its axis faces in the vertical direction. Further, the refrigerant storage pipe 241 is connected to the sub-evaporator 235 via a pair of pipes 243. Therefore, the liquid refrigerant Rl supplied to the refrigerant storage unit 234 is also supplied to the refrigerant storage pipe 241 via the sub-evaporator 235.
  • the pressures (internal pressures) in the refrigerant storage pipe 241 and the sub-evaporator 235 and the refrigerant storage unit 234 are equal to each other. Therefore, as shown by the chain line in FIG. 2, the liquid level heights of the liquid refrigerants Rl in the refrigerant storage pipe 241 and the sub-evaporator 235 and the refrigerant storage unit 234 are equal to each other. Therefore, by detecting the liquid level height of the liquid refrigerant Rl in the refrigerant storage pipe 241, it is possible to detect the liquid level height of the liquid refrigerant Rl in the refrigerant storage unit 234.
  • a liquid level detection sensor 242 is installed in the refrigerant storage pipe 241, and the liquid level of the liquid refrigerant Rl in the refrigerant storage pipe 241 is detected by the liquid level detection sensor 242, whereby the liquid refrigerant in the refrigerant storage unit 234 is detected. It is configured to detect the liquid level height of Rl.
  • the liquid level detection sensor 242 By installing the liquid level detection sensor 242 at a location different from the refrigerant storage unit 234 in this way, the liquid of the liquid refrigerant Rl in the refrigerant storage unit 234 is not hindered from heat exchange between the liquid refrigerant Rl and the salt water B.
  • the surface height can be detected.
  • the configuration of the liquid level measuring unit 24 is not particularly limited as long as the liquid level height of the liquid refrigerant Rl in the refrigerant storage unit 234 can be detected.
  • the refrigerant storage pipe 241 is a circular pipe with both ends closed, and its length and diameter are smaller than those of the sub-evaporator 235. By making the refrigerant storage pipe 241 smaller than the sub-evaporator 235 in this way, the amount of the liquid refrigerant Rl in the refrigerant storage pipe 241 can be reduced. As a result, the amount of the refrigerant R used can be reduced.
  • the liquid level adjusting valve 26 is a valve for controlling the supply amount of the liquid refrigerant Rl to the main evaporator 231 and is installed on the upstream side of the main evaporator 231.
  • the liquid level adjusting valve 26 can be adjusted not only on / off but also in multiple steps or steplessly with an opening degree of 0 to 100%.
  • the drive of the liquid level adjusting valve 26 is controlled by the control device 4.
  • the control device 4 determines the liquid level height Da of the liquid refrigerant Rl in the refrigerant storage unit 234 indicated by the output of the liquid level detection sensor 242, the target liquid level height Dt which is the control target, and the target liquid level height Dt. Perform feedback control to match.
  • the liquid level height Da of the liquid refrigerant Rl in the refrigerant storage unit 234 can be maintained at the target liquid level height Dt (difference from the target liquid level height Dt can be suppressed), and the liquid refrigerant can be suppressed.
  • the heat exchange between Rl and the salt water B can be stably performed under desired conditions. Therefore, the ice slurry S can be stably and efficiently produced. In addition, the ice slurry S produced becomes more homogeneous, and high-quality ice slurry S can be produced.
  • the control device 4 controls the drive of the liquid level adjusting valve 26 by analog control, particularly PID control. Specifically, the control device 4 controls the PID for the liquid level height Da by using the deviation De between the liquid level height Da and the target liquid level Dt, the integral of the deviation De, and the derivative of the deviation De. Run. Note that FIG. 3 shows the proportional gain Kpp, the integrated gain Kpi, and the differential gain Kpd. According to the PID control, the fluctuation of the liquid level height Da of the liquid refrigerant Rl is reduced and the liquid level height Da is stabilized as compared with the simple ON / OFF control. Therefore, heat exchange between the liquid refrigerant Rl and the salt water B can be performed more stably under desired conditions.
  • the ice slurry S can be stably and efficiently produced.
  • the ice slurry S produced becomes more homogeneous, and high-quality ice slurry S can be produced.
  • the control method of the liquid level adjusting valve 26 is not particularly limited, and may be, for example, other analog control such as P control or PI control, or may be digital control.
  • the pressure adjusting valve 27 is a valve for controlling the pressure of the liquid refrigerant Rl in the main evaporator 231 and is installed on the upstream side of the main evaporator 231.
  • the pressure adjusting valve 27 By supplying the high-temperature high-pressure gaseous gas refrigerant Rg to the high-pressure liquid liquid refrigerant Rl, the pressure of the liquid refrigerant Rl flowing into the refrigerant storage unit 234 can be increased, and the supply amount of the gas refrigerant Rg can be increased by the pressure adjusting valve 27.
  • the pressure of the liquid refrigerant Rl in the refrigerant storage unit 234 can be controlled. According to such a control method, the pressure of the liquid refrigerant Rl in the refrigerant storage unit 234 can be controlled with a simple configuration.
  • Such a pressure adjusting valve 27 can be adjusted not only on / off but also in multiple steps or steplessly with an opening degree of 0 to 100%.
  • the drive of the pressure adjusting valve 27 is controlled by the control device 4.
  • the control device 4 executes feedback control for matching the pressure Pa of the liquid refrigerant Rl in the refrigerant storage unit 234 indicated by the output of the pressure sensor 239 with the target pressure Pt, which is the control target. ..
  • the temperature of the liquid refrigerant Rl is proportional to its pressure. Therefore, controlling the pressure of the liquid refrigerant Rl is synonymous with controlling the temperature of the liquid refrigerant Rl. Therefore, by executing such feedback control, the temperature Ta of the liquid refrigerant Rl in the refrigerant storage unit 234 can be maintained at the target temperature Tt (difference from the target temperature Tt can be suppressed), and the liquid can be suppressed.
  • the heat exchange between the refrigerant Rl and the salt water B can be stably performed under desired conditions. Therefore, the ice slurry S can be stably and efficiently produced. In addition, the ice slurry S produced becomes more homogeneous, and high-quality ice slurry S can be produced.
  • the target temperature Tt temperature Ta of the liquid refrigerant Rl
  • the freezing point Tf freezing point
  • Tf-10 ° C. ⁇ Tt ⁇ Tf is preferable, Tf-10 ° C. ⁇ Tt ⁇ Tf-3 ° C. is more preferable, and Tf-10 ° C. ⁇ Tt ⁇ Tf-5 ° C. is more preferable. Is even more preferable.
  • the temperature of the liquid refrigerant Rl so as to satisfy the relationship of Tf-10 ° C. ⁇ Ta ⁇ Tf, and the liquid refrigerant Rl so as to satisfy the relationship of Tf-8 ° C. ⁇ Ta ⁇ Tf-3 ° C. It is more preferable to control the temperature of the liquid refrigerant Rl, and it is further preferable to control the temperature of the liquid refrigerant Rl so as to satisfy the relationship of Tf-7 ° C ⁇ Ta ⁇ Tf-5 ° C.
  • the cooling system 1 uses a full-liquid main evaporator 231 with high work efficiency, a high work amount can be secured even if the temperature difference ⁇ T is small, and the salt water B is cooled at a sufficient speed. It becomes possible to do. That is, the operation with a small temperature difference ⁇ T is realized because the full-liquid main evaporator 231 is used. Further, according to the cooling system 1, since the temperature of the liquid refrigerant Rl can be closely controlled, the temperature difference ⁇ T can be controlled accurately.
  • the control device 4 Since the freezing point Tf of the salt water B is determined by the salt concentration, the freezing point Tf of the salt water B can be obtained if the salt concentration of the salt water B is known. Therefore, the control device 4 first obtains the freezing point Tf of the salt water B from the salt concentration of the salt water B in the cooler 23 indicated by the output of the concentration sensor 33. Next, the control device 4 sets the target temperature Tt of the liquid refrigerant Rl so that the temperature difference ⁇ T becomes a predetermined value. Next, the control device 4 obtains the pressure of the liquid refrigerant Rl corresponding to the set target temperature Tt, and sets this as the target pressure Pt.
  • the control device 4 controls the drive of the pressure adjusting valve 27 by analog control, particularly PID control. Specifically, as shown in FIG. 4, the control device 4 executes PID control for the pressure Pa by using the deviation Pe between the pressure Pa and the target pressure Pt, the integral of the deviation Pe, and the derivative of the deviation Pe. ..
  • FIG. 4 shows the proportional gain Kpp, the integrated gain Kpi, and the differential gain Kpd. According to the PID control, the fluctuation of the pressure Pa of the refrigerant R is reduced and the pressure Pa is stabilized as compared with the simple ON / OFF control. Therefore, heat exchange between the liquid refrigerant Rl and the salt water B can be performed more stably under desired conditions.
  • the ice slurry S can be stably and efficiently produced.
  • the ice slurry S produced becomes more homogeneous, and high-quality ice slurry S can be produced.
  • the control method of the pressure adjusting valve 27 is not particularly limited, and may be, for example, other analog control such as P control or PI control, or may be digital control.
  • the control device 4 has a plurality of pressure control modes in order to efficiently cool the salt water B while suppressing freezing of the salt water B (adhesion of ice to the inner pipe 233) in the cooler 23. ..
  • a quenching mode M1 and a slow cooling mode M2 are provided as a plurality of pressure control modes.
  • the slow cooling mode M2 is the control mode described above, and is a mode in which the drive of the pressure adjusting valve 27 is controlled so that Tf ⁇ 10 ° C. ⁇ Ta ⁇ Tf.
  • the quenching mode M1 is a mode in which the temperature Ta is lower than that of the slow cooling mode M2, and the drive of the pressure adjusting valve 27 is controlled so as to have a larger temperature difference ⁇ T. Therefore, the quenching mode M1 has a larger work load of the liquid refrigerant Rl than the slow cooling mode M2, and the cooling capacity of the salt water B is higher.
  • the control device 4 sets the temperature above the freezing point Tf as the threshold value SH, controls the drive of the pressure adjusting valve 27 in the quenching mode M1 when the temperature of the salt water B is above the threshold value SH, and slow-cools mode when the temperature of the salt water B is less than the threshold value SH.
  • the drive of the pressure adjusting valve 27 is controlled by M2.
  • the salt water B can be cooled with the largest possible temperature difference (the temperature difference just before freezing) while suppressing the freezing of the salt water B. Therefore, the salt water B can be cooled in a shorter time while suppressing the adhesion of ice into the inner pipe 233. Therefore, the production efficiency of the ice slurry S is improved.
  • the threshold value SH is not particularly limited and varies depending on the performance of each part, but for example, the temperature is preferably 0 ° C. to 7 ° C. higher than the freezing point Tf and 3 ° C. to 5 ° C. higher than the freezing point Tf. Is more preferable.
  • the salt water B can be cooled to a lower temperature in the quenching mode M1 while suppressing the freezing of the salt water B, so that the salt water B can be cooled in a shorter time and the production efficiency of the ice slurry S is improved.
  • the control device 4 may have a drive mode other than the quenching mode M1 and the slow cooling mode M2. Further, the control device 4 may have only the slow cooling mode M2.
  • the cooling system 1 has been described above.
  • a cooling system 1 for example, an ice slurry S made from seawater can be continuously generated. Therefore, the cooling system 1 can be installed in, for example, a fishing boat or a fishing port, and the ice slurry S generated by the cooling system 1 can be used for keeping fresh fish cold.
  • the storage tank 31 may be replenished with fresh seawater in an amount commensurate with the amount of ice slurry S consumed for keeping the fresh fish cold by a replenishment pump (not shown). According to the ice slurry S, it is possible to keep the fresh fish cold for a long time without damaging it.
  • the cooling system 1 of the present embodiment has a stirring device 5 for stirring the salt water B in the cooler 23, in addition to the configuration of the first embodiment described above.
  • the stirring device 5 has a rotating shaft 51 arranged along the central axis of the inner pipe 233, a motor 52 for rotating the rotating shaft 51, and a plurality of blades 53 fixed to the rotating shaft 51. Further, the tip of each blade 53 is in contact with the inner peripheral surface of the inner pipe 233.
  • the rotation shaft 51 is rotated, the blades 53 rotate, and spiral convection occurs in the salt water B flowing in the inner pipe 233. Therefore, the heat exchange efficiency between the liquid refrigerant Rl and the salt water B is increased, and the salt water B can be cooled more efficiently.
  • the ice can be scraped off by the blade 53. Therefore, the growth of ice on the inner peripheral surface of the inner tube 233 can be suppressed, and the decrease in the production efficiency of the ice slurry S can be suppressed.
  • each blade 53 may be non-contact with the inner peripheral surface of the inner pipe 233.
  • the dimensional accuracy of the inner pipe 233 and the blade 53 is not required, so that the device configuration becomes simpler.
  • the present invention is not limited thereto.
  • the configuration of each part can be replaced with an arbitrary configuration that exhibits the same function, or an arbitrary configuration can be added.
  • the salt water B is used as the cooling medium, but the cooling medium is not limited to this.
  • the cooling medium may be various aqueous solutions such as various drinking waters and calcium chloride aqueous solutions.
  • the cooling system 1 is not limited to the application for producing the ice slurry S, and for example, liquids, particularly water, soft drinks, milk, fruit juices, vegetable juices, alcoholic drinks and other various drinking waters are unfrozen. It may be used for cooling as it is. That is, the cooling system 1 may be used as a cooling system. Further, the cooling system 1 may be used as a chiller (cooling water circulation device) for cooling a target device or sample.
  • the operation control method of the cooling system 1 having the cooler 23 for cooling the salt water B as the cooling medium by heat exchange with the liquid refrigerant R1 supplies the liquid refrigerant Rl with the high-pressure gaseous gas refrigerant Rg.
  • the temperature of the liquid refrigerant R1 in the cooler 21 is controlled. Therefore, the temperature Ta of the liquid refrigerant Rl in the refrigerant storage unit 234 can be maintained at the target temperature Tt (difference from the target temperature Tt can be suppressed), and heat exchange between the liquid refrigerant Rl and the salt water B is desired. It can be performed stably under the conditions of. Thereby, the ice slurry S can be stably and efficiently produced. In addition, the ice slurry S produced becomes more homogeneous, and high-quality ice slurry S can be produced. Therefore, its industrial applicability is great.
  • Cooling system 2 ... Refrigerator circuit, 21 ... Compressor, 22 ... Condenser, 221 ... Blower fan, 23 ... Cooler, 231 ... Main evaporator, 232 ... Outer pipe, 233 ... Inner pipe, 234 ... Refrigerator storage Department, 235 ... Sub-evaporator, 236 ... Piping, 237 ... Space, 238 ... Dehumidifying member, 239 ... Pressure sensor, 24 ... Liquid level measuring unit, 241 ... Refrigerator storage pipe, 242 ... Liquid level detection sensor, 243 ... Piping, 251 ... Piping, 252 ... Piping, 253 ... Piping, 254 ... Piping, 26 ...

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  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Mechanical Engineering (AREA)
  • Thermal Sciences (AREA)
  • General Engineering & Computer Science (AREA)
  • Devices That Are Associated With Refrigeration Equipment (AREA)
  • Production, Working, Storing, Or Distribution Of Ice (AREA)

Abstract

La présente invention régule la température de fluide frigorigène liquide, de sorte que des propriétés de refroidissement stabilisées peuvent être mises en évidence.　Dans ce procédé de commande du fonctionnement d'un système de réfrigération 1 comportant un refroidisseur 23 qui refroidit l'eau salée B par échange de chaleur avec un fluide frigorigène liquide Rℓ, le fluide frigorigène liquide Rℓ est alimenté par un fluide frigorigène gazeux Rg dans un état gazeux à haute pression pour réguler la température du fluide frigorigène liquide Rℓ à l'Intérieur du refroidisseur 23. En outre, un fluide frigorigène R est comprimé avec un compresseur 21 pour générer le fluide frigorigène gazeux Rg, et le fluide frigorigène gazeux Rg est condensé avec un condenseur 22 pour générer le fluide frigorigène liquide Rℓ. En outre, sur la base de la pression du fluide frigorigène liquide Rℓ à l'intérieur du refroidisseur 23, la quantité de fluide frigorigène gazeux Rg fournie au fluide frigorigène liquide Rℓ est contrôlée par rétroaction.
PCT/JP2021/046894 2020-12-25 2021-12-19 Procédé de commande de fonctionnement et système de refroidissement WO2022138520A1 (fr)

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Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPH04251176A (ja) * 1990-12-29 1992-09-07 Daikin Ind Ltd 製氷装置
JP2000055495A (ja) * 1998-08-05 2000-02-25 Sanyo Electric Co Ltd 氷蓄熱槽を備えた空気調和装置
JP2001033109A (ja) * 1999-07-21 2001-02-09 Daikin Ind Ltd 冷凍装置
JP2004148966A (ja) * 2002-10-30 2004-05-27 Denso Corp 冷凍サイクル装置

Patent Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPH04251176A (ja) * 1990-12-29 1992-09-07 Daikin Ind Ltd 製氷装置
JP2000055495A (ja) * 1998-08-05 2000-02-25 Sanyo Electric Co Ltd 氷蓄熱槽を備えた空気調和装置
JP2001033109A (ja) * 1999-07-21 2001-02-09 Daikin Ind Ltd 冷凍装置
JP2004148966A (ja) * 2002-10-30 2004-05-27 Denso Corp 冷凍サイクル装置

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