WO2012002248A1 - Appareil de réfrigération - Google Patents

Appareil de réfrigération Download PDF

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Publication number
WO2012002248A1
WO2012002248A1 PCT/JP2011/064384 JP2011064384W WO2012002248A1 WO 2012002248 A1 WO2012002248 A1 WO 2012002248A1 JP 2011064384 W JP2011064384 W JP 2011064384W WO 2012002248 A1 WO2012002248 A1 WO 2012002248A1
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WO
WIPO (PCT)
Prior art keywords
refrigerant
hot water
radiator
refrigeration cycle
refrigeration
Prior art date
Application number
PCT/JP2011/064384
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English (en)
Japanese (ja)
Inventor
大竹　雅久
英孝 佐々木
説 長谷川
賢 川久保
西川　弘
Original Assignee
三洋電機株式会社
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Application filed by 三洋電機株式会社 filed Critical 三洋電機株式会社
Publication of WO2012002248A1 publication Critical patent/WO2012002248A1/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
    • F25B7/00—Compression machines, plants or systems, with cascade operation, i.e. with two or more circuits, the heat from the condenser of one circuit being absorbed by the evaporator of the next circuit
    • 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
    • F25B2339/00—Details of evaporators; Details of condensers
    • F25B2339/04—Details of condensers
    • F25B2339/047—Water-cooled condensers
    • 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
    • F25B29/00—Combined heating and refrigeration systems, e.g. operating alternately or simultaneously
    • F25B29/003—Combined heating and refrigeration systems, e.g. operating alternately or simultaneously of the compression type system

Definitions

  • the present invention relates to a refrigeration apparatus used for freezing or refrigeration of food or the like. More specifically, the present invention relates to a refrigeration apparatus that supplies hot water using waste heat generated during cooling (hereinafter referred to as “cooling waste heat” as appropriate).
  • cooling waste heat from the refrigeration cycle is released from the radiator to the atmosphere, etc.
  • hot water used in the same facility is separated by another boiler or the like. It is done to supply using.
  • cooling waste heat is not effectively used.
  • Patent Document 2 an attempt has been made to save energy by effectively using the cooling waste heat of the refrigeration cycle to save energy (for example, Patent Document 2).
  • Patent Document 2 in addition to heating hot water using a heat pump cycle (first refrigerant circulating in the first refrigerant circuit) using air as a heat source, waste from a refrigerator that cools a showcase is disclosed.
  • first refrigerant circulating in the first refrigerant circuit waste from a refrigerator that cools a showcase is disclosed.
  • second refrigerant flowing through the second refrigerant circuit the temperature of the hot water supply water can be raised in a short time.
  • the refrigeration cycle using carbon dioxide as a refrigerant is a transcritical cycle in which the pressure on the high-pressure side exceeds the critical pressure of the refrigerant, and especially under high outside air temperature conditions, the refrigeration effect (refrigerant ratio enthalpy difference at the inlet / outlet of the evaporator) The decline is remarkable. Therefore, compared with the conventional chlorofluorocarbon refrigerant, there is a problem that the refrigerating capacity is greatly reduced when the outside air temperature is increased, and the cooling efficiency (refrigeration COP: refrigeration performance coefficient) of the basic refrigeration cycle is low. Therefore, it was necessary to improve the refrigeration capacity and cycle efficiency of the basic refrigeration cycle, and to efficiently recover waste heat suitable for the transcritical cycle to further save energy.
  • the present invention has been made in view of the above circumstances, and can effectively use the waste heat when cooling foods and the like to perform hot water supply and improve the cooling capacity and cooling efficiency.
  • An object of the present invention is to provide a simple refrigeration apparatus.
  • the refrigeration apparatus of the first invention is formed by sequentially connecting a first compressor, a first radiator, a first pressure reducer, an intermediate pressure receiver, a supercooler, a second pressure reducer, and an evaporator with a refrigerant pipe,
  • a first refrigeration cycle circuit having an auxiliary refrigerant circuit for sucking refrigerant in the pressure receiver in the middle of a compression stroke of the first compressor, a second compressor, a second radiator, a third pressure reducer, and the excess compressor
  • a second refrigeration cycle circuit formed by sequentially connecting a cooler with a refrigerant pipe, and the refrigerant of the first refrigeration cycle circuit by the evaporating action of the refrigerant of the second refrigeration cycle circuit in the subcooler And the hot water is heated by the heat radiation action of the refrigerant in the second refrigeration cycle circuit in the second radiator.
  • a refrigerating apparatus is a refrigeration unit that houses the first compressor, first radiator, first decompressor, intermediate pressure receiver, and auxiliary refrigerant circuit, and a show that houses the second decompressor and evaporator.
  • a supercooling hot water supply device that houses the second compressor, the second radiator, the third pressure reducer, and the supercooler, and a second radiator of the supercooling hot water supply device are connected via a water pipe.
  • a hot water storage device including a hot water tank.
  • the refrigeration apparatus is characterized in that the first refrigeration cycle circuit includes a second receiver between the intermediate pressure receiver and the subcooler.
  • the refrigeration apparatus is the throttle means in which the opening of the first pressure reducer is adjustable, and the opening degree of the throttle means is small when the amount of hot water stored in the hot water supply tank is large and the amount of hot water is small. It is characterized in that it is controlled so as to become large sometimes.
  • a refrigeration apparatus includes a third radiator arranged in parallel with the second radiator, and when heating of the hot water is not required, the refrigerant from the refrigerant to the atmosphere in the third radiator. It is characterized by performing heat dissipation.
  • a refrigeration apparatus provides a water radiator connected to the second radiator via a water pipe, and when heating of the hot water is not required, the water radiator can Heat radiation to
  • the refrigeration apparatus of the seventh invention is characterized in that the refrigerant sealed in the first refrigeration cycle circuit is carbon dioxide, and the first radiator acts as a gas cooler.
  • the refrigeration apparatus is characterized in that the refrigerant enclosed in the second refrigeration cycle circuit is carbon dioxide, and the second radiator acts as a gas cooler.
  • the refrigerant of the first refrigeration cycle circuit after passing through the first pressure reducer in the intermediate pressure receiver is gas-liquid separated, and the gas phase refrigerant that does not contribute to cooling is supplied to the auxiliary Since it can be sucked in the middle of a compression stroke that is higher than the suction pressure of the first compressor and lower than the discharge pressure via the refrigerant circuit, the compression power of the first compressor can be reduced, and the cooling of the refrigeration apparatus Efficiency can be improved.
  • the refrigeration effect of the first refrigeration cycle (the refrigerant at the inlet / outlet of the evaporator)
  • the specific enthalpy difference increases and the refrigeration capacity increases. Since the second refrigeration cycle having a higher evaporation temperature (evaporation pressure) than that of the first refrigeration cycle can perform refrigeration corresponding to the supercooling, the cooling efficiency of the refrigeration apparatus is improved.
  • Hot water supply can be performed by effectively using.
  • the refrigeration apparatus comprises the first compressor, the first radiator, the first decompressor, the refrigeration unit that houses the intermediate pressure receiver and the auxiliary refrigerant circuit, the second decompressor, A showcase for storing the evaporator, a supercooling hot water supply device for storing the second compressor, second radiator, third decompressor and supercooler, and a water pipe for the second radiator of the supercooling hot water supply device And a hot water storage device having a hot water supply tank connected via a combination of the required number of each component device, so that it is suitable for cooling load and hot water supply load, has excellent cooling performance, and reduces cooling waste heat. It is possible to easily construct an energy-saving refrigeration apparatus that can effectively use hot water.
  • the first refrigeration cycle circuit since the first refrigeration cycle circuit includes the second receiver between the intermediate pressure receiver and the subcooler, gas-liquid separation in the intermediate pressure receiver Excess refrigerant can be stored in the second receiver without impairing performance. As a result, a suitable amount of circulating refrigerant corresponding to the operating conditions can be maintained, and a highly efficient cooling operation corresponding to fluctuations in the outside air conditions and the cooling / hot water supply load can be performed.
  • the first pressure reducer is a throttle means whose opening degree can be adjusted, and the opening degree of the throttle means is small when the amount of hot water stored in the hot water supply tank is large.
  • the amount of water is small, it is controlled so as to increase, so that it is possible to perform a suitable and highly efficient operation corresponding to the fluctuation of the hot water supply load. That is, in a situation where the hot water supply tank is filled with hot water and heating water is not required to be heated, the opening of the throttle means as the first pressure reducer is reduced to increase the amount of heat released by the first radiator. Improve cooling capacity and refrigeration efficiency.
  • the amount of hot water in the hot water supply tank is small and it is necessary to heat the hot water
  • the amount of heat dissipated in the first radiator is reduced by increasing the opening of the throttling means to flow into the subcooler. Maintain high coolant temperature and specific enthalpy.
  • the amount of heat exchanged in the subcooler that is, the heat absorption amount of the second refrigeration cycle increases, and the evaporation temperature of the second refrigeration cycle increases.
  • the heating capacity and hot water supply efficiency of the second refrigeration cycle can be improved.
  • the second refrigeration cycle circuit includes a third radiator disposed in parallel with the second radiator, and heating of the hot water is not required. Since heat can be radiated from the refrigerant to the atmosphere in the third radiator, the atmosphere can be used as a heat source even in a state where the amount of remaining hot water in the hot water supply tank is sufficient, that is, in a state where boiling water is not required to be boiled. As described above, the refrigerant of the first refrigeration cycle can be supercooled. Thereby, the cooling capacity of a freezing apparatus can be increased and cooling efficiency can be improved. As a result, it is possible to perform highly efficient operation corresponding to fluctuations in the hot water supply load and the cooling load.
  • the refrigeration apparatus of the sixth aspect of the present invention when a water radiator connected to the second radiator via a water pipe is provided and heating of the hot water is not required, Therefore, the first refrigeration cycle circuit can be supercooled by the second refrigeration cycle circuit without increasing the amount of hot water. As a result, the cooling capacity can be increased without increasing the hot water supply capacity, and the cooling efficiency can be improved. As a result, it is possible to perform highly efficient operation corresponding to fluctuations in the hot water supply load and the cooling load.
  • the refrigerant sealed in the first refrigeration cycle circuit is carbon dioxide and the first radiator acts as a gas cooler, the ozone layer destruction due to refrigerant leakage is eliminated. Moreover, the influence on global warming can be made extremely small.
  • the refrigerant sealed in the second refrigeration cycle circuit is carbon dioxide, and the second radiator acts as a gas cooler, so that hot water is boiled with high efficiency. be able to.
  • FIG. 1 is a schematic configuration diagram of a refrigeration apparatus according to a first embodiment of the present invention. It is sectional drawing of the intermediate pressure receiver which concerns on the 1st Embodiment of this invention. It is the pressure and enthalpy diagram which showed the refrigerating cycle of this invention. It is a schematic block diagram of the freezing apparatus which concerns on the 2nd Embodiment of this invention. It is a schematic block diagram of the freezing apparatus which concerns on the 3rd Embodiment of this invention. It is a schematic block diagram of the freezing apparatus which concerns on the 4th Embodiment of this invention.
  • FIG. 1 is a schematic configuration diagram of a refrigeration apparatus according to the first embodiment of the present invention.
  • the refrigeration apparatus according to the first embodiment includes a first refrigeration cycle circuit 91, a second refrigeration cycle circuit 92, and a hot water supply circuit 93.
  • the refrigeration unit 10, the supercooling hot water supply apparatus 30, the showcase 40, and the hot water storage apparatus 50 are comprised by accommodating and unitizing the refrigeration equipment (element component) which comprises a refrigeration circuit.
  • the first refrigeration cycle circuit 91 employs a two-stage compression compressor described later as the first compressor 1.
  • the first refrigeration cycle circuit 91 includes a discharge unit of the second-stage compression element of the first compressor 1, a first radiator 2, an expansion valve 3 as a first pressure reducer, an intermediate pressure receiver 14, and a subcooler. 5, a first refrigeration cycle circuit side flow path 5 a, an internal heat exchanger 6 medium pressure side flow path, a strainer 9, an expansion valve 13 as a second pressure reducer, an evaporator 4, and a low pressure side flow of the internal heat exchanger 6.
  • the refrigerant flows in order through the passage and the accumulator 8, and is connected by a refrigerant pipe so as to form a closed circuit that returns to the suction portion of the first-stage compression element of the first compressor 1.
  • the first refrigeration cycle circuit 91 is configured such that the refrigerant flows in order through the pipe 16, the intermediate cooler 7, and the pipe 17 through which the refrigerant discharged from the discharge portion of the first compression element of the first compressor 1 flows.
  • paragraph compression element of the 1 compressor 1 is provided.
  • the first refrigeration cycle circuit 91 includes a refrigerant pipe 17 b that connects the intermediate pressure receiver 14 and the pipe 17.
  • the pipe 17 and the pipe 17 b function as an auxiliary refrigerant circuit that sucks the refrigerant in the intermediate pressure receiver 14 during the compression stroke of the first compressor 1.
  • carbon dioxide (R744) is used as the refrigerant.
  • the first compressor 1 is for compressing a low-pressure refrigerant into a high-pressure state.
  • the first compressor 1 is a rotary two-stage compression type including a first-stage compression element, that is, a low-pressure side compression element, and a second-stage compression element, that is, a high-pressure side compression element.
  • the first compressor 1 other known compressors such as a scroll type, a reciprocating type, and a screw type can be used. Moreover, it is possible to provide two or more first compressors 1, which makes it possible to perform capacity control (number control) according to the cooling load. Moreover, although the 1st compressor 1 which concerns on this embodiment is an inverter drive system, a constant speed type is also employable. In the inverter drive system, it is possible to change the rotation speed of the compressor in accordance with the cooling load, and it is possible to operate with higher efficiency compared to the control of the number of constant speed compressors that repeatedly start and stop the compressor. Further, the discharge pipe 15 of the second-stage compression element of the first compressor 1 is provided with a pressure sensor P2 that detects the refrigerant pressure.
  • P2 pressure sensor
  • the first radiator 2 is a heat exchanger for releasing the heat of the refrigerant to the atmosphere, and for example, a fin-and-tube heat exchanger can be adopted. Moreover, the 1st heat radiator 2 is provided with the fan 2f for supplying the air which heat-exchanges with a refrigerant
  • the expansion valve 3 serving as the first pressure reducer is for reducing the refrigerant that has radiated heat to the atmosphere with the first heat radiator 2 and having a low temperature by squeezing and expanding it to an intermediate pressure.
  • a capillary tube, a temperature type expansion valve, an electric expansion valve or the like can be adopted.
  • an electric expansion valve is used.
  • the opening degree of the expansion valve 3 is controlled by the control device 95 so that the pressure of the high-pressure refrigerant detected by the pressure sensor P2 provided in the discharge pipe 15 becomes a predetermined value.
  • the intermediate pressure receiver 14 is for separating the gas-liquid two-phase refrigerant decompressed to the intermediate pressure by the expansion valve 3 into gas-liquid separation, that is, separating the refrigerant into vapor refrigerant (gas phase refrigerant) and liquid refrigerant (liquid phase refrigerant). It is.
  • the intermediate pressure receiver 14 also functions as a refrigerant receiver that stores excess refrigerant in order to appropriately maintain the amount of refrigerant circulating in the refrigeration cycle.
  • FIG. 2 is a cross-sectional view of the intermediate pressure receiver 14 according to the present embodiment.
  • the intermediate pressure receiver 14 includes a receiver main body container 14T, a refrigerant inlet 14d and a vapor refrigerant outlet 14e provided in the upper part of the container 14T, and a liquid refrigerant outlet 14f for taking out the refrigerant in the lower part of the container 14T.
  • the receiver main body container 14T is configured by sealingly joining the upper end plate 14b to one end portion (upper end portion) of the cylindrical receiver body 14a and sealingly joining the lower end plate 14c to the other end portion (lower end portion). ing.
  • the refrigerant inlet 14d and the vapor refrigerant outlet 14e of the intermediate pressure receiver 14 are respectively provided with liquid refrigerant capturing members 14g and 14h for efficient gas-liquid separation.
  • a wire net, a punching metal, a shielding plate, or the like can be adopted as the liquid refrigerant capturing members 14g and 14h.
  • a wire mesh is used as the wire net. Then, the wire net is rounded into a cylindrical shape, and the lower end portion is crushed and sealed and fixed, and is inserted into a pipe serving as the refrigerant inlet 14d and the vapor refrigerant outlet 14e and fixed.
  • the liquid refrigerant capturing member 14g can suppress the disturbance of the liquid level caused by the refrigerant flowing from the refrigerant inlet 14d colliding with the refrigerant liquid level, and has the effect of improving the gas-liquid separation performance.
  • the supercooler 5 is a heat exchanger for further cooling the liquid refrigerant in the first refrigeration cycle circuit 91 that has been gas-liquid separated by the intermediate pressure receiver 14.
  • the subcooler 5 includes a first refrigeration cycle circuit side flow path 5a and a second refrigeration cycle circuit side flow path 5b, and the refrigerant flowing through the flow path is configured to be able to exchange heat.
  • Each of the flow paths is configured such that the flow direction of the refrigerant is opposed to each other, thereby improving the efficiency of heat exchange, and the degree of supercooling of the refrigerant on the first refrigeration cycle circuit side, that is, the supercooler.
  • the entrance / exit temperature difference of 5a can be enlarged.
  • the subcooler 5 according to the present embodiment uses a plate heat exchanger.
  • various heat exchangers such as a double pipe type and a tube contact type can be adopted in addition to the plate type.
  • Plate type heat exchangers are excellent in that heat exchange efficiency is high and the space occupied by heat exchangers can be reduced.
  • Double pipe type and tube contact type are easy to manufacture and process, and pressure resistance It is excellent in that it can be easily increased.
  • the internal heat exchanger 6 performs heat exchange between the medium-pressure refrigerant that has exited the subcooler 5 and the low-pressure refrigerant that flows out of the evaporator 4, and heat for cooling the medium-pressure refrigerant and heating the low-pressure refrigerant. It is an exchanger.
  • the internal heat exchanger 6 includes an intermediate pressure side flow path and a low pressure side flow path, and is configured so that the refrigerant flowing through the flow path can exchange heat and the flow directions of the refrigerant face each other.
  • the internal heat exchanger 6 uses a plate heat exchanger, but other types, for example, various heat exchangers such as a double tube type and a tube contact type can be adopted. As a simple method, the internal heat exchanger 6 can also be configured by applying the refrigerant forward pipe 22 and the refrigerant return pipe 23 in contact with each other.
  • the strainer 9 is for removing foreign matters in the refrigerant circuit and preventing problems such as clogging of the expansion valve 13, and is provided in the refrigerant piping upstream of the expansion valve 13.
  • the expansion valve 13 as the second pressure reducer is for reducing the pressure of the medium-pressure and low-temperature refrigerant flowing through the refrigerant forward pipe 22 by throttling to obtain a low-pressure and low-temperature refrigerant (normal gas-liquid two-phase state).
  • a capillary tube, a temperature type expansion valve, an electric expansion valve, or the like can be employed. In the refrigeration apparatus according to the present embodiment, an electric expansion valve is used.
  • control device 97 controls the degree of superheat of the outlet side refrigerant of the evaporator 4, that is, the refrigerant temperature at the outlet of the evaporator 4 detected by the evaporator outlet refrigerant temperature sensor T7 described later, and the evaporator inlet refrigerant temperature sensor T6 described later.
  • the opening degree of the expansion valve 13 is controlled so that the difference between the refrigerant temperature at the inlet of the evaporator 4 detected in step S1 becomes a predetermined value.
  • the evaporator 4 is a heat exchanger for cooling food and the like by absorbing heat due to the evaporation of the refrigerant, and employs a fin-and-tube heat exchanger.
  • the inlet pipe of the evaporator 4 is provided with an evaporator inlet refrigerant temperature sensor T6 for detecting the refrigerant temperature at the inlet of the evaporator 4, and the outlet pipe of the evaporator 4 is connected to the outlet of the evaporator 4.
  • An evaporator outlet refrigerant temperature sensor T7 for detecting the refrigerant temperature is provided.
  • the evaporator 4 includes a fan 4f for exchanging heat with the refrigerant and supplying cooled air. In the evaporator 4, the air supplied by the fan 4 f is cooled by evaporation of the refrigerant to become a low temperature, and then supplied to a cold storage space such as food.
  • the accumulator 8 is for preventing the liquid refrigerant from being sucked into the first compressor 1, and has a function of performing gas-liquid separation inside and temporarily storing the liquid refrigerant. In particular, the function is exhibited at the time of start-up and defrosting operation.
  • a pressure sensor P1 for detecting the pressure of the refrigerant sucked from the compressor is attached on a pipe 19 connected from the accumulator 8 to the suction port of the compressor.
  • the intercooler 7 is a heat exchanger for performing heat exchange between the refrigerant discharged from the first-stage compression element of the first compressor 1 and the atmosphere and cooling the refrigerant. Thereby, the compression power of the 1st compressor 1 can be reduced and cooling efficiency can be improved.
  • the intercooler 7 is a fin-and-tube heat exchanger, and a fan 2 f of the first radiator 2 is used as a fan for supplying air for heat exchange with the refrigerant.
  • the intermediate cooler 7 shares the cooling fin with the 1st heat radiator 2, and is comprised integrally. Since the intermediate cooler 7 is not an essential component, the intermediate cooler 7 can be omitted.
  • the second refrigeration cycle circuit 92 includes a second compressor 31, a refrigerant passage 32 a of the second radiator 32, an expansion valve 33 as a third decompressor, and a second refrigeration cycle circuit side passage of the subcooler 5. 5b and a closed circuit in which the refrigerant flows in order through the accumulator 38 and returns to the second compressor 31.
  • carbon dioxide is enclosed as a refrigerant in the second refrigeration cycle.
  • the refrigeration cycle using the carbon dioxide refrigerant has a transcritical cycle in which the high pressure side exceeds the critical pressure of the refrigerant, and thus has an advantage that water can be heated to a high temperature and with high efficiency.
  • the second compressor 31 is for compressing a low-pressure refrigerant into a high-pressure state.
  • the pressure of the refrigerant discharged from the second compressor 31 is a pressure exceeding the critical pressure.
  • the second compressor 31 is a rotary type two-stage compression type including a first-stage compression element, that is, a low-pressure side compression element, and a second-stage compression element, that is, a high-pressure side compression element.
  • the second compressor 31 other types of compressors such as a scroll type and a rotary type one-stage compression method may be employed.
  • the 2nd compressor 31 is driven by the inverter and can change driving
  • the discharge pipe 35 of the second compressor 31 is provided with a discharge refrigerant temperature sensor T3 for detecting the temperature of the refrigerant discharged from the second compressor 31.
  • the second radiator 32 is a heat exchanger for exchanging heat between the refrigerant and water and heating hot water to boil hot water.
  • the refrigerant flow path 32a and the water flow path 32b of the second radiator 32 are configured such that heat exchange is possible and the flow directions are opposed to each other. Since the refrigerant pressure inside the refrigerant flow path 32a of the second radiator 32 exceeds the critical pressure, the second radiator 32 acts as a gas cooler. That is, the refrigerant does not condense inside the refrigerant flow path 32a of the second radiator 32, and its temperature decreases as the water is cooled by being heated.
  • the refrigerant flow path 32a of the second radiator 32 uses a plurality of small diameter circular tubes so as to withstand high pressure.
  • a pipe member having a petal-like cross section that is, a circular pipe having a plurality of substantially U-shaped grooves in the axial direction of the outer peripheral surface is used.
  • a small-diameter circular tube serving as the refrigerant flow path 32a is joined to the concave portion so as to allow heat exchange.
  • the expansion valve 33 as a third pressure reducer is for constricting and expanding high-pressure refrigerant to a low-pressure state.
  • the expansion valve 33 is an electric expansion valve, and its opening degree is controlled by the control device 96 so that the discharge refrigerant temperature of the second compressor 31 detected by the discharge refrigerant temperature sensor T3 becomes a predetermined value. The This makes it possible to perform hot water supply with high efficiency.
  • the expansion valve 33 other types of throttle devices such as a temperature type expansion valve, a constant pressure expansion valve, a capillary tube, etc. may be employed.
  • the supercooler 5 performs heat exchange between the refrigerant in the first refrigeration cycle circuit 91 and the refrigerant in the second refrigeration cycle circuit 92 to supercool the refrigerant in the first refrigeration cycle circuit 91. It is a heat exchanger.
  • the configuration of the subcooler 5 is as already described.
  • the second refrigeration cycle circuit side flow path 5b functions as an evaporator of the second refrigeration cycle, in which the refrigerant absorbs heat and evaporates.
  • coolant of the 1st refrigerating cycle after overcooling is provided in the exit piping of the 1st refrigerating cycle side flow path 5a of the subcooler 5. ing.
  • the accumulator 38 is for preventing the liquid refrigerant from being sucked into the second compressor 31, and the function thereof is the same as that of the accumulator 8 of the first refrigeration cycle circuit 91.
  • the hot water supply circuit 93 is configured such that piping is connected so that hot water flows through the hot water supply tank 51, the circulation pump 52, and the water flow path 32 b of the second radiator 32 in order, and returns to the hot water supply tank 51.
  • the pipe 59 connected to the suction side of the circulation pump 52 is connected to the lower side of the hot water supply tank 51, whereby low temperature water can be supplied to the second radiator 32.
  • a pipe 60 connected to the outlet of the water flow path 32 b of the second radiator 32 is connected to the upper part of the hot water supply tank 51.
  • the hot water heated by the second radiator 32 is returned to the upper part of the hot water supply tank 51, and the hot water can be stored in a temperature stratified form inside the hot water supply tank 51.
  • a hot water supply pipe 58 is connected to the upper part of the hot water supply tank 51 of the hot water supply circuit 93 via a check valve 56, and a water supply pipe 57 is connected to the lower part of the hot water supply tank 51 via a pressure reducing valve 54 and a check valve 55.
  • the hot water supply pipe 58 is a pipe for supplying hot water from the hot water supply tank 51 to a hot water supply load facility that requires hot water, and the water supply pipe 57 is for supplying city water to the hot water supply tank 51.
  • hot water is supplied from the upper part of the hot water supply tank 51 through the hot water supply pipe 58, and accordingly, hot water flows through the water supply pipe 57 and cold water is supplied to the lower part of the hot water supply tank 51. Supplied.
  • a mixing valve is further provided, and the low temperature hot water (water) taken out from the lower part of the hot water supply tank 51 and the hot water taken out from the upper part of the hot water supply tank 51 are provided. Can also be mixed.
  • a plurality of temperature sensors T9 for detecting the temperature of hot water stored in the tank are attached at different heights. Thereby, the temperature distribution in the hot water supply tank 51 can be measured, and the amount of hot water in the hot water supply tank 51 can be grasped based on the temperature distribution. Further, a temperature sensor T8 for detecting the temperature of hot water heated by the second radiator 32 is attached to the pipe 60 on the outlet side of the water flow path 32b of the second radiator 32.
  • the hot water supply circuit 93 includes a bypass pipe connecting the low temperature pipe 59 and the high temperature pipe 60 and a three-way valve 53.
  • the three-way valve 53 switches whether the water flowing through the circulation pump is supplied from the low-temperature pipe 59 side connected to the hot water supply tank 51 or from the bypass pipe side. Normally, when performing an operation of boiling hot water in the second refrigeration cycle, the three-way valve 53 is switched to supply water from the low-temperature pipe 59 side connected to the hot water supply tank 51.
  • the three-way valve 53 By switching the three-way valve 53 so that water from the bypass pipe side flows, the water extruded by the circulation pump 52 flows through the water flow path 32b of the second radiator 32, passes through the three-way valve 53, and passes through the circulation pump 52.
  • a closed circuit is formed returning to Such a closed circuit is formed immediately after the boiling operation by the second refrigeration cycle is started or after the operation is stopped.
  • the refrigeration unit 10 includes a first compressor 1 that compresses refrigerant, an intermediate cooler 7 that cools an intermediate-pressure refrigerant discharged from the first-stage compression element of the first compressor 1, and a second stage of the first compressor 1.
  • the first radiator 2 that cools the high-temperature and high-pressure refrigerant discharged from the compression element, the expansion valve 3 as the first decompressor, and the intermediate-pressure receiver 14 that performs gas-liquid separation of the intermediate-pressure refrigerant decompressed by the expansion valve 3
  • an accumulator 8 for preventing the liquid refrigerant from being sucked into the first compressor 1.
  • the refrigeration unit 10 includes a control device 95, a discharge pressure sensor P2, a radiator outlet refrigerant temperature sensor T1, a suction pressure sensor P1, and other temperature sensors and pressure sensors (not shown).
  • the refrigeration unit 10 includes a refrigerant outlet pipe connection port connected to the refrigerant outlet side pipe 22 a connected to the liquid refrigerant outlet 14 f of the intermediate pressure receiver 14 and a refrigerant return pipe connection port connected to the accumulator 8.
  • the showcase 40 includes an expansion valve 13 that depressurizes the medium-pressure refrigerant, an evaporator 4 that cools food and the like by the evaporating action of the refrigerant, and a strainer 9 that removes foreign matters in the refrigerant circuit.
  • the showcase 40 also includes a control device 97, an evaporator inlet refrigerant temperature sensor T6, an evaporator outlet refrigerant temperature sensor T7, other refrigerant temperature sensors, a space for storing food, an exhibition shelf, and the like. ing.
  • the showcase 40 includes a refrigerant inlet pipe connection port connected to the strainer 9 and a refrigerant outlet pipe connection port connected to the outlet side of the evaporator 4.
  • each showcase 40 the refrigerant inlet pipe connection port of the showcase 40 is connected to the refrigerant forward pipe 22, and the refrigerant outlet pipe connection port is returned to the refrigerant. Connected to tube 23.
  • the showcase 40 is not necessarily limited to the display of the objects to be cooled, but may be a cold storage that is not intended for display.
  • the supercooling hot water supply device 30 is a refrigeration device constituting a second refrigeration cycle circuit 92 including the supercooler 5, that is, a second compressor 31, a second radiator 32, an expansion valve 33 as a third decompressor, A subcooler 5 and an accumulator 38 are provided.
  • the supercooling hot water supply device 30 includes a control device 96, a discharged refrigerant temperature sensor T3, a supercooling temperature sensor T4, and other refrigerant temperature sensors and pressure sensors. Furthermore, the supercooling hot water supply device 30 is connected to the connection port of the pipe 22a into which the refrigerant of the first refrigeration cycle to be subcooled flows, the connection port of the pipe for the refrigerant after subcooling to flow out, and the second radiator 32.
  • a connection port for incoming hot water (cold water) piping and a connection port for piping 60 for flowing hot water (hot water) heated by the second radiator 32 are provided.
  • the hot water storage device 50 includes a hot water supply tank 51, a three-way valve 53, and a circulation pump 52.
  • the hot water storage device 50 includes a control device 98, a temperature sensor T8, a temperature sensor T9 and other temperature sensors, and a pressure reducing valve 54, a check valve 55, and a check valve 56.
  • a plurality of hot water supply tanks 51 may be provided in series or in parallel depending on the amount of hot water to be stored.
  • the refrigeration apparatus is composed of the refrigeration unit 10, the supercooling hot water supply apparatus 30, the showcase 40, and the hot water storage apparatus 50 that are unitized, so that the installation work can be easily performed.
  • the first refrigeration cycle circuit 91, the second refrigeration cycle circuit 92, and the hot water supply circuit 93 are configured.
  • the pipe connection ports of the devices that are unitized in this way may be connected by piping. In this case, according to the cooling load or hot water supply load required at the installation site, the number of units installed in each unit can be selected, and the required number can be combined.
  • FIG. 3 is a pressure-specific enthalpy diagram showing the refrigeration cycle of the refrigeration apparatus according to the present invention.
  • the horizontal axis represents the refrigerant specific enthalpy (kJ / kg)
  • the vertical axis represents the refrigerant pressure (MPa)
  • the symbol SL represents the saturated liquid line of the refrigerant
  • SV represents the saturated vapor line.
  • 1C is a 1st freezing cycle and 2C is a 2nd freezing cycle.
  • the low-temperature refrigerant vapor indicated by the state a in FIG. 3 is sucked from the first-stage intake port of the first compressor 1, compressed by the first-stage compression element, and the high-temperature medium-pressure refrigerant vapor. And discharged.
  • the refrigerant in this state is indicated by state b in FIG.
  • This refrigerant enters the intercooler 7, where it is cooled by exchanging heat with the atmosphere, and the temperature drops to state c.
  • the refrigerant discharged from the first stage compression element of the first compressor 1 is cooled by the intermediate cooler 7, so the temperature of the refrigerant discharged from the second stage compression element of the first compressor 1 is lowered. This makes it possible to suppress problems caused by abnormally high temperatures such as compressors.
  • the compression power of the 1st compressor 1 can be reduced by employ
  • the refrigerant indicated by the state c exiting the intercooler 7 joins the low-temperature refrigerant indicated by the state n flowing from the auxiliary circuit side (pipe 17b side) at the junction 82.
  • the refrigerant after joining is indicated by a state d.
  • the merged refrigerant is sucked from the second-stage suction port of the first compressor 1, compressed by the second-stage compression element of the first compressor 1, and discharged as a high-temperature and high-pressure refrigerant (state e).
  • state e since carbon dioxide is used as the refrigerant in the first refrigeration cycle, the pressure of the refrigerant discharged from the first compressor 1 may exceed the critical pressure as shown in state e in FIG.
  • the refrigerant discharged from the first compressor 1 flows into the first radiator 2 and is cooled by exchanging heat with the atmosphere. As shown in FIG. 3, when the pressure of the refrigerant in the first radiator 2 exceeds the critical pressure, the refrigerant cooled there does not condense and its temperature decreases as it is cooled.
  • the refrigerant cooled by the first radiator 2 is indicated by a state f.
  • the refrigerant that has exited the first radiator 2 passes through the expansion valve 3 and is squeezed and expanded (equal enthalpy expansion) to reduce the pressure to an intermediate pressure that is higher than the first stage suction pressure and lower than the second stage discharge pressure. Then, the gas-liquid two-phase state is entered as shown in FIG.
  • the intermediate pressure receiver 14 the refrigerant is separated into a vapor refrigerant indicated by the state n and a liquid refrigerant indicated by the state h. Due to the density difference, the vapor refrigerant is located above the receiver container 14T and the liquid refrigerant is contained within the container 14T. Flows downward.
  • the liquid refrigerant capturing member 14g is provided at the refrigerant inlet 14d of the intermediate pressure receiver 14, the mist liquid refrigerant collides and adheres to the refrigerant capturing member 14g and efficiently performs gas-liquid separation. Is possible. Further, the liquid refrigerant capturing member 14g is separated because the refrigerant flowing from the refrigerant inlet 14d can suppress the disturbance of the liquid level caused by the collision with the liquid level of the refrigerant stored below the receiver container 14T. It is possible to prevent re-misting by the refrigerant into which the liquid refrigerant flows, and the gas-liquid separation performance by the intermediate pressure receiver 14 can be further improved.
  • the liquid refrigerant capturing member 14h is provided at the vapor refrigerant outlet 14e of the intermediate pressure receiver 14, the mist liquid refrigerant contained in the vapor refrigerant flowing out from the intermediate pressure receiver 14 is captured by the liquid refrigerant capturing member 14h. Can be separated. Therefore, the gas-liquid separation performance of the intermediate pressure receiver 14 can be further improved.
  • the liquid refrigerant in the state h separated from the gas and liquid by the intermediate pressure receiver 14 flows out from the liquid refrigerant outlet 14f, flows through the pipe 22a, and flows to the cooling load side (the evaporator 4 side). Since the specific enthalpy of the liquid refrigerant flowing out from the intermediate pressure receiver 14 (state h) is smaller than the specific enthalpy of the refrigerant flowing into the intermediate pressure receiver 14 (state g), it corresponds to the specific enthalpy difference between the states g and h. Thus, the refrigerant refrigeration effect in the evaporator 4 is increased.
  • the vapor refrigerant in the state n separated from the gas and liquid by the intermediate pressure receiver 14 flows through the pipe 17b from the vapor refrigerant outlet 14e and is cooled by the intermediate cooler 7 as described above and the branch point. At 82, they merge and become state d. And The air is sucked from the second-stage suction port of the first compressor 1.
  • the vapor refrigerant (state n) that has been gas-liquid separated by the intermediate pressure receiver 14 has a large specific enthalpy and cannot exhibit the refrigeration effect even if it flows into the evaporator 4.
  • the compression power of the first-stage compression element is compared with the case where the refrigerant is returned to the first-stage suction section. Can be reduced. As a result, the refrigeration efficiency of the refrigeration cycle can be improved.
  • the refrigerant in this state is state i.
  • the specific enthalpy of the refrigerant is further reduced, and the refrigeration effect is increased by an amount corresponding to the specific enthalpy difference between the state h and the state i as compared with the case where the refrigerant is not supercooled by the supercooler 5.
  • the liquid refrigerant in the medium pressure / low temperature state i flowing out of the subcooler 5 flows through the intermediate pressure channel of the internal heat exchanger 6 and is cooled by exchanging heat with the low pressure / low temperature refrigerant flowing in the low pressure channel. . That is, the medium-pressure side refrigerant changes from the state i to the state j, and the low-pressure side refrigerant changes from the state m to the state a.
  • the internal heat exchanger 6 cools the medium-pressure refrigerant, thereby preventing the generation of flash gas inside the refrigerant forward pipe 22 and heating the low-pressure refrigerant, thereby preventing wet compression of the first compressor 1. Further, by adopting the internal heat exchanger 6, a large number of two-phase regions having a high heat transfer coefficient can be secured inside the evaporator 4, so that the heat transfer performance of the evaporator 4 can be improved and the cycle performance can be improved. .
  • the refrigerant flowing into the evaporator 4 is represented by a state k and is in a low-pressure gas-liquid two-phase state.
  • the refrigerant exchanges heat with the air to be cooled supplied by the fan 4f, cools the air, and the liquid phase portion evaporates.
  • the refrigerant is a slightly superheated vapor and is represented by state m.
  • the supply of the refrigerant to the evaporator 4 is adjusted by controlling the opening degree of the expansion valve 3 by the control device 97, and as described above, the refrigerant is controlled to be slightly overheated at the outlet of the evaporator 4. Has been.
  • the refrigerant that has flowed out of the evaporator 4 passes through the refrigerant return pipe 23 and flows into the low-pressure side flow path of the internal heat exchanger 6, where it is heat-exchanged with the medium-pressure refrigerant flowing through the medium-pressure side flow path.
  • the refrigerant in this state is state a.
  • the refrigerant passes through the accumulator 8, where it is surely gas-liquid separated, and then flows to the first stage inlet of the first compressor 1 and is compressed.
  • the first refrigeration cycle operates continuously and the refrigeration capacity is exhibited in the evaporator 4.
  • the air cooled by the evaporator 4 circulates in the cold storage space, and the object to be cooled such as food is frozen and refrigerated.
  • the operation of the first compressor 1 is controlled by a control device 95 built in the refrigeration unit 10. Specifically, the rotational speed control and start / stop control of the first compressor 1 are performed so that the pressure of the low-pressure refrigerant detected by the suction pressure sensor P1 provided in the suction refrigerant pipe 19 falls within a predetermined pressure range. Yes.
  • the predetermined pressure range is determined so as to obtain a suitable refrigeration cycle by reading the cold set temperature of the space to be cooled through communication with the control device 97 provided in the showcase 40. Thereby, highly efficient cooling corresponding to the cooling load is performed.
  • the opening degree of the expansion valve 3 serving as the first pressure reducer is controlled so that the pressure of the refrigerant discharged from the first compressor 1 detected by the pressure sensor P2 attached to the pipe 15 becomes a predetermined value. 95. That is, control is performed to increase the opening of the expansion valve 3 if the discharge refrigerant pressure is higher than a predetermined target value, and to decrease the opening of the expansion valve 3 if the discharge refrigerant pressure is lower than a predetermined value. Accordingly, the heat radiation amount of the refrigerant in the first radiator 2, the temperature and specific enthalpy of the refrigerant flowing into the subcooler 5, and the flow rate of the refrigerant flowing through the auxiliary refrigerant circuit are appropriately maintained, and a highly efficient cooling operation is performed. It becomes possible.
  • the opening degree of the expansion valve 3 when the opening degree of the expansion valve 3 is large, the heat release amount of the refrigerant in the first radiator 2 is reduced, and the specific enthalpy of the refrigerant (state g) flowing into the intermediate pressure receiver 14 is increased. Further, the pressure in the intermediate pressure receiver 14 increases. If it does so, the specific enthalpy of the liquid refrigerant (state h) which gas-liquid-separates in the intermediate pressure receiver 14, and flows into the cooling load side will become large. On the contrary, if the opening degree of the expansion valve 3 is small, the amount of heat released from the refrigerant in the first radiator 2 increases, and the specific enthalpy of the refrigerant (state g) flowing into the intermediate pressure receiver 14 decreases.
  • the pressure in the intermediate pressure receiver 14 decreases. Then, the specific enthalpy of the liquid refrigerant (state h) that is separated into gas and liquid in the intermediate pressure receiver 14 and flows to the cooling load side is reduced. Therefore, the control is performed such that when the hot water is required to be heated, the opening of the expansion valve 3 is increased, and when the hot water is not required to be heated, the opening of the expansion valve 3 is decreased.
  • the control device 95 serves as a reference for controlling the expansion valve 3 based on a signal indicating whether or not the hot water supply operation is received by communication from the control device 98 of the hot water storage device 50 and the control device 96 of the supercooling hot water supply device 30.
  • the target discharge pressure value is set. If the target discharge refrigerant pressure is increased, the opening degree of the expansion valve 3 is controlled to be small, and the heat radiation amount of the refrigerant in the first radiator 2 is increased. On the other hand, if the target discharge refrigerant pressure is lowered, the opening degree of the expansion valve 3 is largely controlled, and the heat radiation amount of the refrigerant in the first radiator 2 is increased.
  • reference numeral 2C represents a second refrigeration cycle.
  • the low-temperature refrigerant vapor indicated by the state v in FIG. 3 is drawn into the second compressor 31 and compressed to a high temperature and a high pressure.
  • the refrigerant in this state is indicated by a state w in FIG.
  • the pressure of the refrigerant discharged from the compressor 31 exceeds the critical pressure.
  • the refrigerant compressed by the second compressor 31 flows into the refrigerant flow path 32a of the second radiator 32, where it is cooled by exchanging heat with hot water flowing through the water flow path 32b (state x).
  • the refrigerant does not condense because it is in a supercritical state, and its temperature decreases as it is cooled by heat exchange with water.
  • the refrigerant flow path 32a and the water flow path 32b of the second radiator 32 are configured so that the respective flows face each other, the supercritical refrigerant having a temperature gradient accompanying heat exchange and water Efficient heat exchange is possible.
  • the refrigeration cycle of the present invention uses a carbon dioxide refrigerant that becomes a transcritical cycle, the hot water is hotter than the case of using a fluorocarbon refrigerant that condenses at a constant temperature in the high-pressure side heat exchanger. Is advantageous in that it can be boiled with high efficiency.
  • the high-pressure supercritical refrigerant cooled by the second radiator 32 is throttled by the expansion valve 33, isenthalpy-expanded, and then flows into the second refrigeration cycle circuit side channel 5 b of the subcooler 5.
  • the refrigerant is indicated by a state y in FIG. 3 and is normally in a gas-liquid two-phase state.
  • the refrigerant of the second refrigeration cycle circuit 92 exchanges heat with the refrigerant of the first refrigeration cycle flowing through the first refrigeration cycle circuit side flow path 5a, and the liquid phase portion evaporates.
  • the refrigerant of the first refrigeration cycle is supercooled by the evaporation action of the refrigerant of the second refrigeration cycle.
  • the low-temperature vapor refrigerant (state v) that has flowed out of the second refrigeration cycle circuit side flow path 5b of the subcooler 5 flows into the accumulator 38, where it is reliably gas-liquid separated, and then the second compressor 31 It flows into the suction port and is compressed again.
  • the operations described above are continuously performed, and the first refrigeration cycle can be supercooled by the second refrigeration cycle and the hot water can be heated using the waste heat.
  • the rotation speed of the second compressor 31 and the opening degree of the expansion valve 33 are controlled by the control device 96 provided in the supercooling hot water supply device 30.
  • the rotation speed of the second compressor 31 is determined by the refrigerant temperature of the first refrigeration cycle after the supercooling detected by the supercooling temperature sensor T4 provided at the first refrigeration cycle circuit side outlet of the subcooler 5 being predetermined. It is adjusted to become the value of. As a result, an appropriate degree of supercooling corresponding to the cooling load can be realized, and a highly efficient cooling operation can be realized.
  • control device 96 of the supercooling hot water supply device 30 communicates with the control device 95 provided in the refrigeration unit 10, and in conjunction with the start / stop of the first compressor 1 of the first refrigeration cycle circuit 91, The start and stop of the two compressors 31 are controlled. This can prevent unnecessary supercooling operation when the first compressor 1 of the first refrigeration cycle circuit 91 is stopped.
  • the opening degree of the expansion valve 33 is adjusted so that the discharge refrigerant temperature detected by the discharge refrigerant temperature sensor T3 provided in the discharge pipe 35 becomes a predetermined value. This makes it possible to maintain suitable cycle conditions for boiling hot water to a predetermined temperature, and to perform highly efficient supercooling and hot water supply.
  • cold water taken out from the lower part of the hot water supply tank 51 circulates through the low temperature pipe 59, passes through the three-way valve 53, and is pushed out by the circulation pump 52, so that the water flow path 32 b of the second radiator 32. Flow into.
  • the water is heated by exchanging heat with the high-temperature and high-pressure refrigerant of the second refrigeration cycle.
  • the hot water heated to a high temperature flows through the high temperature pipe 60 and flows into the tank from the upper part of the hot water tank 51.
  • the temperature of the hot water to be boiled is adjusted by the control device 98 of the hot water storage device 50 so as to be a predetermined temperature. Specifically, the number of revolutions of the circulation pump 52 is changed so that the outlet water temperature of the second radiator 32b detected by the temperature sensor T8 attached to the high-temperature pipe 60 becomes a predetermined value, and the circulating hot water is circulated. The flow rate is controlled. In addition, as a method of adjusting the circulating water flow rate, instead of the method of controlling the rotation speed of the circulation pump 52, it is also possible to perform flow rate adjustment using a separately provided flow rate adjustment valve.
  • the supercooler 5 supercools the refrigerant in the first refrigeration cycle circuit 91 by the evaporation action of the refrigerant in the second refrigeration cycle circuit 92.
  • the refrigeration effect of the refrigeration cycle increases, and the refrigeration capacity (cooling capacity) increases. Since the second refrigeration cycle having a higher evaporation temperature (evaporation pressure) than that of the first refrigeration cycle can perform refrigeration corresponding to the supercooling, the cooling efficiency of the refrigeration apparatus is improved. Further, since the hot water is heated by the heat radiation action of the refrigerant in the second refrigeration cycle circuit 92 in the second radiator 32, the waste heat that has been cooled by the amount corresponding to the above-described supercooling, that is, the increase in the refrigeration capacity. Hot water supply can be performed by effectively using.
  • the refrigeration equipment is unitized to include the refrigeration unit 10, the showcase 40, the supercooling hot water supply apparatus 30, and the hot water storage apparatus 50.
  • the opening degree of the expansion valve 3 as the first pressure reducer is controlled so as to be small when the amount of hot water stored in the hot water supply tank 51 is large and large when the amount of hot water is small. Therefore, it is possible to perform a suitable and highly efficient operation according to the fluctuation of the hot water supply load. That is, in a situation where the hot water supply tank 51 is filled with hot water and heating of the hot water is not required, the opening degree of the expansion valve 3 is reduced, the amount of heat released from the first radiator 2 is increased, and the cooling capacity is increased. Improve refrigeration efficiency.
  • the supercooler 5 is reduced by increasing the opening of the expansion valve 3 to reduce the heat radiation amount in the first radiator 2.
  • the temperature and specific enthalpy of the refrigerant flowing into the tank are kept high.
  • the amount of heat exchanged in the subcooler 5, that is, the amount of heat absorbed in the second refrigeration cycle is increased, and the evaporation temperature of the second refrigeration cycle is increased.
  • the heating capacity and hot water supply efficiency of the second refrigeration cycle can be improved.
  • FIG. 4 is a schematic configuration diagram of a refrigeration apparatus according to the second embodiment of the present invention.
  • the refrigeration apparatus according to the second embodiment includes a second receiver 114 between the intermediate pressure receiver 14 and the subcooler 5. This is the difference from the refrigeration apparatus according to the first embodiment described above.
  • the second refrigeration cycle circuit 92 and the hot water supply circuit 93, and the supercooled hot water supply device 30, the showcase 40, and the hot water storage device 50 that house the devices constituting them are the same as the refrigeration device according to the first embodiment already described. Since the same operation and effect are obtained with the same configuration, the description thereof will be omitted, and only the differences from the first embodiment will be described in detail.
  • the first refrigeration cycle circuit 191 includes a second receiver 114 that stores excess refrigerant.
  • the second receiver 114 includes a receiver container body having a space for storing the refrigerant therein, a refrigerant inlet for introducing the refrigerant into the upper part of the space, and a refrigerant outlet for allowing the refrigerant to flow out from the lower part of the space.
  • the refrigerant inlet of the second receiver 114 is connected to the liquid refrigerant outlet 14f of the intermediate pressure receiver 14 via a pipe 22a, and the refrigerant outlet of the second receiver 114 is connected to the first refrigeration cycle of the subcooler 5.
  • a refrigerant pipe is connected to the inlet side of the circuit side flow path 5a.
  • the receiver main body container of the second receiver 114 has the same structure as the main body container 14T of the intermediate pressure receiver 14, and is configured by sealing and joining end plates to both ends of a cylindrical receiver body.
  • the second receiver 114 is accommodated in the refrigeration unit 110.
  • the refrigerant outlet pipe connection port of the refrigeration unit 110 is connected to the refrigerant outlet of the second receiver 114.
  • the refrigerant in the intermediate pressure receiver 14, the refrigerant is separated into vapor refrigerant and liquid refrigerant.
  • the liquid refrigerant separated into gas and liquid flows downward in the receiver container 14T of the intermediate pressure receiver 14 due to the density difference, flows out from the liquid refrigerant outlet 14f, and enters the second receiver 114.
  • the liquid refrigerant flowing into the second receiver 114 flows out from the refrigerant outlet provided below the receiver container of the second receiver 114 and flows to the supercooler 5.
  • a saturated vapor refrigerant is stored in the upper part, and a saturated liquid refrigerant is stored in the lower part.
  • the total amount of refrigerant stored in the second receiver 114 is adjusted by the pressure change in the receiver container and the ratio of vapor refrigerant to liquid refrigerant. That is, a large amount of refrigerant can be stored if the pressure in the receiver container is high, and the amount of refrigerant stored is small if the pressure is low. Moreover, if the ratio of liquid refrigerant becomes high, many refrigerants can be stored, and if the ratio of vapor refrigerant becomes high, the amount of refrigerant stored decreases.
  • the amount of refrigerant circulating through the refrigeration cycle is adjusted by storing excess refrigerant in the intermediate pressure receiver 14 and the second receiver 114.
  • the pressure of the high-pressure side refrigerant detected by the discharge pressure sensor P2 the pressure of the low-pressure refrigerant detected by the suction pressure sensor P1
  • the degree of superheat of the outlet side refrigerant of the evaporator 4 and the like.
  • the operating frequency of the compressor, the opening degree of the expansion valve 3, the opening degree of the expansion valve 13, the rotational speed of the fan 2f, the rotational speed of the fan 4f, and the like are controlled so as to be within an appropriate range.
  • the refrigeration apparatus includes the second receiver 114 in addition to the intermediate pressure receiver 14, more surplus refrigerant can be adjusted. As a result, since a suitable refrigeration cycle operation can be performed in response to a wider range of load fluctuations, the cooling efficiency of the refrigeration apparatus can be improved. In addition, since the refrigerant can be stored in the second receiver 114, the amount of refrigerant stored in the intermediate pressure receiver 14 can be reduced. As a result, since the refrigerant flowing from the refrigerant inlet 14d of the intermediate pressure receiver 14 collides with the liquid level of the refrigerant stored below the receiver container 14T, it is possible to suppress the disturbance of the liquid level.
  • FIG. 5 is a schematic configuration diagram of a refrigeration apparatus according to the third embodiment of the present invention.
  • the same number is attached
  • the refrigeration apparatus according to the third embodiment includes means for releasing heat from the second refrigeration cycle to the atmosphere when the hot water is sufficiently heated. This is the difference from the refrigeration apparatus according to the first embodiment described above.
  • the first refrigeration cycle circuit 91 and the hot water supply circuit 93, and the refrigeration unit 10, the showcase 40, and the hot water storage device 50 that house the devices constituting them are the same as the refrigeration device according to the first embodiment already described. Since the configuration has the same actions and effects, the description thereof will be omitted, and only differences from the first embodiment will be described in detail.
  • the second refrigeration cycle circuit 192 includes a second compressor 131, a switching valve 74, a refrigerant flow path 32a of the second radiator 32, an expansion valve 33 as a third decompressor, and a supercooler. 5, the refrigerant flows in order through the second refrigeration cycle circuit side flow path 5 b, the low pressure side flow path of the internal heat exchanger 64, and the accumulator 38 and returns to the first stage compression element suction port of the second compressor 131.
  • the refrigeration cycle hereinafter referred to as the hot water supply cycle
  • the hot water supply cycle circuit constituted by this closed circuit (hereinafter referred to as the hot water supply cycle circuit)
  • the first refrigeration cycle is supercooled, and at the same time, hot water is utilized utilizing the waste heat. Can do.
  • the second refrigeration cycle circuit 192 includes a pipe 36 and a switching valve 76 for flowing the refrigerant discharged from the intermediate pressure portion of the second compressor 131, that is, the first-stage compression element discharge portion.
  • a refrigerant circuit in which the refrigerant flows in order through the intermediate cooler 67 and the switching valve 77 and returns to the suction portion of the second-stage compression element of the second compressor 131 is provided.
  • the second refrigeration cycle circuit 192 branches from the branch portion 71 provided in the discharge pipe 35 of the second compressor 131, and switches the switching valve 73, the third radiator 62, the internal heat.
  • the refrigerant flows in order through the high-pressure side flow path of the exchanger 64 and the expansion valve 63 as the fourth pressure reducer, and is provided with a refrigerant circuit that reaches the junction 72 provided in the pipe 34.
  • the second refrigeration cycle circuit 192 includes a bypass pipe that connects the first-stage outlet pipe 36 and the second-stage inlet pipe 37 of the second compressor 131 via the switching valve 75.
  • the bypass pipe is a pipe for bypassing the intermediate cooler 67 and circulating the refrigerant when configuring the hot water supply cycle circuit.
  • the second refrigeration cycle circuit 192 includes a pipe that connects the outlet side pipe of the intermediate cooler 67 and the outlet side pipe 69 of the third radiator 62 via the switching valve 78.
  • the connecting pipe is a pipe for connecting the space of the intermediate cooler 67 part sealed by the switching valve 76 and the switching valve 77 and the space of the third radiator 62 part when the hot water supply cycle circuit is configured. It is. This makes it possible to adjust the amount of refrigerant stored in the intermediate cooler 67 part during the hot water supply cycle operation, to prevent abnormal high pressure in the relevant part, and to maintain the circulating refrigerant amount in the hot water supply cycle suitably and to improve the cycle performance. Can be improved.
  • connection place of the said connection piping can make the exit side piping of the intermediate cooler 67 into the entrance side piping of the intermediate cooler 67, and the piping 69 side is the 1st step
  • the refrigeration cycle circuit that radiates heat to the atmosphere when the hot water supply is not required to be heated by the refrigerant circuit added as described above (hereinafter referred to as the atmospheric heat dissipation cycle circuit. Also, the refrigeration cycle realized by this circuit is the atmosphere. A heat release cycle).
  • the refrigerant sucked and compressed by the first stage compression element of the second compressor 131 is discharged from the first stage discharge port, and the intermediate pressure discharge pipe 36, the switching valve 76, the intermediate cooler 67, and the switching valve.
  • the intermediate pressure suction pipe 37, and the second compressor 131 sequentially flow into the second stage suction port, and after being compressed by the second stage compression element, the high pressure discharge pipe 35, the branch point 71, the switching valve 73, the first Three radiators 62, high-pressure side flow path of internal heat exchanger 64, expansion valve 63, junction 72, second refrigeration cycle circuit-side flow path 5b of supercooler 5, low-pressure side flow path of internal heat exchanger 64
  • the accumulator 38 flows in order and returns to the first stage inlet of the second compressor 131.
  • the switching valves 73, 76, and 77 are opened, and the switching valves 74, 75, and 78 are closed.
  • carbon dioxide is enclosed as a refrigerant in the second refrigeration cycle circuit, similarly to the refrigeration apparatus according to the first embodiment.
  • the high-pressure side is a transcritical cycle in which the critical pressure of the refrigerant is exceeded, so that there is an advantage that water can be heated to a high temperature and with high efficiency.
  • Other refrigerants can also be used.
  • the second compressor 131 is a rotary type two-stage compression type as in the first embodiment.
  • the difference is that a first-stage discharge port for discharging the refrigerant after being compressed by the first-stage compression element and a suction port for the second-stage compression element are provided.
  • the intermediate cooler 67 can be connected, and as a result, the cooling efficiency can be improved. Since the intermediate cooler 67 is not an essential component, the intermediate cooler 67 may not be provided.
  • the second compressor 131 employs another type of compressor such as the second compressor 31 similar to the first embodiment that does not include the first-stage discharge port, or a scroll type or rotary type one-stage compression method. It is also possible to do.
  • the second compressor 131 is driven by an inverter, as in the first embodiment, and can change the operating rotational speed. Thereby, the supercooling capacity and the hot water supply capacity can be changed according to the refrigeration load, and highly efficient capacity control becomes possible.
  • the intermediate cooler 67 is a heat exchanger for performing heat exchange between the refrigerant discharged from the first-stage compression element of the second compressor 131 and the atmosphere and cooling the refrigerant. Thereby, the compression power of the 2nd compressor 131 can be reduced and cooling efficiency can be improved.
  • the intermediate cooler 67 is a fin-and-tube heat exchanger, and a fan 62f of a third radiator 62 described later is used as a fan for supplying air for heat exchange with the refrigerant.
  • the intermediate cooler 67 shares a cooling fin with the third radiator 62 and is integrally formed.
  • the third radiator 62 is a heat exchanger for performing heat exchange between the refrigerant discharged from the second-stage compression element of the second compressor 131 and the atmosphere and cooling the refrigerant.
  • the third radiator 62 is a fin-and-tube heat exchanger and includes a fan 62f for supplying air for heat exchange with the refrigerant.
  • the form of the heat exchanger of the intercooler 67 and the third radiator 62 is not limited to this.
  • the intermediate cooler 67 and the third radiator 62 may be included in the supercooling hot water supply device 130 as a unit, or may be configured as a unit different from the supercooling hot water supply device 130.
  • the required number of heat exchanger units can be selected according to the cooling load and hot water supply load of the facility to be installed. Can be installed.
  • the internal heat exchanger 6 4 exchanges heat between the high-pressure refrigerant that has exited the third radiator 62 and the low-pressure refrigerant that flows out of the second refrigeration cycle circuit side flow path 5b of the supercooler 5, and the high-pressure refrigerant Is a heat exchanger for heating the low-pressure refrigerant.
  • the internal heat exchanger 64 includes a high-pressure channel and a low-pressure channel, and is configured so that the refrigerant flowing through the channel can exchange heat and the refrigerant flow directions face each other.
  • the internal heat exchanger 64 according to the present embodiment uses a plate heat exchanger, but other types, for example, various heat exchangers such as a double tube type and a tube contact type can be adopted.
  • the expansion valve 63 as a fourth pressure reducer is for constricting and expanding high-pressure refrigerant to a low-pressure state.
  • the expansion valve 63 is an electric expansion valve, and its opening degree is controlled by the control device 96 so that the discharge refrigerant temperature of the second compressor 131 detected by the discharge refrigerant temperature sensor T3 becomes a predetermined value. The Thereby, it becomes possible to supercool the first refrigeration cycle with high efficiency.
  • the expansion valve 63 other types of expansion devices such as a temperature type expansion valve, a constant pressure expansion valve, a capillary tube, etc. may be employed.
  • the second radiator 32, the expansion valve 33, the supercooler 5 and the accumulator 38 constituting the second refrigeration cycle circuit 192 according to the present embodiment are the same as the refrigeration apparatus according to the first embodiment. Detailed description is omitted.
  • the refrigeration apparatus switches the refrigerant flow path of the second refrigeration cycle circuit 192 by determining whether it is necessary to boil hot water. It is determined whether or not boiling of hot water is required by the control device 98 of the hot water storage device 50 from the hot water temperature in the hot water tank 51 detected by the temperature sensor T9 provided in the hot water tank 51. This is done by determining the amount of hot water inside. That is, the control device 98 determines that the hot water supply needs to be heated when the amount of hot water in the hot water supply tank 51 is smaller than the predetermined amount of hot water, and determines that the heating is unnecessary when the amount is higher than the predetermined amount of hot water. .
  • the predetermined amount of hot water can be determined in advance, or the amount of hot water used can be measured and set by the learning function of the control device 98.
  • the second refrigeration cycle circuit 192 When boiling of hot water is required, the second refrigeration cycle circuit 192 constitutes a hot water cycle circuit, performs supercooling of the first refrigeration cycle, and warms hot water. On the other hand, when it is not necessary to boil hot water, the second refrigeration cycle circuit 192 constitutes an atmospheric heat dissipation cycle circuit, and performs supercooling of the first refrigeration cycle using the atmosphere as a heat dissipation source.
  • a hot water supply cycle circuit is configured in which the refrigerant flows in order through the low-pressure side flow path of the internal heat exchanger 64 and the accumulator 38 and returns to the first-stage compression element suction port of the second compressor 131.
  • the switching operation of the switching valve is performed by the control device 96 of the supercooling hot water supply device 130, and the control device 96 communicates the hot water supply by communication from the control device 98 of the hot water storage device 50 when operating the switching valve. Receive a signal of necessity.
  • the space between the third radiator 62 and the intermediate cooler 67 not used in the hot water supply cycle is connected to the low-pressure side circuit.
  • the switching valve 73 and the expansion valve 63 it is possible to adjust the amount of refrigerant stored in the space, and as a result, appropriately maintain the amount of refrigerant circulating in the cycle. Here you can improve cycle performance.
  • the operation of the hot water supply cycle for supercooling the first refrigeration cycle while warming hot water is the same as that of the refrigeration apparatus according to the first embodiment already described, the operation and effect are also the same. Detailed description will be omitted.
  • the internal heat exchanger 64 is provided. However, in the hot water supply cycle circuit, the refrigerant in the high-pressure side passage of the internal heat exchanger 64 does not flow. I will not. Therefore, as an effect of the refrigeration cycle, it can be considered that the internal heat exchanger 64 is not provided.
  • the switching valves 73, 76, 77 and the expansion valve 33 are opened, and the switching valves 74, 75, 78 are closed.
  • the refrigerant sucked and compressed by the first-stage compression element of the second compressor 131 is discharged from the first-stage discharge port, and the intermediate-pressure discharge pipe 36, the switching valve 76, the intercooler 67, the switching valve 77,
  • the pressure suction pipe 37 and the second compressor 131 sequentially flow to the second stage suction port, and after being compressed by the second stage compression element, the high pressure discharge pipe 35, the branch point 71, the switching valve 73, and the third radiator.
  • the switching operation of the switching valve is performed by the control device 96 of the supercooling hot water supply device 130 based on the hot water supply necessity signal from the control device 98 of the hot water storage device 50.
  • the space of the refrigerant flow path 32a portion of the second radiator 32 that is not used in the atmospheric heat radiation cycle is connected to the low-pressure side circuit.
  • the switching valve 74 and the expansion valve 33 the amount of refrigerant stored in the space can be adjusted, and as a result, the amount of refrigerant circulating in the cycle is appropriately maintained.
  • low-temperature and low-pressure refrigerant vapor is sucked from the first-stage suction port of the second compressor 131 and compressed by the first-stage compression element of the second compressor 131 to become high-temperature intermediate pressure, and then discharged from the first stage. It is discharged to the pipe 36.
  • the refrigerant passes through the switching valve 76, enters the intermediate cooler 67, and is cooled by exchanging heat with the atmosphere in the intermediate cooler 67.
  • the intermediate pressure refrigerant in the intermediate cooler 67 By cooling the intermediate pressure refrigerant in the intermediate cooler 67, the temperature of the refrigerant discharged from the second stage compression element of the second compressor 131 can be kept low, the compression power of the compressor is reduced, and the cycle Efficiency is improved.
  • the refrigerant cooled by the intermediate cooler 67 passes through the switching valve 77 and is sucked from the second-stage suction port of the second compressor 131.
  • the refrigerant is compressed into a high-temperature and high-pressure state by the second-stage compression element of the second compressor 131 and is discharged to the pipe 35. Since carbon dioxide is used as the refrigerant of the second refrigeration cycle circuit 192, the pressure of the refrigerant in this state may exceed the critical pressure.
  • the refrigerant passes through the switching valve 73 and flows into the third radiator 62 and is cooled by exchanging heat with the atmosphere.
  • the refrigerant cooled in the third radiator 62 becomes a high-pressure and low-temperature refrigerant.
  • coolant pressure in the said heat exchanger exceeds the critical pressure, a refrigerant
  • coolant does not condense but temperature falls as it cools.
  • the refrigerant cooled by the third radiator 62 flows through the high-pressure side passage of the internal heat exchanger 64, and is cooled by exchanging heat with the low-pressure and low-temperature refrigerant flowing through the low-pressure side passage. Since the low-pressure refrigerant is heated by the internal heat exchanger 64, it is possible to prevent problems caused by wet compression of the second compressor 131. Further, by adopting the internal heat exchanger 64, the high-pressure refrigerant is cooled, and the specific enthalpy of the refrigerant at the inlet of the second refrigeration cycle circuit side channel 5b of the subcooler 5 acting as an evaporator is reduced. The degree of superheat of the refrigerant at the outlet of the heat exchanger channel 5b can be reduced.
  • the refrigerant that has flowed out of the high-pressure side flow path of the internal heat exchanger 64 is throttled and expanded (equal enthalpy expansion) by the expansion valve 63, and flows to the second refrigeration cycle circuit side flow path 5b of the subcooler 5.
  • the refrigerant flowing into the subcooler 5 is in a low-pressure gas-liquid two-phase state.
  • the refrigerant exchanges heat with the refrigerant of the first refrigeration cycle flowing in the first refrigeration cycle circuit side flow path 5a, and the first refrigeration cycle.
  • the refrigerant is cooled and the liquid phase part evaporates.
  • the refrigerant of the first refrigeration cycle is supercooled by the evaporation action of the refrigerant of the second refrigeration cycle.
  • the low-temperature vapor refrigerant that has flowed out of the second refrigeration cycle circuit side flow path 5b of the subcooler 5 flows into the accumulator 38, where it is reliably gas-liquid separated, and then to the first stage inlet of the second compressor 131. It flows in and is compressed again.
  • the operation described above is performed continuously, and the first refrigeration cycle can be supercooled by the second refrigeration cycle using the atmosphere as a heat source.
  • the rotation speed of the second compressor 131 and the opening degree of the expansion valve 63 are controlled by the control device 96 provided in the supercooling hot water supply device 130.
  • the number of revolutions of the second compressor 131 is determined by the refrigerant temperature of the first refrigeration cycle after the supercooling detected by the supercooling temperature sensor T4 provided at the first refrigeration cycle circuit side outlet of the subcooler 5. It is adjusted to become the value of. As a result, an appropriate degree of supercooling corresponding to the cooling load can be realized, and a highly efficient cooling operation can be realized.
  • the control device 96 of the supercooling hot water supply device 130 communicates with the control device 95 provided in the refrigeration unit 10, and in conjunction with the start / stop of the first compressor 1 of the first refrigeration cycle circuit 91, The start / stop of the two compressors 131 is controlled. This can prevent unnecessary supercooling operation when the first compressor 1 of the first refrigeration cycle circuit 91 is stopped.
  • the opening degree of the expansion valve 63 is adjusted so that the discharge refrigerant temperature detected by the discharge refrigerant temperature sensor T3 provided in the discharge pipe 35 becomes a predetermined value. This makes it possible to maintain a suitable high-pressure side pressure in the transcritical refrigeration cycle, and to perform highly efficient supercooling.
  • the second refrigeration cycle circuit 192 includes the third radiator 62 arranged in parallel with the second radiator 32, and the third radiator 62 removes the refrigerant from the refrigerant. Since heat release to the atmosphere can be performed, the first refrigeration cycle circuit 91 can be supercooled by the second refrigeration cycle circuit 192 without heating hot water. Thereby, even in a state where the amount of remaining hot water in the hot water supply tank 51 is sufficient, that is, in a state where boiling water is not required to be heated, the second refrigeration cycle has a higher evaporation temperature and higher cooling efficiency than the first refrigeration cycle. The first refrigeration cycle can be supercooled to improve refrigeration capacity and cooling efficiency. [Fourth Embodiment] Next, a refrigerating apparatus according to a fourth embodiment, which is another embodiment of the present invention, will be described in detail with reference to the drawings.
  • FIG. 6 is a schematic configuration diagram of a refrigeration apparatus according to the fourth embodiment of the present invention.
  • the same number is attached
  • the refrigeration apparatus according to the fourth embodiment is provided with means for releasing heat from the hot water in the hot water supply circuit to the atmosphere when the hot water is sufficiently heated. This is the difference from the refrigeration apparatus according to the first embodiment described above.
  • a supercooling operation (atmospheric heat radiation operation) using the atmosphere as a heat source can be performed by means different from the refrigeration apparatus according to the third embodiment.
  • the first refrigeration cycle circuit 91 and the second refrigeration cycle circuit 92, and the refrigeration unit 10, the supercooling hot water supply device 30, the showcase 40, and the hot water storage device 50 that house the devices constituting them are the first described above. Since the same operation and effect are produced with the same configuration as the refrigeration apparatus according to the embodiment, the description thereof will be omitted, and only differences from the first embodiment will be described in detail.
  • the refrigeration apparatus is characterized in that the hot water supply circuit 193 includes a water radiator 85.
  • the water radiator 85 is a heat exchanger for exchanging heat between the hot water supplied to the second radiator 32 and the atmosphere and cooling the hot water. It is provided in a water pipe connecting the water flow path 32b.
  • the water radiator 85 is a fin-and-tube heat exchanger, and includes a fan 85f for supplying air for heat exchange with water.
  • the form of the heat exchanger is not limited to this.
  • the hot water supply circuit 193 allows the hot water taken out from under the hot water tank 51 to flow through the three-way valve 53, the circulation pump 52, the water radiator 85, the water flow path 32b of the second radiator 32, and the piping.
  • a closed circuit (hereinafter, referred to as a hot water supply circuit) is formed in which 60 is circulated in sequence and returned to the upper part of the hot water supply tank 51.
  • the hot water supply circuit 193 causes the hot water extruded by the circulation pump 52 to pass through the water radiator 85, the water flow path 32b of the second radiator 32, the bypass pipe and the three-way valve 53 in order.
  • a closed circuit (atmospheric heat radiation circuit) that circulates and returns to the circulation pump 52 is formed.
  • the water radiator 85 can constitute a device as a unit different from the refrigeration unit 10, the supercooling hot water supply device 30 and the showcase 40.
  • the necessary number of heat exchanger units can be installed according to the cooling load and hot water supply load of the facility to be installed.
  • the refrigeration apparatus determines whether or not it is necessary to boil hot water using the same method as the refrigeration apparatus according to the third embodiment. Then, by switching the three-way valve 53, the hot water supply circuit is configured when the hot water is required to be heated, and when the hot water is not required to be heated, the atmospheric heat dissipation circuit is configured. Further, when the hot water is required to be heated, the fan 85f of the water radiator 85 is stopped, and when the hot water is not required to be heated and the first refrigeration cycle needs to be supercooled, the fan 85f is stopped. Drive 85f. These controls are performed by the control device 96 of the supercooling hot water supply device 30 and the control device 98 of the hot water storage device 50.
  • the water radiator 85 does not exchange heat between the hot water and the outside air. Since the hot water supply circuit 193 forms a hot water supply circuit, the hot water supply operation is performed in which the hot water heated by the refrigerant in the circuit of the second refrigeration cycle is stored in the hot water supply tank 51 in the second radiator 32. It will be.
  • the operation of the refrigeration apparatus in this case is the same as that of the refrigeration apparatus according to the first embodiment already described.
  • the hot water that has taken the heat from the refrigerant in the second radiator 32 and has reached a high temperature flows through the three-way valve 53 and the circulation pump 52 into the water radiator 85 without returning to the hot water tank 51.
  • the hot hot water is cooled by exchanging heat with the outside air supplied by the fan 85f.
  • the hot water that has been cooled and cooled to low temperature in the water radiator 85 flows into the water flow path 32b of the second radiator 32, where it exchanges heat with the refrigerant in the second refrigeration cycle flowing in the refrigerant flow path 32a.
  • the refrigerant of the refrigeration cycle can be cooled.
  • the temperature of hot water heated by the second radiator 32 may be lower than when hot water is required. Further, the compressor discharge refrigerant temperature (detected by the temperature sensor T3) of the second refrigeration cycle circuit 92 can also be set low. Thereby, the supercooling efficiency of the second refrigeration cycle can be improved.
  • the water radiator 85 is set to a high temperature on the outlet side of the second radiator 32. It is also possible to provide the pipe 60.
  • the same circuit configuration as the hot water supply circuit can be used without switching the three-way valve 53 even during the atmospheric heat radiation operation.
  • the fan 85f of the water radiator 85 may be operated.
  • the start / stop of the fan 85f may be determined based on the temperature detected by the temperature sensor T9 provided in the hot water supply tank 51, or may be a temperature separately installed in the inlet side pipe of the water radiator 85. You may perform based on the temperature detected by a sensor (not shown).
  • the circulation amount of the hot water is set so that the hot water temperature at the outlet of the second radiator 32 detected by the temperature sensor T8 becomes a predetermined temperature for hot water supply. It is necessary to control, and the compressor discharge refrigerant temperature of the second refrigeration cycle circuit 92 needs to be set to a high temperature as in the case of performing the hot water supply operation.
  • the refrigeration apparatus further includes the water radiator 85 connected to the water pipe between the second radiator 32 and the hot water supply tank 51 of the second refrigeration cycle circuit 92, and the water Since the radiator 85 can radiate heat from the hot water supply to the atmosphere, the second refrigeration cycle circuit 92 can supercool the first refrigeration cycle circuit 91 without increasing hot water. Thereby, even if the hot water supply tank 51 is filled with hot water, that is, no hot water supply is required, the first refrigeration cycle has a higher evaporating temperature and higher cooling efficiency than the first refrigeration cycle. Refrigerating capacity and cooling efficiency can be improved by supercooling the refrigeration cycle.
  • the refrigeration unit 10 or 110, the supercooling hot water supply apparatus 30 or 130, the showcase 40, and the hot water storage apparatus 50, which are unitized, are included in the control apparatuses 95 to 95.
  • the configuration and the control operation have been described assuming that each of 98 is built in, the configuration of the control device is not limited to this.
  • an integrated control device that integrates and controls the entire refrigeration apparatus of the present invention is separately provided, and the refrigeration apparatus is controlled only by the integrated control apparatus or in cooperation with the integrated control apparatus and the control apparatuses 95 to 98. It is also possible.
  • the refrigeration apparatus of the present invention can be used as a refrigeration apparatus for freezing and refrigeration of foods in supermarkets, convenience stores, restaurants and the like, and also in other applications that require cooling and hot water supply. is there.

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  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Mechanical Engineering (AREA)
  • Thermal Sciences (AREA)
  • General Engineering & Computer Science (AREA)
  • Heat-Pump Type And Storage Water Heaters (AREA)

Abstract

L'invention concerne un appareil de réfrigération dans lequel de l'eau chaude peut être alimentée en utilisant efficacement la chaleur perdue produite lorsqu'un aliment ou similaire est refroidi, ce qui permet d'améliorer la capacité de refroidissement et l'efficacité du refroidissement. Un dispositif de surfusion (5) pour la surfusion du réfrigérant introduit depuis le récepteur intermédiaire (14) dans le deuxième décompresseur (13) est disposé dans un premier circuit de cycle de réfrigération (91) muni d'un premier décompresseur (3), d'un récepteur de pression intermédiaire (14) et d'un deuxième décompresseur (13). Du réfrigérant à l'intérieur du récepteur de pression intermédiaire (14) est introduit dans un premier compresseur (1) au cours d'un processus de compression. Le réfrigérant dans le premier circuit de cycle de réfrigération (91) est surfondu par l'évaporation du réfrigérant dans un deuxième circuit de cycle de réfrigération (92) dans le dispositif de surfusion (5), et l'eau devant être alimentée est chauffée par une action de libération de chaleur du réfrigérant dans un deuxième dispositif de libération de chaleur (32) du deuxième circuit de cycle de réfrigération (92). Le réfrigérant dans le premier circuit de cycle de réfrigération (91) est surfondu par le deuxième circuit de cycle de réfrigération (92), et en conséquence, la capacité de refroidissement et l'efficacité du refroidissement du premier cycle de réfrigération peuvent être améliorées, et de l'eau chaude peut être alimentée en utilisant efficacement la chaleur perdue produite lorsque le réfrigérant est surfondu.
PCT/JP2011/064384 2010-06-28 2011-06-23 Appareil de réfrigération WO2012002248A1 (fr)

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JP2010146124 2010-06-28

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Publication number Priority date Publication date Assignee Title
WO2014030237A1 (fr) * 2012-08-23 2014-02-27 三菱電機株式会社 Dispositif de réfrigération
WO2015141633A1 (fr) * 2014-03-19 2015-09-24 サンデンホールディングス株式会社 Dispositif de réfrigération
JP2016033432A (ja) * 2014-07-31 2016-03-10 パナソニックＩｐマネジメント株式会社 冷凍システム
WO2020071300A1 (fr) * 2018-10-02 2020-04-09 ダイキン工業株式会社 Dispositif à cycle frigorifique

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JPH06201204A (ja) * 1993-01-06 1994-07-19 Tabai Espec Corp 非共沸混合冷媒使用の二段凝縮式冷凍装置
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JP5818996B2 (ja) * 2012-08-23 2015-11-18 三菱電機株式会社 冷凍装置
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WO2020071300A1 (fr) * 2018-10-02 2020-04-09 ダイキン工業株式会社 Dispositif à cycle frigorifique
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