Defrost system for refrigeration apparatus, and cooling unit

Abstract

A defrost system is disclosed that includes a cooling device disposed in a freezer, a heat exchanger pipe leading into a casing, a drain receiver unit; a refrigerating device for cooling and liquefying CO.sub.2 refrigerant; a refrigerant circuit for permitting the CO.sub.2 refrigerant to circulate to the heat exchanger pipe; a defrost circuit branched from the heat exchanger pipe forming a CO.sub.2 circulation path with the heat exchanger pipe; an on-off valve so that the CO.sub.2 circulation path becomes a closed circuit; a pressure adjusting unit for adjusting the pressure of the CO.sub.2 refrigerant; and a first heat exchanger unit for heating the CO.sub.2 refrigerant circulating with brine, disposed below the cooling device to which the defrost circuit and a first brine circuit in which brine, a first heating medium, circulates, are led, in which the CO.sub.2 refrigerant naturally circulates in the closed circuit when defrosting by a thermosiphon effect.

Claims

1. A defrost system for a refrigeration apparatus including: a cooling device which is disposed in a freezer, and includes a casing, a heat exchanger pipe led into the casing, and a drain receiver unit disposed below the heat exchanger pipe; a refrigerating device configured to cool and liquefy CO.sub.2 refrigerant; and a refrigerant circuit connected to the heat exchanger pipe, for permitting the CO.sub.2 refrigerant cooled and liquefied by the refrigerating device to circulate to the heat exchanger pipe, the defrost system comprising: a defrost circuit which is branched from an inlet path and an outlet path of the heat exchanger pipe and forms a CO.sub.2 circulation path together with the heat exchanger pipe; an on-off valve disposed in each of the inlet path and the outlet path of the heat exchanger pipe and configured to be closed at a time of defrosting so that the CO.sub.2 circulation path becomes a closed circuit; a pressure adjusting valve configured to adjust a pressure of the CO.sub.2 refrigerant circulating in the closed circuit at the time of defrosting; and a first heat exchanger configured to heat the CO.sub.2 refrigerant circulating in the defrost circuit with brine, disposed below the cooling device and to which the defrost circuit and a first brine circuit, in which the brine as a first heating medium circulates, are led, wherein the CO.sub.2 refrigerant is permitted to naturally circulate in the closed circuit at the time of defrosting by a thermosiphon effect, wherein the defrost system further comprises a second heat exchanger configured to heat the brine with a second heating medium, wherein the first brine circuit is disposed between the first heat exchanger and the second heat exchanger, and wherein the first brine circuit includes a second brine circuit led to the drain receiver unit.

2. A defrost system for a refrigeration apparatus including: a cooling device which is disposed in a freezer, and includes a casing, a heat exchanger pipe led into the casing, and a drain receiver unit disposed below the heat exchanger pipe; a refrigerating device configured to cool and liquefy CO.sub.2 refrigerant; and a refrigerant circuit connected to the heat exchanger pipe, for permitting the CO.sub.2 refrigerant cooled and liquefied by the refrigerating device to circulate to the heat exchanger pipe, the defrost system comprising: a defrost circuit which is branched from an inlet path and an outlet path of the heat exchanger pipe and forms a CO.sub.2 circulation path together with the heat exchanger pipe; an on-off valve disposed in each of the inlet path and the outlet path of the heat exchanger pipe and configured to be closed at a time of defrosting so that the CO.sub.2 circulation path becomes a closed circuit; a pressure adjusting valve configured to adjust a pressure of the CO.sub.2 refrigerant circulating in the closed circuit at the time of defrosting; and a first heat exchanger configured to heat the CO.sub.2 refrigerant circulating in the defrost circuit with brine, disposed below the cooling device and to which the defrost circuit and a first brine circuit, in which the brine as a first heating medium circulates, are led, wherein the CO.sub.2 refrigerant is permitted to naturally circulate in the closed circuit at the time of defrosting by a thermosiphon effect, wherein the defrost system further comprises a second heat exchanger configured to heat the brine with a second heating medium, wherein the first brine circuit is disposed between the first heat exchanger and the second heat exchanger, wherein the defrost circuit and the first brine circuit are led to the drain receiver unit, wherein the first heat exchanger includes the defrost circuit led to the drain receiver unit and the first brine circuit led to the drain receiver unit, and wherein the defrost system is configured to heat the drain receiver unit and the CO.sub.2 refrigerant in the defrost circuit with the brine circulating in the first brine circuit.

3. A defrost system for a refrigeration apparatus including: a cooling device which is disposed in a freezer, and includes a casing, a heat exchanger pipe led into the casing, and a drain receiver unit disposed below the heat exchanger pipe; a refrigerating device configured to cool and liquefy CO2 refrigerant; and a refrigerant circuit connected to the heat exchanger pipe, for permitting the CO2 refrigerant cooled and liquefied by the refrigerating device to circulate to the heat exchanger pipe, the defrost system comprising: a defrost circuit which is branched from an inlet path and an outlet path of the heat exchanger pipe and forms a CO2 circulation path together with the heat exchanger pipe; an on-off valve disposed in each of the inlet path and the outlet path of the heat exchanger pipe and configured to be closed at a time of defrosting so that the CO2 circulation path becomes a closed circuit; a pressure adjusting valve configured to adjust a pressure of the CO2 refrigerant circulating in the closed circuit at the time of defrosting; and a first heat exchanger configured to heat the CO2 refrigerant circulating in the defrost circuit with brine, disposed below the cooling device and to which the defrost circuit and a first brine circuit, in which the brine as a first heating medium circulates, are led, wherein the CO2 refrigerant is permitted to naturally circulate in the closed circuit at the time of defrosting by a thermosiphon effect, and wherein the defrost system further includes a second brine circuit branched from the first brine circuit and led into the cooling device, configured to heat the CO.sub.2 refrigerant circulating in the heat exchanger pipe with the brine.

4. The defrost system for the refrigeration apparatus according to claim 1, further comprising a first temperature sensor and a second temperature sensor which are respectively disposed at an inlet and an outlet of the first brine circuit, for detecting a temperature of the brine flowing through the inlet and the outlet.

5. The defrost system for the refrigeration apparatus according to claim 1, wherein the refrigerating device includes: a primary refrigerant circuit in which NH.sub.3 refrigerant circulates and a refrigerating cycle component is disposed; a secondary refrigerant circuit in which the CO.sub.2 refrigerant circulates, the secondary refrigerant circuit led to the cooling device, the secondary refrigerant circuit being connected to the primary refrigerant circuit through a cascade condenser; and a liquid CO.sub.2 receiver configured to store the CO.sub.2 refrigerant liquefied in the cascade condenser and a liquid CO.sub.2 pump for sending the CO.sub.2 refrigerant stored in the liquid CO.sub.2 receiver to the cooling device, which are disposed in the secondary refrigerant circuit.

6. The defrost system for the refrigeration apparatus according to claim 1, wherein the refrigerating device is a NH.sub.3/CO.sub.2 cascade refrigerating device including: a primary refrigerant circuit in which NH.sub.3 refrigerant circulates and a first refrigerating cycle component is disposed; and a secondary refrigerant circuit in which the CO.sub.2 refrigerant circulates and a second refrigerating cycle component is disposed, the secondary refrigerant circuit led to the cooling device, the secondary refrigerant circuit being connected to the primary refrigerant circuit through a cascade condenser.

7. A defrost system for a refrigeration apparatus including: a cooling device which is disposed in a freezer, and includes a casing, a heat exchanger pipe led into the casing, and a drain receiver unit disposed below the heat exchanger pipe; a refrigerating device configured to cool and liquefy CO.sub.2 refrigerant; and a refrigerant circuit connected to the heat exchanger pipe, for permitting the CO.sub.2 refrigerant cooled and liquefied by the refrigerating device to circulate to the heat exchanger pipe, the defrost system comprising: a defrost circuit which is branched from an inlet path and an outlet path of the heat exchanger pipe and forms a CO.sub.2 circulation path together with the heat exchanger pipe; an on-off valve disposed in each of the inlet path and the outlet path of the heat exchanger pipe and configured to be closed at a time of defrosting so that the CO.sub.2 circulation path becomes a closed circuit; a pressure adjusting valve configured to adjust a pressure of the CO.sub.2 refrigerant circulating in the closed circuit at the time of defrosting; a first heat exchanger configured to heat the CO.sub.2 refrigerant circulating in the defrost circuit with brine, disposed below the cooling device and to which the defrost circuit and a first brine circuit, in which the brine as a first heating medium circulates, are led; and a second heat exchanger configured to heat the brine with a second heating medium, wherein the CO.sub.2 refrigerant is permitted to naturally circulate in the closed circuit at the time of defrosting by a thermosiphon effect, wherein the first brine circuit is disposed between the first heat exchanger and the second heat exchanger, wherein the refrigerating device includes: a primary refrigerant circuit in which NH.sub.3 refrigerant circulates and a refrigerating cycle component is disposed; a secondary refrigerant circuit in which the CO.sub.2 refrigerant circulates, the secondary refrigerant circuit led to the cooling device, the secondary refrigerant circuit being connected to the primary refrigerant circuit through a cascade condenser; and a liquid CO.sub.2 receiver configured to store the CO.sub.2 refrigerant liquefied in the cascade condenser and a liquid CO.sub.2 pump for sending the CO.sub.2 refrigerant stored in the liquid CO.sub.2 receiver to the cooling device, which are disposed in the secondary refrigerant circuit, wherein the defrost system further includes a cooling water circuit led to a condenser as a part of the refrigerating cycle component disposed in the primary refrigerant circuit, and wherein the cooling water circuit and the first brine circuit are led to the second heat exchanger for heating the brine circulating in the first brine circuit with cooling water circulating in the cooling water circuit and having been heated in the condenser.

8. A defrost system for a refrigeration apparatus including: a cooling device which is disposed in a freezer, and includes a casing, a heat exchanger pipe led into the casing, and a drain receiver unit disposed below the heat exchanger pipe; a refrigerating device configured to cool and liquefy CO.sub.2 refrigerant; and a refrigerant circuit connected to the heat exchanger pipe, for permitting the CO.sub.2 refrigerant cooled and liquefied by the refrigerating device to circulate to the heat exchanger pipe, the defrost system comprising: a defrost circuit which is branched from an inlet path and an outlet path of the heat exchanger pipe and forms a CO.sub.2 circulation path together with the heat exchanger pipe; an on-off valve disposed in each of the inlet path and the outlet path of the heat exchanger pipe and configured to be closed at a time of defrosting so that the CO.sub.2 circulation path becomes a closed circuit; a pressure adjusting valve configured to adjust a pressure of the CO.sub.2 refrigerant circulating in the closed circuit at the time of defrosting; a first heat exchanger configured to heat the CO.sub.2 refrigerant circulating in the defrost circuit with brine, disposed below the cooling device and to which the defrost circuit and a first brine circuit, in which the brine as a first heating medium circulates, are led; and a second heat exchanger configured to heat the brine with a second heating medium, wherein the CO.sub.2 refrigerant is permitted to naturally circulate in the closed circuit at the time of defrosting by a thermosiphon effect, wherein the first brine circuit is disposed between the first heat exchanger and the second heat exchanger, wherein the refrigerating device includes: a primary refrigerant circuit in which NH.sub.3 refrigerant circulates and a refrigerating cycle component is disposed; a secondary refrigerant circuit in which the CO.sub.2 refrigerant circulates, the secondary refrigerant circuit led to the cooling device, the secondary refrigerant circuit being connected to the primary refrigerant circuit through a cascade condenser; and a liquid CO.sub.2 receiver configured to store the CO.sub.2 refrigerant liquefied in the cascade condenser and a liquid CO.sub.2 pump for sending the CO.sub.2 refrigerant stored in the liquid CO.sub.2 receiver to the cooling device, which are disposed in the secondary refrigerant circuit, wherein the defrost system further includes a cooling water circuit led to a condenser as a part of the refrigerating cycle component disposed in the primary refrigerant circuit, and wherein the second heat exchanger includes: a cooling tower for cooling cooling water circulating in the cooling water circuit with spray water; and a heating tower for receiving the spray water and heating the brine circulating in the first brine circuit with the spray water.

9. The defrost system for the refrigeration apparatus according to claim 1, wherein the pressure adjusting valve is disposed in the outlet path of the heat exchanger pipe.

10. The defrost system for the refrigeration apparatus according to claim 1, wherein the drain receiver unit further includes an auxiliary heating electric heater.

11. A cooling unit comprising: a cooling device which includes: a casing; a heat exchanger pipe led into the casing; and a drain pan disposed below the heat exchanger pipe; a defrost circuit which is branched from an inlet path and an outlet path of the heat exchanger pipe and forms a CO.sub.2 circulation path together with the heat exchanger pipe; an on-off valve disposed in each of the inlet path and the outlet path of the heat exchanger pipe and configured to be closed at a time of defrosting so that the CO.sub.2 circulation path becomes a closed circuit; a pressure adjusting valve configured to adjust pressure of the CO.sub.2 refrigerant circulating in the closed circuit at the time of defrosting; a heat exchanger that includes the defrost circuit led to the drain pan and a first brine circuit led to the drain pan, and configured to heat the drain receiver unit with the brine circulating in the first brine circuit; and a second brine circuit branched from the first brine circuit and led into the cooling device, for heating the CO2 refrigerant circulating in the heat exchanger pipe with the brine.

Description

BRIEF DESCRIPTION OF DRAWINGS

(1) FIG. 1 is a general configuration diagram of a refrigeration apparatus according to one embodiment.

(2) FIG. 2 is a general configuration diagram of a refrigeration apparatus according to one embodiment.

(3) FIG. 3 is a general configuration diagram of a refrigeration apparatus according to one embodiment.

(4) FIG. 4 is a sectional view of a cooling device in the refrigeration apparatus shown in FIG. 3.

(5) FIG. 5 is a sectional view of the cooling device according to one embodiment.

(6) FIG. 6 is a general configuration diagram of a refrigeration apparatus according to one embodiment.

(7) FIG. 7 is a system diagram of a refrigerating device according to one embodiment.

(8) FIG. 8 is a system diagram of a refrigerating device according to one embodiment.

(9) FIG. 9 is a general configuration diagram of a refrigeration apparatus according to one embodiment.

(10) FIG. 10 is a general configuration diagram of a refrigeration apparatus according to one embodiment.

(11) FIG. 11 is a sectional view of a cooling device according to one embodiment.

DETAILED DESCRIPTION

(12) Some embodiments of the present invention will now be described in detail with reference to the accompanying drawings. It is intended, however, that dimensions, materials, shapes, relative positions, and the like of components described in the embodiments shall be interpreted as illustrative only and not limitative of the scope of the present invention.

(13) For example, expressions indicating a relative or absolute arrangement such as in a certain direction, along a certain direction, parallel to, orthogonal to, center of, concentric to, and coaxially do not only strictly indicate such arrangements but also indicate a state including a tolerance or a relative displacement within an angle and a distance achieving the same function.

(14) For example, expressions such as the same, equal to, and equivalent to indicating a state where the objects are the same, do not only strictly indicate the same state, but also indicate a state including a tolerance or a difference achieving the same function.

(15) For example, expressions indicating shapes such as rectangular and cylindrical do not only indicate the shapes such as rectangular and cylindrical in a geometrically strict sense, but also indicate shapes including recesses/protrusions, chamfered portions, and the like, as long as the same effect can be obtained.

(16) Expressions such as comprising, including, includes, provided with, or having a certain component are not exclusive expressions that exclude other components.

(17) FIG. 1 to FIG. 11 show refrigeration apparatuses 10A to 10F including defrost systems according to some embodiments of the present invention.

(18) The refrigeration apparatuses 10A to 10F each include: cooling devices 33a and 33b respectively disposed in freezers 30a and 30b; a refrigerating device 11A or 11D for cooling and liquefying CO.sub.2 refrigerant; and a refrigerant circuit (corresponding to a secondary refrigerant circuit 14) which permits the CO.sub.2 refrigerant cooled and liquefied by the refrigerating device to circulate to the cooling devices 33a and 33b. The cooling devices 33a and 33b respectively include: casings 34a and 34b; heat exchanger pipes 42a and 42b disposed in the casings; and drain pans 50a and 50b disposed below the heat exchanger pipes 42a and 42b.

(19) The refrigerating device 11A shown in FIG. 1 to FIG. 3, FIG. 6, and FIG. 10 and the refrigerating device 11D shown in FIG. 9 include: a primary refrigerant circuit 12 in which NH.sub.3 refrigerant circulates and a refrigerating cycle component is disposed; and a secondary refrigerant circuit 14 in which the CO.sub.2 refrigerant circulates, the secondary refrigerant circuit extending to the cooling devices 33a and 33. The secondary refrigerant circuit 14 is connected to the primary refrigerant circuit 12 through a cascade condenser 24.

(20) The refrigerating cycle component disposed in the primary refrigerant circuit 12 includes a compressor 16, a condenser 18, a liquid NH.sub.3 receiver 20, an expansion valve 22, and the cascade condenser 24.

(21) The secondary refrigerant circuit 14 includes a liquid CO.sub.2 receiver 36 which stores the liquid CO.sub.2 refrigerant liquefied in the cascade condenser 24 and a liquid CO.sub.2 pump 38 for permitting the liquid CO.sub.2 refrigerant stored in the liquid CO.sub.2 receiver 36 to circulate to the heat exchanger pipes 42a and 42b.

(22) A CO.sub.2 circulation path 44 is disposed between the cascade condenser 24 and the liquid CO.sub.2 receiver 36. CO.sub.2 refrigerant gas introduced from the liquid CO.sub.2 receiver 36 to the cascade condenser 24 through the CO.sub.2 circulation path 44 is cooled and liquefied with the NH.sub.3 refrigerant in the cascade condenser 24, and then returns to the liquid CO.sub.2 receiver 36.

(23) The refrigerating devices 11A and 11D use natural refrigerants of NH.sub.3 and CO.sub.2 and thus facilitate an attempt to prevent the ozone layer depletion, global warming, and the like. Furthermore, the refrigerating devices 11A and 11D use NH.sub.3, with high cooling performance and toxicity, as a primary refrigerant and use CO.sub.2, with no toxicity or smell, as a secondary refrigerant, and thus can be used for room air conditioning and for refrigerating food products.

(24) In the refrigeration apparatuses 10A to 10F, the secondary refrigerant circuit 14 is branched to CO.sub.2 branch circuits 40a and 40b outside the freezers 30a and 30b. The CO.sub.2 branch circuits 40a and 40b are connected to an inlet tube 42c and an outlet tube 42d of the heat exchanger pipes 42a and 42b led to the outside of the casings 34a and 34b, respectively.

(25) The inlet tube 42c and the outlet tube 42d described above are areas of the heat exchanger pipes 42a and 42b outside the casings 34a and 34b and in the freezers 30a and 30b (refer to FIG. 4 and FIG. 11).

(26) In the freezers 30a and 30b, solenoid on-off valves 54a and 54b are disposed in the inlet tube 42c and the outlet tube 42d. Defrost circuits 52a and 52b are connected to the inlet tube 42c and the outlet tube 42d between the solenoid on-off valves 54a and 54b and the cooling devices 33a and 33b.

(27) The defrost circuits 52a and 52b form a CO.sub.2 circulation path together with the heat exchanger pipes 42a and 42b. The CO.sub.2 circulation path becomes a closed circuit when the solenoid on-off valves 54a and 54b close at the time of defrosting.

(28) Solenoid on-off valves 55a and 55b are disposed in the defrost circuits 52a and 52b. At the time of a refrigerating operation, the solenoid on-off valves 54a and 54b are opened and the solenoid on-off valves 55a and 55b are closed. At the time of defrosting, the solenoid on-off valves 54a and 54b are closed and the solenoid on-off valves 55a and 55b are opened.

(29) In the refrigeration apparatuses 10A to 10E, pressure adjusting units 45a and 45b are disposed in the outlet tube 42d of the heat exchanger pipes 42a and 42b. The pressure adjusting units 45a and 45b respectively include: pressure adjustment valves 48a and 48b disposed in parallel with the solenoid on-off valves 54a and 54b disposed in the outlet tube 42d; pressure sensors 46a and 46b disposed in the outlet tube 42d on the upstream side of the pressure adjustment valves 48a and 48b and detecting pressure of the CO.sub.2 refrigerant; and control devices 47a and 47b to which detected values of the pressure sensors 46a and 46b are input. The control devices 47a and 47b control valve apertures of the pressure adjustment valves 48a and 48b at the time of defrosting based on the detected values from the pressure sensors 46a and 46b. Thus, the pressure of the CO.sub.2 refrigerant is controlled in such a manner that condensing temperature of the CO.sub.2 refrigerant circulating in the closed circuit becomes higher than a freezing point (for example, 0 C.) of water vapor in the air in the freezer.

(30) In the refrigeration apparatus 10F shown in FIG. 10, a pressure adjusting unit 67 is disposed instead of the pressure adjusting units 45a and 45b. The pressure adjusting unit 67 includes: a three way valve 67a dispose on the downstream side of a temperature sensor 68 in a brine circuit (send path) 60; a bypass path 67b connected to the three way valve 67a and the brine circuit (return path) 60 on the upstream side of a temperature sensor 66; and a control device 67c to which a temperature of brine detected by the temperature sensor 66 is input, the control device 67c controlling the three way valve 67a in such a manner that the input value becomes equal to a set temperature. The control device 67c controls the three way valve 67a in such a manner that a temperature of the brine supplied to brine branch paths 61a and 61b is adjusted to be at a set value (for example, 10 to 15 C.).

(31) The brine circuit 60 (the first brine circuit shown with a dashed line) in which the brine as a first heating medium circulates is disposed. The brine circuit 60 is branched to the brine branch circuits 61a and 61b (shown with a dashed line) outside the freezers 30a and 30b.

(32) In the embodiments shown in FIG. 1, FIG. 6, and the like, the brine branch circuits 61a and 61b are led into the freezers 30a and 30b and are disposed on back surfaces of the drain pans 50a and 50b.

(33) In the embodiments shown in FIG. 2, FIG. 3, and FIG. 9, the brine branch circuits 61a and 61b are connected to brine branch circuits 63a and 63b (shown with a dashed line) through a contact part 62 outside the freezers 30a and 30b. The brine branch circuits 63a and 63b are led to the back surfaces of the drain pans 50a and 50b.

(34) In this configuration, sensible heat of the brine circulating in the brine branch circuits 61a and 61b or 63a and 63b can prevent drainage that has dropped onto the brine branch circuits 61a, 61b or 63a, from refreezing at the time of defrosting.

(35) In the embodiments shown in FIG. 1 and FIG. 6, heat exchangers 70a and 70b are disposed below the heat exchanger pipes 42a and 42b in the freezers 30a and 30b. The defrost circuits 52a and 52b are led to the heat exchangers 70a and 70b.

(36) The brine circuit 60 is branched to brine branch circuits 72a and 72b outside the freezers 30a and 30b. The brine branch circuits 72a and 72b are respectively led to the heat exchangers 70a and 70b.

(37) In the embodiments shown in FIG. 2, FIG. 3, FIG. 9, and the like, the brine branch circuits 63a, 63b and the defrost circuits 52a and 52b are led to the back surfaces of the drain pans 50a and 50b instead of providing the heat exchangers 70a and 70b. A heat exchanger unit (first heat exchanger unit) is formed in which the brine circulating in the brine branch circuits 63a and 63b heats the CO.sub.2 refrigerant circulating in the defrost circuits 52a and 52b.

(38) The brine circulating in the brine branch circuits 63a and 63b can heat the drain pans 50a and 50b.

(39) In the embodiments described above, the brine circulating in the brine circuit 60 can be heated with another heating medium.

(40) In some embodiments shown in FIG. 1 to FIG. 3, FIG. 6, and the like, a cooling water circuit 28 is led to the condenser 18. A cooling water branch circuit 56 including a cooling water pump 57 is branched from the cooling water circuit 28, and is connected to a heat exchanger unit 58 (second heat exchanger unit). The brine circuit 60 is also connected to the heat exchanger unit 58.

(41) Cooling water circulating in the cooling water circuit 28 is heated with the NH.sub.3 refrigerant in the condenser 18. The heated cooling water (second heating medium) heats the brine circulating in the brine circuit 60 as the heating medium at the time of defrosting, in the heat exchanger unit 58.

(42) For example, when a temperature of the cooling water introduced to the cooling water branch circuit 56 is 20 to 30 C., the brine can be heated up to 15 to 20 C. with the cooling water.

(43) An aqueous solution such as ethylene glycol or propylene glycol can be used as the brine for example.

(44) In other embodiments, for example, any heating medium other than the cooling water can be used as the second heating medium. Such a heating medium includes NH.sub.3 refrigerant gas with high temperature and high pressure discharged from the compressor 16, warm discharge water from a factory, a medium that has absorbed heat emitted from a boiler or potential heat of an oil cooler, and the like.

(45) In the exemplary configurations in some embodiments shown in FIG. 1 to FIG. 3, FIG. 6, and the like, the cooling water circuit 28 is disposed between the condenser 18 and a closed-type cooling tower 26. A cooling water pump 29 makes the cooling water circulate in the cooling water circuit 28. The cooling water that has absorbed exhaust heat from the NH.sub.3 refrigerant in the condenser 18 comes into contact with the outer air and spray water in the closed-type cooling tower 26 and is cooled with vaporization latent heat of the spray water.

(46) The closed-type cooling tower 26 includes: a cooling coil 26a connected to the cooling water circuit 28; a fan 26b that blows outer air a into the cooling coil 26a; and a spray pipe 26c and a pump 26d for spraying the cooling water onto the cooling coil 26a. The cooling water sprayed from the spray pipe 26c partially vaporizes. The cooling water flowing in the cooling coil 26c is cooled with the vaporization latent heat thus produced.

(47) In the embodiment shown in FIG. 9, a closed-type cooling and heating unit 90 integrating the closed-type cooling tower 26 and a closed-type heating tower 91 is provided. A configuration of the closed-type cooling tower 26 in the present embodiment is basically the same as that of the closed-type cooling tower 26 in the embodiments described above.

(48) The brine circuit 60 is connected to the closed-type heating tower 91. The closed-type heating tower 91 includes: a heating coil 91a connected to the brine circuit 60; and a spray pipe 91c and a pump 91d for spraying the cooling water onto the cooling coil 91a. An inside of the closed-type cooling tower 26 communicates with an inside of the closed-type heating tower 91 through a lower portion of a common housing.

(49) The cooling water that has absorbed the exhaust heat from the NH.sub.3 refrigerant circulating in the primary refrigerant circuit 12 is sprayed onto the cooling coil 91a from the spray pipe 91c, and is used as a heating medium which heats the brine circulating in the brine circuit 60.

(50) In the embodiments shown in FIG. 3 and FIG. 6, brine branch circuits 74a and 74b are branched from the brine circuit 60 outside the freezers 30a and 30b.

(51) In the embodiment shown in FIG. 3, the brine branch circuits 74a and 74b are connected to brine branch circuits 78a and 78b (the second brine circuit shown with a dashed line) through a contact part 76 outside the freezers 30a and 30b. The brine branch circuits 78a and 78b are led into the cooling devices 33a and 33b, disposed adjacent to the heat exchanger pipes 42a and 42b, and form a heat exchanger unit which heats the CO.sub.2 refrigerant circulating in the heat exchanger pipes 42a and 42b with the brine circulating in the brine branch circuits 78a and 78b.

(52) In the embodiment shown in FIG. 6, the brine branch circuits 74a and 74b are led into the cooling devices 33a and 33b, and form a heat exchanger unit having a configuration similar to that of the heat exchanger unit described above.

(53) In some embodiments shown in FIG. 1 to FIG. 3, FIG. 6, and the like, a receiver (open brine tank) 64 that stores the brine, a brine pump 65 that makes the brine circulate, and the temperature sensor 66 that detects a temperature of the CO.sub.2 refrigerant are disposed in the send path of the brine circuit 60. The temperature sensor 68 that detects the temperature of the temperature sensor 68 is disposed in the return path of the brine circuit 60.

(54) In the embodiment shown in FIG. 9, an expansion tank 92 for offsetting pressure change and adjusting a flowrate of the brine is disposed instead of the receiver 64.

(55) FIG. 7 shows a refrigerating device 11B that can be applied to the present invention and has a configuration different from those of the refrigerating devices 11A and 11D.

(56) In the refrigerating device 11B, a lower stage compressor 16b and a higher stage compressor 16a are disposed in the primary refrigerant circuit 12 in which the NH.sub.3 refrigerant circulates. An intermediate cooling device 84 is disposed in the primary refrigerant circuit 12 and between the lower stage compressor 16b and the higher stage compressor 16a. A branch path 12a is branched from the primary refrigerant circuit 12 at an outlet of the condenser 18, and an intermediate expansion valve 86 is disposed in the branch path 12a. The NH.sub.3 refrigerant flowing in the branch path 12a is expanded and cooled in the intermediate expansion valve 86, and is then introduced into the intermediate cooling device 84. In the intermediate cooling device 84, the NH.sub.3 refrigerant discharged from the lower stage compressor 16b is cooled with the NH.sub.3 refrigerant introduced from the branch path 12a.

(57) The intermediate cooling device 84 can improve the COP of the refrigerating device 11B.

(58) The liquid CO.sub.2 refrigerant, cooled and liquefied by exchanging heat with the NH.sub.3 refrigerant in the cascade condenser 24, is stored in the liquid CO.sub.2 receiver 36. Then, the liquid CO.sub.2 pump 38 makes the liquid CO.sub.2 refrigerant circulate in the cooling device 33 disposed in the freezer 30, from the liquid CO.sub.2 receiver 36.

(59) FIG. 8 shows a refrigerating device 11C that can be applied to the present invention and has still another configuration.

(60) The refrigerating device 11C forms a cascade refrigerating cycle. A higher temperature compressor 88a and an expansion valve 22a are disposed in the primary refrigerant circuit 12. A lower temperature compressor 88b and an expansion valve 22b are disposed in the secondary refrigerant circuit 14 connected to the primary refrigerant circuit 12 through the cascade condenser 24.

(61) The refrigerating device 11C is a cascade refrigerating device in which a mechanical compression refrigerating cycle is formed in each of the primary refrigerant circuit 12 and the secondary refrigerant circuit 14, whereby the COP of the refrigerating device can be improved.

(62) In the embodiments shown in FIG. 2, FIG. 3, and FIG. 9, the CO.sub.2 branch circuits 40a and 40b are respectively connected to the inlet tube 42c and the outlet tube 42d of the heat exchanger pipes 42a and 42b through a contact part 41, outside the freezers 30a and 30b.

(63) The cooling device 33a shown in FIG. 4 is used for the refrigeration apparatus 10C shown in FIG. 3. The heat exchanger pipe 42a and the brine branch circuit 78a, led into the freezer 30a, are formed to have winding shapes in an upper and lower direction and a horizontal direction in the cooling device 33a.

(64) The defrost circuit 52a and the brine branch circuit 63a disposed on the back surface of the drain pan 50a are formed to have winding shapes in the upper and lower direction and the horizontal direction. The cooling device 33b in FIG. 3 has a configuration that is similar to that of the cooling device 33a in FIG. 3.

(65) In an exemplary configuration of the cooling device 33a shown in FIG. 11, an auxiliary heating electric heater 94a is disposed on the back surface of the drain pan 50a. Thus, when the amount of sensible heat of the brine circulating in the brine branch circuit 63a disposed on the back surface of the drain pan 50a falls short, the shortage amount can be covered.

(66) In exemplary configurations of the cooling device 33a shown in FIG. 4 and FIG. 11, air openings are formed on upper and side surfaces (not shown) of the casing 34a. The freezer inner air c flows in through the side surface and flows out through the upper surface.

(67) In an exemplary configuration of the cooling device 33a shown in FIG. 5, air openings are formed on both side surfaces, whereby the freezer inner air c flows in and out of the casing 34a through both side surfaces.

(68) In the embodiments shown in FIG. 2 and FIG. 9, cooling units 31a and 31b are formed.

(69) The cooling units 31a and 31b respectively include: the casings 34a and 34b forming the cooling devices 33a and 33b; the heat exchanger pipes 42a and 42b led into the casings; the inlet tube 42c; the outlet tube 42d; and the drain pans 50a and 50b disposed below the heat exchanger pipes 42a and 42b.

(70) The heat exchanger pipes 42a and 42b are connected to the CO.sub.2 branch circuits 40a and 40b disposed outside the freezers 30a and 30b through the contact part 41, to be attached to the freezers 30a and 30b.

(71) The cooling units 31a and 31b respectively include: defrost circuits 52a and 52b branched from the inlet tube 42c and the outlet tube 42d outside the casings 34a and 34b; and the solenoid on-off valves 54a and 54b disposed in the inlet tube 42c and the outlet tube 42d. The solenoid on-off valves 54a and 54b can make the heat exchanger pipes 42a and 42b, which are more on the cooling device side than the defrost circuits 52a and 52b and branch portions of the defrost circuits, the closed circuit at the time of defrosting.

(72) The cooling units 31a and 31 respectively include the pressure adjustment valves 48a and 48b disposed in the outlet tube 42d outside the casings 34a and 34b for adjusting pressure in the closed circuit.

(73) The cooling units 31a and 31b respectively include the brine branch circuits 63a and 63b and the defrost circuits 52a and 52b that are led to the drain pans 50a and 50b, and form a heat exchanger unit which heats the CO.sub.2 refrigerant circulating in the defrost circuits 52a and 52b with the brine circulating in the brine branch circuits 63a and 63b.

(74) The brine branch circuits 63a and 63b are connected to the brine branch circuits 61a and 61b disposed outside the freezers 30a and 30b through the contact part 62 to be attached to the freezers 30a and 30b.

(75) The components of the cooling units 31a and 31b may be integrally formed in advance.

(76) In the embodiment shown in FIG. 3, cooling units 32a and 32b are formed. The cooling units 32a and 32b are obtained by adding the brine branch circuits 78a and 78b branched from the brine circuit 60 and led into the cooling devices 33a and 33b to the cooling units 31a and 31b.

(77) The brine branch circuits 78a and 78b are connected to the brine branch circuits 74a and 74b disposed outside the freezers 30a and 30b through the contact part 76 to be attached to the freezers 30a and 30b.

(78) The components of the freezers 30a and 30b may be integrally formed in advance.

(79) In an exemplary embodiment shown in FIG. 11, a cooling unit 93a is formed. The cooling unit 93a is obtained by adding the auxiliary heating electric heater 94a disposed on the back surfaces of the drain pans 50a and 50b to the cooling units 32a and 32b.

(80) The components of the cooling unit 93a can be integrally formed in advance.

(81) In the exemplary configuration of the cooling device 33a shown in FIG. 4 and FIG. 11, the drain pans 50a and 50b are inclined from the horizontal direction so that the drainage is discharged, and are respectively provided with drain outlet tubes 51a and 51b at the lower ends. Returning paths of the defrost circuits 52a and 52b are inclined along the back surfaces of the drain pans 50a and 50b in such a manner that a portion more on the downstream side is positioned higher.

(82) The exemplary configurations of the cooling devices 33a and 33b are described. For example, in the cooling device 33a shown in FIG. 4 and FIG. 11, the heat exchanger pipe 42a includes headers 43a and 43b at the inlet tube 42c and the outlet tube 42d of the cooling device 33a, and is formed to have a winding shape in the upper and lower direction and the horizontal direction in the cooling device 33a. The defrost circuit 52a is disposed on the back surface of the drain pan 50a.

(83) The brine branch circuit 78a has headers 80a and 80b disposed at an inlet and an outlet of the cooling device 33a. The defrost circuit 52a is disposed on the back surface of the drain pan 50a to be adjacent to the drain pan 50a and the brine branch circuit 63a, and is formed to have a winding shape in the horizontal direction.

(84) A large number of plate fins 82a are disposed in the upper and lower direction in the cooling device 33a. The heat exchanger pipe 42a and the branch circuit 78a are inserted in a large number of holes formed on the plate fins 82a and thus are supported by the plate fins 82a. With the plate fins 82a, supporting strength for the heat exchanger pipe 42a and the brine branch circuit 78 is increased, and the heat transmission between the heat exchanger pipe 42a and the brine branch circuit 78a is facilitated.

(85) The drain pan 50a is inclined from the horizontal direction, and is provided with the drain outlet tube 51a at a lower end. Return paths of the defrost circuit 52a and the brine branch circuit 63a are also inclined along the back surface of the drain pan 50a.

(86) As described above, the return path of the defrost circuit 52a is inclined in such a manner that a portion more on the downstream side is positioned higher. Thus, the CO.sub.2 refrigerant gas heated and vaporized by the brine b circulating in the brine branch circuit 63a can be favorably outgassed in the return path of the defrost circuit 52a. This can prevent a sudden pressure rise due to the vaporization of the CO.sub.2 refrigerant.

(87) In the exemplary configuration of the cooling device 33a shown in FIG. 4 and FIG. 11, the casing 34a is provided with an inlet opening and an outlet opening for air. For example, the inlet opening is formed on a side surface of the casing 34a and the outlet opening is formed on the upper surface of the casing 34a. Fans 35a and 35b are disposed at the outlet opening. When the fans 35a and 35b operate, the freezer inner air c forms an air flow flowing in and out of the casings 34a and 34b.

(88) The cooling device 33b has a configuration that is similar to that of the cooling device 33a.

(89) In the configuration of the present embodiment, the solenoid on-off valves 54a and 54b are opened and the solenoid on-off valves 55a and 55b are closed in the refrigerating operation. Thus, the CO.sub.2 refrigerant supplied from the secondary refrigerant circuit 14 circulates in the CO.sub.2 branch circuits 40a and 40a and the heat exchanger pipes 42a and 42b. The fans 35a and 35b form a circulation flow of the freezer inner air c passing in the cooling devices 33a and 33b inside the freezers 30a and 30b. The freezer inner air c is cooled by the CO.sub.2 refrigerant circulating in the heat exchanger pipes 42a and 42b, whereby the internal temperature of the freezers 30a and 30b is kept as low as 25 C., for example.

(90) The solenoid on-off valves 54a and 54b are closed and the solenoid on-off valves 55a and 55b are opened at the time of defrosting. Thus, the closed CO.sub.2 circulation path including the heat exchanger pipes 42a and 42b and the defrost circuits 52a and 52b is formed. The pressure of the CO.sub.2 refrigerant circulating in the closed circuit is adjusted with the pressure adjusting units 45a and 45b or the pressure adjusting unit 67 in such a manner that the condensing temperature of the CO.sub.2 refrigerant circulating in the heat exchanger pipes 42a and 42b is adjusted to be at, for example, +5 C. (4.0 MPa) that is a temperature higher than the freezing point (for example, 0 C.) of the freezer inner air c.

(91) The pressure adjusting units 45a and 45b may be provided with a temperature sensor that detects a temperature of the CO2 refrigerant instead of the pressure sensors 46a and 46b. Thus, the control devices 47a and 47b may convert the saturation pressure of the CO.sub.2 refrigerant corresponding to the temperature detected value.

(92) At the time of defrosting, frost attached to the surfaces of the heat exchanger pipes 42a and 42b is melted by the condensation latent heat (for example, 219 kJ/kg under +5 C./4.0 MPa when warm brine at +15 C. is used as the heating source) of the CO.sub.2 refrigerant circulating in the heat exchanger pipes 42a and 42b, and drops onto the drain pans 50a and 50b.

(93) The water as a result of the melting that has dropped onto the drain pans 50a and 50b is prevented from refreezing with the sensible heat of the brine circulating in the brine branch circuits 61a and 61b or 63a and 63b led to the drain pans 50a and 50b. Furthermore, heating and defrosting of the drain pans 50a and 50b can be achieved.

(94) The CO.sub.2 refrigerant circulating in the heat exchanger pipes 42a and 42b naturally circulate in the closed circuit by an effect of a looped thermosiphon obtained with, for example, the brine b at +15 C. used as the heating source and the frost attached on the surfaces of the heat exchanger pipes 42a and 42b used as a cooling source.

(95) More specifically, in the embodiments shown in FIG. 1 and FIG. 6, the CO.sub.2 refrigerant is heated by the brine in the heat exchangers 70a and 70b.

(96) In the embodiments shown in FIG. 2, FIG. 3, and FIG. 9, the CO.sub.2 refrigerant is heated and vaporized with the brine in the heat exchanger units formed on the back surfaces of the drain pans 50a and 50b. The CO.sub.2 refrigerant gas vaporized in the heat exchanger units rises in the defrost circuits 52a and 52b to return to the heat exchanger pipes 42a and 42b, and melts the frost attached to the heat exchanger pipes 42a and 42b and is condensed. The condensed liquid CO2 refrigerant falls in the defrost circuits 52a and 52b with gravity, to be heated and vaporized again in the heat exchanger units.

(97) The temperatures of the brine at the inlet and the outlet of the brine circuit 60 are detected by the temperature sensors 66 and 68. It is determined that the defrosting is completed when the difference between the detected values decreases so that the temperature difference reduces to a threshold value (for example, 2 to 3 C.), and thus the defrosting operation is terminated.

(98) In some embodiments of the present invention, condensation latent heat of the CO.sub.2 refrigerant with the condensing temperature exceeding the freezing point of the water vapor in the freezer inner air c is used to heat the frost attached to the heat exchanger pipes 42a and 42b from the inside of the heat exchanger pipes. Thus, a large amount of heat can be transmitted to the frost, and no heating means needs to be disposed outside the heat exchanger pipes 42a and 42b, whereby power saving and cost reduction can be achieved.

(99) The CO.sub.2 refrigerant is permitted to naturally circulate in the closed circuit by the thermosiphon effect. Thus, a power source such as a pump for circulating the CO.sub.2 refrigerant is not required, and thus further power saving can be achieved.

(100) With the condensing temperature of the CO.sub.2 refrigerant at the time of defrosting kept at a temperature closer to the freezing point of the moisture content as much as possible, fogging can be prevented, and the thermal load can be lowered and the water vapor diffusion can be prevented as much as possible. The pressure of the CO.sub.2 refrigerant can be reduced, whereby the pipes and the valves forming the closed circuit may be designed for lower pressure, whereby further cost reduction can be achieved.

(101) The water as a result of the melting that has dropped onto the drain pans 50a and 50b can be prevented from defrosting by the sensible heat of the brine circulating in the brine branch circuits 61a and 61b or 63a and 63b led to the drain pans 50a and 50b. Furthermore, the drain pans 50a and 50b can be heated and defrosted by the sensible heat of the brine. Thus, no heater needs to be additionally provided to the drain pans 50a and 50b, whereby the cost reduction can be achieved.

(102) According to the embodiments shown in FIG. 2, FIG. 3, and FIG. 9, the defrost circuits 52a and 52b and the brine branch circuits 63a and 63b form the heat exchanger units on the back surfaces of the drain pans 50a and 50b. Thus, the heating and defrosting of the drain pans 50a and 50b and the heating of the CO.sub.2 refrigerant circulating in the defrost circuits 52a and 52b can be both achieved at the time of defrosting. Thus, no additional heater needs to be provided, whereby the cost reduction can be achieved.

(103) According to the embodiments shown in FIG. 1 and FIG. 6, when the heat exchangers 70a and 70b are formed of, for example, a plate heat exchanger unit, which has high heat exchange efficiency, the efficiency of the heat exchange between the brine and the CO.sub.2 refrigerant can be improved.

(104) In the refrigeration apparatus 10C shown in FIG. 3 and the refrigeration apparatus 10D shown in FIG. 6, the brine branch circuits 74a and 74b or 78a and 78b are led into the freezers 30a and 30b, and the heat exchanger pipes 42a and 42b are heated from inside and outside. Thus, the heat exchanger pipes 42a and 42 can be effectively heated, and the defrosting time can be shortened.

(105) With the cooling device 33a shown in FIG. 4 and FIG. 11, the heat is transmitted from the brine branch circuit 78a to the heat exchanger pipe 42a through the plate fins 82a, thus, the heat can be transmitted more efficiently. The brine branch circuit 78a and the heat exchanger pipe 42a are supported by the plate fins 82a, whereby the supporting strength for the pipes can be increased.

(106) The difference between the detection values from the temperature sensors 66 and 68 is obtained, and a timing at which the difference between the detection values reduced to the threshold is determined as the timing at which the defrosting operation is completed. Thus, the timing at which the defrosting operation is completed can be accurately determined, whereby the excessive heating and the water vapor diffusion in the freezer can be prevented.

(107) Thus, further power saving can be achieved, and the quality of the food products cooled in the freezers 30a and 30b can be improved with a more stable freezer inner temperature.

(108) In some embodiments, the brine can be heated with the cooling water heated in the condenser 18 of the refrigerating device. Thus, no heating source is required outside the refrigeration apparatus.

(109) The temperature of the cooling water can be reduced with the brine at the time of defrosting. Thus, the COP of the refrigerating device can be improved with the condensing temperature of the NH.sub.3 refrigerant at the time of the refrigerating operation lowered.

(110) Furthermore, in the exemplary configuration where the cooling water circuit 28 is disposed between the condenser 18 and the cooling tower 26, the heat exchanger unit 58 can be disposed in the cooling tower. Thus, the installation space for the device used for the defrosting can be downsized.

(111) With the refrigeration apparatus 10E shown in FIG. 9, in the closed-type cooling and heating unit 90, the brine can be heated with the spray water that has absorbed the sensible heat of the cooling water. Thus, the heat exchanger unit 58 is no longer required, and by integrating the heating tower 91 and the cooling tower 26, the installation space can be downsized.

(112) By using the spray water in the closed-type cooling tower 26 as the heat source for the brine, the heat can also be acquired from the outer air. When the refrigeration apparatus 10E employs an air cooling system, the cooling water can be cooled and the brine can be heated with the outer air as the heat source, with the heating tower alone.

(113) A plurality of the closed-type cooling towers 26, incorporated in the closed-type cooling and heating unit 90, may be laterally coupled in parallel to be installed.

(114) In some embodiments, the pressure adjusting units 45a and 45b adjust pressure of in the closed circuit, whereby the pressure adjusting units can be simplified and can be provided with a low cost.

(115) In the embodiment shown in FIG. 10, the pressure adjusting unit 67 is provided. Thus, the pressure adjusting unit needs not to be provided for each cooling device, and only a single pressure adjusting unit needs to be provided. Thus, the cost reduction can be achieved, and the pressure in the closed circuit can be easily adjusted with the pressure in the closed circuit adjusted from the outside of the freezer.

(116) In the cooling device 33a shown in FIG. 11, the drain pans 50a and 50b are provided with the auxiliary heating electric heater 94a. Thus, the drainage stored in the drain pans 50a and 50b can be prevented from refreezing. Even when the amount of heat of the brine circulating in the brine branch circuits falls short, the auxiliary heating electric heater 94a can add the vaporization heat of the CO.sub.2 refrigerant circulating in the defrost circuits 52a and 52b, when the heat exchanger units formed of the defrost circuits 52a and 52b and the brine branch circuits 61a and 61b or 63a and 63b are formed on the drain pans 50a and 50b.

(117) In the embodiments shown in FIG. 2 and FIG. 9, the cooling units 31a and 31b are formed. Thus, the freezers 30a and 30b with defrosting devices can be easily attached to the freezers 30a and 30b. When the components of the cooling units 31a and 31b are integrally assembled, the freezers 30a and 30b can be more easily attached.

(118) According to the embodiment shown in FIG. 3, the cooling units 32a and 32b are formed. Thus, the heat exchanger pipes 42a and 42b can be heated from both inner and outer sides at the time of defrosting. Thus, the cooling devices with the defrosting devices exerting high heating effect can be attached easily.

(119) When the components of the cooling units 31a and 31b are integrally assembled, the cooling devices can be more easily attached

(120) According to the embodiment shown in FIG. 11, the cooling unit 93a provided with the auxiliary heating electric heater 94a is formed. Thus, the cooling devices with the defrosting devices which can auxiliary heat the CO2 refrigerant circulating in the defrost circuits 52a and 52b led to the drain pans, as well as the drain pans 50a and 50b, can be easily attached.

(121) The configurations of some embodiments are described above. The embodiments can be combined as appropriate in accordance with an object and a purpose of the refrigeration apparatus.

INDUSTRIAL APPLICABILITY

(122) According to the present invention, reduction in initial and running costs required for defrosting a refrigeration apparatus used for forming a freezer and other cooling spaces and power saving can be achieved.

REFERENCE SIGNS LIST

(123) 10A, 10B, 10C, 10D, 10E, 10F refrigeration apparatus 11A, 11B, 11C, 11D refrigerating device 12 primary refrigerant circuit 14 secondary refrigerant circuit 16 compressor 16a higher stage compressor 16b lower stage compressor 18 condenser 20 liquid NH.sub.3 receiver 22, 22a, 22b expansion valve 24 cascade condenser 26 closed-type cooling tower 28 cooling water circuit 29, 57 cooling water pump 30, 30a, 30b freezer 31a, 31b, 32a, 32b, 93a cooling unit 33, 33a, 33b cooling device 34a, 34b casing 35a, 35b fan 36 liquid CO2 receiver 38 liquid CO.sub.2 pump 40a, 40b CO.sub.2 branch circuit 41, 62, 76 contact part 42a, 42b heat exchanger pipe 42a inlet tube 42d outlet tube 43a, 43b, 80a, 80b header 44 CO.sub.2 circulation path 45a, 45b, 67 pressure adjusting unit 46a, 46b pressure sensor 47a, 47b, 67c control device 48a, 48b pressure adjustment valve 50a, 50b drain pan 51a, 51b drain outlet tube 52a, 52b defrost circuit 54a, 54b, 55a, 55b solenoid on-off valve 56 cooling water branch circuit 58 heat exchanger unit (second heat exchanger unit) 60 brine circuit 61a, 61b, 63a, 63b, 72a, 72b, 74a, 74b, 78a, 78b brine branch circuit 64 receiver 65 brine pump 66, 68 temperature sensor 70a, 70b heat exchanger unit (first heat exchanger unit) 82a plate fin 86 intermediate expansion valve 84 intermediate cooling device 88a higher temperature compressor 88b lower temperature compressor 90 closed-type cooling and heating unit 91 closed-type heating tower 92 expansion tank 94a auxiliary heating electric heater a outer air b brine c freezer inner air