JP4794511B2 - Refrigeration cycle equipment - Google Patents

Description

  The present invention relates to a refrigeration cycle apparatus, and more particularly to a technology for improving energy saving in an air conditioning / refrigeration / refrigeration apparatus used in a store such as a supermarket or a convenience store.

  When it is required to cover multiple heat loads with different temperature ranges, such as air conditioning loads and refrigeration loads, such as supermarkets and convenience stores, multiple compressors are installed in one refrigeration cycle, and the same refrigerant is circulated. A refrigeration cycle apparatus that can cover a plurality of heat loads has been proposed (see, for example, Patent Document 1).

  In addition, it is composed of a plurality of independent refrigeration cycles that cover each heat load, and a plurality of independent refrigerants circulating through each refrigeration cycle exchange heat with each other, so that the high-stage refrigeration cycle is the low-stage refrigeration cycle. Proposed a refrigeration cycle system that increases the subcooling degree of the refrigeration cycle on the lower stage, increases the refrigeration capacity, and saves energy for the entire system by arranging the refrigerant / refrigerant heat exchanger to recover the exhaust heat (For example, see Patent Document 2 and Patent Document 3).

JP 2002-357367 A (FIG. 1, paragraphs 0016 to 0039) JP 2003-4321 A (FIGS. 1-4, paragraphs 0016-0031) JP 2004-170001 A (FIG. 1, paragraphs 0043-0056)

  However, in the refrigeration cycle apparatus shown in Patent Document 1, since a plurality of heat loads are configured by one refrigeration cycle, in order to balance the total amount of heat at the time of changes in the surrounding environment such as outside air temperature or air conditioning load, etc. Therefore, frequent mode switching has to be performed, and there is a problem in that useless energy loss occurs with mode switching and energy saving is not achieved.

  In addition, since the same refrigerant is circulated to one heat exchanger on the heat source side, the effect of improving the efficiency only at a specific time when heating is fully operated can be obtained. There was a problem that wasteful loss was large and energy was not saved.

  Further, in the refrigeration cycle apparatuses described in Patent Document 2 and Patent Document 3, since the refrigeration cycle for a plurality of heat loads can be operated independently, there is no problem like the refrigeration cycle apparatus of Patent Document 1, When the heat load of the stage-side refrigeration cycle is small, the high-stage refrigeration cycle needs to be thermo-off or shutdown periodically or irregularly to avoid excessive operation. Since the refrigeration capacity and COP of the refrigeration cycle are reduced to the same level as when operating alone, there is a problem that energy is not saved.

  Further, in the refrigeration cycle apparatuses described in Patent Document 2 and Patent Document 3, when the outside air temperature is high, the temperature of the high-stage refrigerant flowing through the refrigerant-refrigerant heat exchanger increases, Therefore, there is a problem that a large degree of supercooling cannot be applied, the refrigerating capacity and the COP on the refrigerator side are reduced, and energy is not saved.

  The present invention has been made to solve the above-described problems in the prior art, and compared with a conventional refrigeration cycle apparatus that maintains a high refrigeration capacity and a high COP and does not perform heat exchange when a plurality of heat loads are covered. The object is to obtain a refrigeration cycle apparatus that always saves energy.

  In addition, the present invention suppresses development investment for air conditioners and refrigerators in the case of providing multiple heat loads, and maintains a high refrigeration capacity and high COP that can be introduced to existing air conditioners and refrigerators. An object of the present invention is to obtain a refrigeration cycle apparatus that always saves energy compared to a conventional refrigeration cycle apparatus that does not perform heat exchange.

In the refrigeration cycle apparatus of the present invention, the first refrigerant circulates, the first compressor, the four-way valve, the outdoor heat exchanger for air conditioning, the indoor heat exchanger for air conditioning, and the outdoor heat exchanger for air conditioning. A first refrigeration cycle having a plurality of first air-conditioning throttle means disposed between the air-conditioning indoor heat exchanger and the first refrigerant flowing in series; A second refrigeration cycle comprising a second compressor, an article cooling outdoor heat exchanger, an article cooling throttling means, and an article cooling indoor heat exchanger, A refrigerant that circulates, a third compressor, a subcooling outdoor heat exchanger, a first refrigerant refrigerant heat exchanger that exchanges heat between the first refrigerant and the third refrigerant; And a second refrigerant refrigerant heat exchanger for exchanging heat between the second refrigerant and the third refrigerant. And the refrigeration cycle,
One end is connected to a flow path between the first air conditioning throttle means provided in the first refrigeration cycle, and the other end is connected to the first air conditioning throttle means and the outdoor air exchange for air conditioning. And a bypass circuit having a second air conditioning throttle means connected between the first and second air conditioners, wherein the first refrigerant refrigerant heat exchanger is more than the second air conditioning throttle means of the bypass circuit. The second refrigerant refrigerant inserted into the air-conditioning outdoor heat exchanger side and inserted between the outlet side of the subcooling outdoor heat exchanger and the inlet side of the first subcooling throttling means. The heat exchanger is inserted between the outlet side of the outdoor cooling heat exchanger for article cooling and the inlet side of the throttle means for cooling the article, and the outlet side of the first supercooling throttle means and the third side It is inserted between the inlet side of the compressor.

  In the refrigeration cycle apparatus of the present invention, the first refrigerant circulates, the first compressor, the four-way valve, the outdoor heat exchanger for air conditioning, the indoor heat exchanger for air conditioning, and the outdoor heat for air conditioning. A first refrigeration cycle having a first air-conditioning throttle means provided between the exchanger and the air-conditioning indoor heat exchanger, wherein a plurality of the first refrigerants are arranged to flow in series, A second refrigerant circulating, a second compressor, an article cooling outdoor heat exchanger, a first refrigerant refrigerant heat exchanger in which the first refrigerant and the second refrigerant exchange heat. A second refrigeration cycle having a first article cooling throttling means and an article cooling indoor heat exchanger, a third refrigerant circulates, a third compressor, and an outdoor cooling heat exchange A second refrigerant refrigerant heat exchanger for exchanging heat between the second refrigerant and the third refrigerant; A third refrigeration cycle having one end connected to a flow path between the first refrigeration cycle and the first air conditioning throttle means provided in the first refrigeration cycle, and the other end connected to the first air conditioning throttle. And a bypass circuit having a second air conditioning throttle means connected between the air conditioning outdoor heat exchanger and the first refrigerant refrigerant heat exchanger of the bypass circuit Inserted between the air conditioning outdoor heat exchanger side from the second air conditioning throttling means and inserted between the article cooling outdoor heat exchanger and the first article cooling throttling means, The refrigerant / refrigerant heat exchanger is inserted between the outlet side of the outdoor heat exchanger for cooling the article and the inlet side of the first cooling means for cooling the article, and the outlet of the first supercooling throttle means. It is inserted between the side and the entrance side of the third compressor.

  In the refrigeration cycle apparatus of the present invention, the first refrigerant circulates, the first compressor, the first article cooling outdoor heat exchanger, the first article cooling throttle means, A first refrigeration cycle having an article cooling indoor heat exchanger, a second refrigerant circulates, a second compressor, a second article cooling outdoor heat exchanger, and a second article cooling. A second refrigeration cycle having a squeezing means and a second article cooling indoor heat exchanger, a third refrigerant is circulated, a third compressor, an overcooling outdoor heat exchanger, The first refrigerant and the third refrigerant exchange heat, the supercooling throttle means, the second refrigerant and the third refrigerant exchange heat. A third refrigeration cycle having a second refrigerant / refrigerant heat exchanger to perform, one end of the first refrigerant cooling outdoor heat exchanger and the first The other end is connected between the outlet side of the first article cooling indoor heat exchanger and the inlet side of the first compressor. And a bypass circuit having a third article cooling throttle means, wherein the first refrigerant refrigerant heat exchanger is inserted downstream of the third article cooling throttle means in the bypass circuit. And the second refrigerant refrigerant heat exchanger is inserted between the outlet side of the subcooling outdoor heat exchanger and the inlet side of the subcooling throttle means, and the second refrigerant cooling heat exchanger Inserted between the outlet side of the exchanger and the inlet side of the second article cooling throttle means, and between the outlet side of the supercooling throttle means and the inlet side of the third compressor It is inserted.

In the refrigeration cycle apparatus of the present invention, the first refrigerant circulates, the first compressor, the four-way valve, the outdoor heat exchanger for air conditioning, the indoor heat exchanger for air conditioning, and the outdoor heat for air conditioning. A first refrigeration cycle having a first air-conditioning throttle means provided between the exchanger and the air-conditioning indoor heat exchanger, wherein a plurality of the first refrigerants are arranged to flow in series , second refrigerant circulates, the second refrigerant cycle having a second compressor, and stuff products cooling outdoor heat exchanger, and means diaphragm goods product cooling, and stuff products cooling indoor heat exchanger, the And the third refrigerant circulates, the third compressor, the subcooling outdoor heat exchanger, the first refrigerant and the third refrigerant exchange heat with each other. Yusuke and vessels, a first supercooling throttle means, and a second refrigerant-refrigerant heat exchanger and the second refrigerant and the third refrigerant performs heat exchange, the A third refrigeration cycle, comprising a front Symbol first refrigerant-refrigerant heat exchanger is connected to a flow path between said first said first provided plurality in a refrigeration cycle of the air conditioning throttle means which is connected between the outlet side of the supercooling outdoor heat exchanger and the entry side of the first supercooling throttle means, said second refrigerant-refrigerant heat exchanger before SL product article cooled outdoor heat with is connected between the input side of the output side and the front SL product article cooling throttle means of exchangers, the entrance side of the exit side of the third compressor of the first supercooling throttle means It is connected between them.

  According to the present invention, when a plurality of heat loads are provided, a refrigeration cycle apparatus that always maintains a high refrigeration capacity and a high COP as compared with a conventional refrigeration cycle apparatus that does not perform heat exchange, thereby realizing energy saving. Can be obtained.

  According to the present invention, when a plurality of heat loads are provided, a general-purpose air conditioner or refrigerator is used to constantly maintain a high refrigerating capacity and a high COP compared to a conventional refrigeration cycle apparatus that does not perform heat exchange. Thus, a refrigeration cycle apparatus that achieves energy saving can be obtained.

Embodiment 1 FIG.
1 and 3 to 7 show a refrigeration cycle apparatus showing Embodiment 1 of the present invention. First, the configuration and operation of the refrigeration cycle will be described with reference to FIG. As shown in FIG. 1, the refrigeration cycle apparatus includes an air conditioning refrigeration cycle 1, a refrigeration or refrigeration cycle 2, and a supercooling refrigeration cycle 3. The air conditioning refrigeration cycle 1 and the supercooling The refrigeration cycle 3 is a refrigerant refrigerant heat exchanger 41a, and the refrigeration or refrigeration cycle 2 and the supercooling refrigeration cycle 3 are refrigerant refrigerant heat exchangers 51, which exchange heat without mixing the two refrigerants. It is configured as follows.

  The air-conditioning refrigeration cycle 1 in which the air-conditioning refrigerant circulates is constituted by a main circuit that performs indoor air-conditioning and a branch circuit that performs heat exchange with the supercooling refrigeration cycle 3, and the main circuit that performs indoor air-conditioning is an air-conditioning compressor. 11, an air conditioning outdoor heat exchanger 12, an air conditioning liquid receiver 14, an air conditioning throttle means 15 a, 15 b, 15 c and an air conditioning indoor heat exchanger 17 a, 17 b are connected by an air conditioning refrigerant pipe 10. The branch circuit configured to perform heat exchange with the supercooling refrigeration cycle 3 includes the refrigerant refrigerant heat exchanger 41a and the air conditioning throttle means 19a, 19b, 19c, and the air conditioning refrigerant pipes 10a, 10b, 10c. It is comprised by connecting by.

  When the air-conditioning refrigeration cycle is in the cooling mode, the air-conditioning refrigerant that has exited the air-conditioning compressor 11 is directed from the four-way valve 18 to the air-conditioning outdoor heat exchanger 12, and the air-conditioning outdoor heat exchanger 12 is outside the air-conditioning outdoor. The fan 13 radiates heat to the outdoor air, expands in the air conditioning throttle means 15c and becomes an intermediate pressure refrigerant, and further expands in the air conditioning throttle means 15a and 15b to become a low-temperature and low-pressure refrigerant. By the action of 16b, heat is absorbed by the indoor heat exchangers 17a and 17b for air conditioning and cold is supplied into the room. On the other hand, a part of the air-conditioning refrigerant exiting the air-conditioning throttle means 15c branches off from the air-conditioning refrigerant pipe 10a, becomes a low-temperature and low-pressure refrigerant by the air-conditioning throttle means 19a, and is subcooled by the refrigerant refrigerant heat exchanger 41a. 3 and evaporates by exchanging heat with the high-temperature supercooling refrigerant flowing through 3, and returns to the air conditioning compressor 11 through the air conditioning refrigerant pipe 10c. At this time, the air conditioning throttle means 19b is closed, the air conditioning throttle means 19c is open, and the flow rate to the branch circuit is adjusted by the opening degree of the air conditioning throttle means 19a.

  When the air-conditioning refrigeration cycle is in the heating mode, the air-conditioning refrigerant exiting the air-conditioning compressor 11 is directed from the four-way valve 18 to the air-conditioning indoor heat exchangers 17a and 17b and to the air-conditioning indoor heat exchangers 17a and 17b. Then, the indoor air blowers 16a and 16b for air conditioning supply warm heat into the room, expands in the air conditioning throttle means 15a and 15b to become an intermediate pressure refrigerant, and further becomes a low-temperature and low-pressure refrigerant in the air conditioning throttle means 15c. The outdoor fan 13 absorbs heat and evaporates in the outdoor heat exchanger 12 for air conditioning. On the other hand, part of the air-conditioning refrigerant exiting the air-conditioning throttle means 15a, 15b branches off from the air-conditioning refrigerant pipe 10a, becomes a low-temperature low-pressure refrigerant by the air-conditioning throttle means 19a, and is used for supercooling by the refrigerant-refrigerant heat exchanger 41a. Heat exchange with the high-temperature supercooling refrigerant flowing in the refrigeration cycle 3 evaporates and merges with the air conditioning refrigerant that has passed through the air conditioning throttle means 15c through the air conditioning refrigerant pipe 10b. At this time, the air conditioning throttle means 19c is closed, the air conditioning throttle means 19b is open, and the flow rate to the branch circuit is adjusted by the opening degree of the air conditioning throttle means 19a.

  The refrigeration or refrigeration refrigeration cycle 2 in which the refrigeration or refrigeration refrigerant circulates includes a refrigeration or refrigeration compressor 21, a refrigeration or refrigeration outdoor heat exchanger 22, and a refrigeration or refrigeration receiver 24. And refrigerant refrigerant heat exchanger 51, refrigeration or refrigeration throttling means 25a, 25b, and refrigeration or refrigeration indoor heat exchangers 27a, 27b are connected by refrigeration or refrigeration refrigerant piping 20. It is composed.

  The refrigeration or refrigeration refrigerant exiting the refrigeration or refrigeration compressor 21 radiates heat to the outdoor air by the refrigeration or refrigeration outdoor heat exchanger 22 and acts as a refrigerant refrigerant. The heat exchanger 51 exchanges heat with the low-temperature supercooling refrigerant flowing in the supercooling refrigeration cycle 3 to increase the degree of supercooling, and expands in the refrigeration or freezing squeezing means 25a and 25b to cause low-temperature and low-pressure. It becomes a refrigerant, absorbs heat in the refrigeration or refrigeration indoor heat exchangers 27a and 27b by the action of the refrigeration or refrigeration indoor fans 26a and 26b, and supplies cold heat to the room.

  The supercooling refrigeration cycle 3 in which the supercooling refrigerant circulates includes a supercooling compressor 31, a supercooling outdoor heat exchanger 32, a supercooling liquid receiver 34, a refrigerant refrigerant heat exchanger 41a, The subcooling throttling means 35 and the refrigerant refrigerant heat exchanger 51 are connected by a supercooling refrigerant pipe 30.

  The supercooling refrigerant that has exited the supercooling compressor 31 is radiated to the outdoor air by the supercooling outdoor heat exchanger 32 by the action of the supercooling outdoor blower 33, and the refrigerant refrigerant heat exchanger 41a is used for air conditioning. Heat exchange with the low-temperature air-conditioning refrigerant flowing in the refrigeration cycle 1 increases the degree of supercooling, expands in the subcooling throttling means 35 to become a low-temperature low-pressure refrigerant, and refrigerates in the refrigerant refrigerant heat exchanger 51 Heat exchanges with the high-temperature refrigeration or refrigeration refrigerant flowing through the refrigeration cycle 2 evaporates and returns to the supercooling compressor 31.

  In FIG. 1, the air conditioning throttle means 19b and 19c are used as the flow path switching means of the air conditioning refrigerant pipes 10b and 10c, so that energy saving is not greatly deteriorated even if a cheaper flow path switching means is used. Therefore, you may comprise using a solenoid valve or a check valve. In addition, a part of the air-conditioning refrigerant exiting the air-conditioning throttle means 15a and 15b during the heating is branched from the air-conditioning refrigerant pipe 10a. However, by fully closing the air-conditioning throttle means 15c, all of the air-conditioning refrigerant is removed. You may flow through the refrigerant piping 10a for air conditioning. The air conditioning throttle means 15a, 15b, 15c, 19a, the refrigeration or refrigeration throttle means 25a, 25b, and the supercooling throttle means 35 are low-cost refrigerant flow rate adjusting means such as capillaries, or precise flow rates by electronic expansion valves. Any of the control means may be used.

  The air-conditioning compressor 11, the refrigeration or refrigeration compressor 21, and the supercooling compressor 31 may be any of various types such as reciprocating, rotary, scroll, and screw, and the number of rotations can be varied. Or a fixed number of revolutions.

  The refrigerant flowing in the air-conditioning refrigeration cycle 1, the refrigeration or refrigeration refrigeration cycle 2, and the supercooling refrigeration cycle 3 may be any refrigerant, such as natural refrigerants such as carbon dioxide, hydrocarbons, helium, HFC410A, Any of refrigerants that do not contain chlorine, such as alternative refrigerants such as HFC407C and HFC404A, or fluorocarbon refrigerants such as R22 and R134a that are used in existing products may be used.

  In addition, the air-conditioning refrigeration cycle 1, the refrigeration or refrigeration refrigeration cycle 2, and the supercooling refrigeration cycle 3 are independent refrigerant circuits, and the refrigerants flowing through them may be of the same type or different. However, the refrigerant refrigerant heat exchangers 41a and 51 exchange heat with each other without being mixed with each other.

  Moreover, although the case where each refrigerant | coolant absorbs heat from air in the outdoor heat exchanger 12 for an air conditioning, the outdoor heat exchanger 22 for refrigeration or freezing, and the outdoor heat exchanger 32 for supercooling is shown, it does not restrict to this Alternatively, heat may be absorbed from water, refrigerant, brine, or the like. Further, the outdoor air blower 13 for air conditioning, the outdoor blower 23 for refrigeration or freezing, and the outdoor blower 33 for supercooling may be a pump or the like. FIG. 1 shows an example of a configuration in which there are two indoor heat exchangers for air conditioning and two indoor heat exchangers for refrigeration or refrigeration. However, the number of units may be three or more or one. They may be different, or the capacity of each indoor unit may vary from large to small, or all of them may have the same capacity. Moreover, although the case where the excess refrigerant | coolant was each stored with a liquid receiver in the refrigerating cycle 1 for air conditioning, the refrigerating cycle 2 for freezing or freezing, and the refrigerating cycle 3 for supercooling was shown, it is not restricted to this, You may remove a liquid receiver as storing in the heat exchanger used as a heat radiator.

  FIG. 2 shows the refrigeration cycle 1 for air conditioning, the refrigeration cycle 2 for refrigeration or refrigeration 2 and the refrigeration cycle 3 for supercooling shown in the Ph diagram. FIG. 2A shows a Ph diagram in the cooling mode, and FIG. 2B shows a Ph diagram in the heating mode. In FIG. 2, the Ph diagram of the refrigeration cycle apparatus according to the present invention is indicated by a solid line, and the Ph diagram when the refrigeration or refrigeration cycle 2 does not exchange heat with the supercooling refrigeration cycle 3 is indicated by a dotted line. When the subcooling refrigeration cycle 3 exchanges heat with the refrigeration or refrigeration refrigeration cycle 2 but does not exchange heat with the air conditioning refrigeration cycle 1, the Ph diagram in the case of the air conditioning refrigeration cycle 1 Shows a Ph diagram when the heat is not exchanged with the supercooling refrigeration cycle 3 by a two-dot chain line.

  As can be seen from FIG. 2, in the refrigeration cycle apparatus according to the present invention, the temperature of the refrigerant at the inlet of the refrigeration or freezing throttling means 25a, 25b is lower by ΔTc2 than when operating alone without performing heat exchange, The enthalpy difference Δh of the refrigerant increases by this temperature difference between the inlet side and the outlet side of the refrigeration or refrigeration indoor heat exchangers 27a and 27b, and the per unit refrigerant flow rate in the refrigeration or refrigeration indoor heat exchangers 27a and 27b increases. The amount of heat absorbed by the refrigerant, the so-called refrigeration effect, increases, and the refrigeration capacity of the refrigeration cycle 2 for refrigeration or refrigeration increases.

  At this time, the circulation amount of the refrigeration or freezing refrigerant with respect to the same refrigeration or freezing heat load is reduced, and less power is required for circulation of the refrigeration or freezing refrigerant. The COP of the refrigeration cycle 2 becomes higher than when operating alone without performing heat exchange, thus saving energy. In addition, since the pressure loss in the piping is reduced by reducing the refrigerant circulation amount, the piping size of the refrigeration cycle 2 for refrigeration or freezing can be reduced, the workability is improved, and the heat loss in the piping is reduced to save energy. It becomes.

  Further, the supercooling refrigeration cycle 3 can increase the degree of supercooling and increase the refrigeration capacity by heat exchange with the air conditioning refrigeration cycle 1 compared with the case where there is no heat exchange. It saves energy compared to the case where there is no heat exchange.

  Further, since the supercooling refrigeration cycle 3 is operated so that the outlets of the refrigeration or refrigeration throttling means 25a, 25b are two-phased, the evaporation temperature Te3 is usually the evaporation temperature of the refrigeration or refrigeration cycle 2 for refrigeration. It becomes higher than Te2. Further, as shown in FIG. 1, when the radiator is configured by an air-cooled heat exchanger using outside air for both the supercooling refrigeration cycle 3 and the refrigeration or refrigeration cycle 2, the condensing temperature is approximately the same. The COP of No. 3 is higher than the COP when the refrigeration or refrigeration cycle is operated alone without performing heat exchange.

  Further, when the air-conditioning refrigeration cycle 1 is in the cooling mode, the evaporation temperature Te1 is often used at least at 0 ° C. or higher, and the evaporation temperature of the refrigeration or freezing refrigeration cycle 2 used for article cooling is used. Since Te2 is often used at about -10 ° C for refrigeration applications and about -40 ° C for refrigeration applications, the evaporation temperature is higher in the refrigeration cycle 1 for air conditioning than in the refrigeration cycle 2 for refrigeration or freezing. Become. Further, as shown in FIG. 1, when the radiator is configured by an air-cooled heat exchanger using outside air for both the air-conditioning refrigeration cycle 1 and the refrigeration or refrigeration cycle 2, the condensing temperature is approximately the same. The COP of the refrigeration or the refrigeration cycle for refrigeration is higher than that when the refrigeration cycle for refrigeration is operated alone without performing heat exchange.

  The heat received when the air-conditioning refrigeration cycle 1 increases the degree of supercooling of the sub-cooling refrigeration cycle 3 becomes a cooling load when the air-conditioning refrigeration cycle 1 is in the cooling mode, and the mechanical input in the air-conditioning compressor. However, in the heating mode, it becomes a heat source of the evaporator, leading to an increase in the evaporation temperature or a reduction in the input of the blower for the evaporator. Therefore, both the air-conditioning refrigeration cycle 1 and the supercooling refrigeration cycle 3 exchange heat. The COP is higher than when no operation is performed.

Therefore, the COP of the refrigeration cycle apparatus according to the present invention does not perform heat exchange between the air-conditioning refrigeration cycle and the refrigeration or refrigeration cycle regardless of whether the air-conditioning refrigeration cycle is in the cooling mode or the heating mode. It becomes higher than the COP in the case of operating independently each, and it becomes energy saving.
Even when the air-conditioning refrigeration cycle 1 is stopped due to power-off, thermo-off, replacement for replacing refrigerant or oil, maintenance for replacing or repairing equipment, etc., Since the degree of supercooling of the refrigeration or freezing refrigeration cycle 2 can be increased by heat exchange, the refrigeration effect or COP is higher than when the refrigeration or freezing refrigeration cycle 2 operates alone without heat exchange. Both can maintain large operation and save energy.

  Further, when the outside air temperature is high and the air conditioning load is high, and the evaporation temperature of the air conditioning refrigeration cycle 1 is high, a refrigeration cycle apparatus configured only by a conventional air conditioning refrigeration cycle and a refrigeration or refrigeration cycle. In the refrigeration cycle apparatus according to the present invention, the degree of supercooling of the refrigeration cycle for refrigeration or freezing could not be increased sufficiently. Since the degree of supercooling of the refrigeration cycle 2 can be increased, energy can be saved more than when the refrigeration or refrigeration cycle is operated alone without heat exchange.

  FIG. 3 shows, in addition to the refrigeration cycle apparatus shown in FIG. 1, a supercooling refrigerant pipe 30a arranged in parallel so as to bypass the supercooling outdoor heat exchanger 32, and the supercooling refrigerant pipe 30a and the supercooling. Supercooling throttling means 39a and 39b for controlling distribution of the supercooling refrigerant flowing to the outdoor heat exchanger 32, and supercooling bypassing the supercooling outdoor heat exchanger 32 upstream of the supercooling receiver 34 1 shows a refrigeration cycle apparatus comprising an air conditioning refrigerant and a refrigerant refrigerant heat exchanger 41b that exchange heat with a supercooling refrigerant arranged to function as a refrigerant radiator.

  In FIG. 3, the basics of the air-conditioning refrigeration cycle 1, the refrigeration or freezing refrigeration cycle 2, and the supercooling refrigeration cycle 3 with the supercooling throttling means 39b opened and the supercooling throttling means 39a closed. Since the operation is the same as that of FIG.

  In FIG. 3, when the air-conditioning refrigeration cycle 1 performs a heating operation, when the supercooling throttle means 39b of the supercooling refrigeration cycle 3 is closed and the supercooling throttle means 39a is opened, the refrigeration shown in FIG. In the cycle device, all the heat that has been radiated to the outside air in the subcooling outdoor heat exchanger 32 can be used as the evaporation heat source of the air-conditioning refrigeration cycle 1 via the refrigerant refrigerant heat exchanger 41b. In addition to the refrigeration cycle apparatus shown, it is possible to increase the evaporation temperature of the air-conditioning refrigeration cycle 1 or to reduce the input of the blower for the evaporator, thereby improving the COP and realizing energy saving.

  FIG. 4 shows a refrigeration cycle apparatus in which the supercooling receiver 34 and the refrigerant / refrigerant heat exchanger 41b are removed from the refrigeration cycle apparatus shown in FIG.

  In FIG. 4, the basics of the air-conditioning refrigeration cycle 1, the refrigeration or refrigeration cycle 2, and the supercooling refrigeration cycle 3 with the supercooling throttling means 39b opened and the supercooling throttling means 39a closed. Since the operation is the same as in FIG. 1 except that the excess refrigerant is stored in the radiator instead of the liquid receiver, the description is omitted.

  In FIG. 4, when the air-conditioning refrigeration cycle 1 performs a heating operation, when the supercooling throttle means 39b of the supercooling refrigeration cycle 3 is closed and the supercooling throttle means 39a is opened, the refrigeration shown in FIG. In the cycle device, all the heat that has been radiated to the outside air in the subcooling outdoor heat exchanger 32 can be used as the evaporation heat source of the air-conditioning refrigeration cycle 1 via the refrigerant refrigerant heat exchanger 41a. In addition to the refrigeration cycle apparatus shown, it is possible to increase the evaporation temperature of the air-conditioning refrigeration cycle 1 or to reduce the input of the blower for the evaporator, thereby improving the COP and realizing energy saving.

  Further, in FIG. 4, since there is no liquid receiver as in FIG. 3, a refrigerant refrigerant heat exchanger as a radiator is disposed upstream of the liquid receiver, and a degree of supercooling is increased downstream of the liquid receiver. Since it is not necessary to use a configuration in which the refrigerant / refrigerant heat exchanger is arranged, the number of refrigerant / refrigerant heat exchangers can be reduced, so that energy saving can be realized at a lower cost.

  5 shows, in addition to the refrigeration cycle apparatus shown in FIG. 1, an air conditioning refrigerant pipe 10d arranged in parallel so as to bypass the air conditioning outdoor heat exchanger 12, an air conditioning refrigerant pipe 10d, and an air conditioning outdoor heat exchange. 1 shows a refrigeration cycle apparatus comprising air conditioning throttle means 19d, 19e for controlling the distribution of refrigerant flowing into the vessel 12.

  In FIG. 5, the basic operation in a state where the air conditioning throttle means 19e is opened and the air conditioning throttle means 19d is closed is substantially the same as that of the refrigeration cycle apparatus shown in FIG.

When the air-conditioning refrigeration cycle 1 shown in FIG. 5 performs the heating operation with the air-conditioning throttle means 19e opened and the air-conditioning throttle means 19d closed, the heat exchange amount in the refrigerant refrigerant heat exchanger 41a is the air-conditioning refrigeration. If it is less than the amount of heat of evaporation required by cycle 1, the air-conditioning outdoor heat exchanger 12 must function as an evaporator, so the evaporation temperature needs to be lower than the temperature of the outside air. If the amount of heat exchange in the exchanger 41a is equal to or greater than the amount of heat of evaporation required by the air-conditioning refrigeration cycle 1, the air-conditioning outdoor heat exchanger 12 does not need to function as an evaporator, so the evaporation temperature is set higher than the outside air temperature. I can do it.
However, in this case, the air-conditioning outdoor heat exchanger 12 functions as a radiator and acts in a direction that hinders increase in the evaporation temperature.
In such a case, in FIG. 5, when the air conditioning throttle means 19 e of the air conditioning refrigeration cycle 1 is closed and the air conditioning throttle means 19 d is opened, the air conditioning refrigerant exchanges heat with the outside air in the air conditioning outdoor heat exchanger 12. Therefore, the evaporating temperature of the air-conditioning refrigeration cycle 1 can be increased or the evaporator fan input can be reduced more than the refrigeration cycle apparatus shown in FIG. realizable.

  5 shows, in addition to the refrigeration cycle apparatus shown in FIG. 1, an air conditioning refrigerant pipe 10d arranged in parallel so as to bypass the air conditioning outdoor heat exchanger 12, an air conditioning refrigerant pipe 10d, and the air conditioning outdoor unit. Air-conditioning throttling means 19d and 19e for controlling the distribution of the air-conditioning refrigerant flowing to the heat exchanger 12, but with respect to the refrigeration cycle apparatus shown in FIGS. A circuit that bypasses the heat exchanger 12 may be added, and in this case, the same effect can naturally be expected.

  Further, when the air-conditioning refrigeration cycle 1 is controlled, a control device (control means) for controlling the refrigeration or refrigeration cycle 2 and a control device for controlling the supercooling refrigeration cycle 3 each have communication means. If mutual information can be exchanged by wired or wireless communication, control can be performed in cooperation, so that a more advanced and more stable energy saving system can be constructed.

  For example, in the refrigeration cycle apparatus shown in FIGS. 1 and 3 to 5, the operating state of the refrigeration or refrigeration cycle 2 is changed from the control apparatus for the refrigeration or refrigeration cycle 2 to the control apparatus for the supercooling refrigeration cycle 3. If the system is configured so that the refrigeration cycle 2 for refrigeration or refrigeration for refrigeration 2 is turned on / off, the ON / OFF timing of the refrigeration cycle 3 for supercooling can be controlled, eliminating unnecessary operation and saving energy. Become.

  Further, in the refrigeration cycle apparatus shown in FIG. 3 or FIG. 4, the system is configured such that the operating state of the air conditioning refrigeration cycle 1 is transmitted from the control apparatus of the air conditioning refrigeration cycle 1 to the control apparatus of the supercooling refrigeration cycle 3. Then, when the air-conditioning refrigeration cycle 1 is in the heating mode, the supercooling throttle means 39b is closed and the supercooling throttle means 39a is opened, so that the high-temperature supercooling discharged from the supercooling compressor is opened. By bypassing the refrigerant, the operation can be controlled so that all of this heat is used as the evaporation heat source of the air-conditioning refrigeration cycle 1 without being exhausted by the subcooling refrigeration cycle 3 at an appropriate timing. It becomes energy saving.

  Normally, the evaporation temperature of the air-conditioning refrigeration cycle 1 is about several degrees lower than the outside air temperature during the heating mode operation, has a difference of 20 ° C. or more during the cooling mode operation, and is the same as the outside temperature during the operation stop. The temperature is about. Therefore, the refrigerant refrigerant heat exchanger 41a or 41b is provided with an evaporating temperature detecting means for the air conditioning refrigerant, and the system is configured so that the detected value and the outside air temperature are transmitted to the control device of the supercooling refrigeration cycle 3. By doing so, the operating state of the air-conditioning refrigeration cycle 1 can be estimated without communicating with the control device for the air-conditioning refrigeration cycle 1, so that energy saving can be realized at a lower cost.

  FIG. 6 shows a refrigeration cycle apparatus in which the air conditioning refrigerant pipe 10c and the air conditioning throttle means 19c are removed from the refrigeration cycle apparatus shown in FIG. 1. Also in this refrigeration cycle apparatus, the energy saving effect according to the present invention is obtained. I can do it.

  When the air-conditioning refrigeration cycle 1 is in the heating mode, the refrigerant flowing through the refrigerant-refrigerant heat exchanger 41a flows from the air-conditioning throttle means 19a toward the air-conditioning throttle means 19b in both FIG. 1 and FIG. When 1 is in the cooling mode, in FIG. 1, it flows from the air conditioning throttle means 19a toward the air conditioning throttle means 19b as in the heating mode, whereas in FIG. It flows in the direction of the throttle means 19a.

  In the refrigeration cycle apparatus shown in FIG. 6, the raw material cost can be reduced by the amount excluding the air conditioning refrigerant pipe 10c and the air conditioning throttle means 19c, and the number of piping construction work steps connected to the air conditioning refrigeration cycle is reduced. Since the cost can be reduced, energy saving can be realized at a lower cost.

  FIG. 7 shows a portion of the air-conditioning refrigerant pipe 10 that passes through the air-conditioning throttle means 15c and is arranged in parallel with the air-conditioning refrigerant pipes 10a and 10b, and the air-conditioning throttle means 15c from the refrigeration cycle apparatus shown in FIG. The refrigeration cycle in which, is removed is shown, and this refrigeration cycle apparatus can also achieve the same effects as in FIG.

  When the air-conditioning refrigeration cycle 1 is in the heating mode, the refrigerant circulation amount circulating through the air-conditioning refrigerant pipe 10a can be adjusted by adjusting the air-conditioning throttle means 19a and the air-conditioning throttle means 15c in FIG. In FIG. 7, all the refrigerant circulates through the air conditioning refrigerant pipe 10a.

  In the refrigeration cycle apparatus shown in FIG. 7, since the air conditioning throttle means 15c can be reduced, energy saving can be realized at a lower cost.

Embodiment 2. FIG.
8 and 10 to 14 show a refrigeration cycle apparatus showing Embodiment 2 of the present invention. First, the configuration and operation of the refrigeration cycle will be described with reference to FIG. As shown in FIG. 8, the refrigeration cycle apparatus includes an air conditioning refrigeration cycle 1, a refrigeration or refrigeration cycle 2, and a supercooling refrigeration cycle 3. The air conditioning refrigeration cycle 1 and refrigeration cycle Alternatively, the refrigeration cycle 2 is a refrigerant / refrigerant heat exchanger 41a, and the refrigeration or refrigeration cycle 2 and the supercooling refrigeration cycle 3 are refrigerant / refrigerant heat exchangers 51, which exchange heat without mixing the two refrigerants. Is configured to do.

  The air-conditioning refrigeration cycle 1 in which the air-conditioning refrigerant circulates includes a main circuit that performs indoor air-conditioning and a branch circuit that performs heat exchange with the refrigeration or refrigeration cycle 2 and the main circuit that performs indoor air-conditioning is used for air-conditioning. The compressor 11, the air conditioning outdoor heat exchanger 12, the air conditioning receiver 14, the air conditioning throttling means 15 a, 15 b, 15 c, and the air conditioning indoor heat exchangers 17 a, 17 b are connected to the air conditioning refrigerant pipe 10. The branch circuit configured to be connected to each other and exchanging heat with the refrigeration or refrigeration refrigeration cycle 2 includes the refrigerant refrigerant heat exchanger 41a and the air conditioning throttle means 19a, 19b, 19c, and the air conditioning refrigerant pipe 10a. 10b and 10c are used for connection.

  When the air-conditioning refrigeration cycle is in the cooling mode, the air-conditioning refrigerant exiting the air-conditioning compressor 11 is directed from the four-way valve 18 to the air-conditioning outdoor heat exchanger 12, and the air-conditioning outdoor heat exchanger 12 uses the air-conditioning outdoor fan. 13 radiates heat to the outdoor air, expands in the air conditioning throttle means 15c and becomes an intermediate pressure refrigerant, further expands in the air conditioning throttle means 15a and 15b and becomes a low-temperature and low-pressure refrigerant, and the air conditioner indoor fans 16a and 16b. As a result, the air-conditioning indoor heat exchangers 17a and 17b absorb heat and supply cold air to the room, and a part of the air-conditioning refrigerant exiting the air-conditioning throttle means 15c branches off from the air-conditioning refrigerant pipe 10a. The squeezing means 19a becomes a low-temperature and low-pressure refrigerant, and the refrigerant refrigerant heat exchanger 41a evaporates by exchanging heat with the high-temperature refrigeration or refrigeration refrigerant flowing in the refrigeration or refrigeration cycle 2. , Back through the air conditioning refrigerant pipe 10c to the air conditioning compressor 11. At this time, the air conditioning throttle means 19b is closed, the air conditioning throttle means 19c is open, and the flow rate to the branch circuit is adjusted by the opening degree of the air conditioning throttle means 19a.

  When the air-conditioning refrigeration cycle is in the heating mode, the air-conditioning refrigerant exiting the air-conditioning compressor 11 is directed from the four-way valve 18 to the air-conditioning indoor heat exchangers 17a and 17b and to the air-conditioning indoor heat exchangers 17a and 17b. Then, the indoor air blowers 16a and 16b for air conditioning supply warm heat into the room, expands in the air conditioning throttle means 15a and 15b to become an intermediate pressure refrigerant, and further becomes a low-temperature and low-pressure refrigerant in the air conditioning throttle means 15c. The outdoor fan 13 absorbs heat and evaporates in the air-conditioning outdoor heat exchanger 12, and a part of the air-conditioning refrigerant exiting the air-conditioning throttle means 15a and 15b branches off from the air-conditioning refrigerant pipe 10a. The squeezing means 19a becomes a low-temperature and low-pressure refrigerant, and the refrigerant refrigerant heat exchanger 41a exchanges heat with the high-temperature refrigeration or refrigeration refrigerant flowing in the refrigeration or refrigeration cycle 2 for steaming. The air-conditioning refrigerant that has passed through the air-conditioning refrigerant pipe 10b and passed through the air-conditioning throttle means 15c joins. At this time, the air conditioning throttle means 19c is closed, the air conditioning throttle means 19b is open, and the flow rate to the branch circuit is adjusted by the opening degree of the air conditioning throttle means 19a.

  The refrigeration or refrigeration refrigeration cycle 2 in which the refrigeration or refrigeration refrigerant circulates includes a refrigeration or refrigeration compressor 21, a refrigeration or refrigeration outdoor heat exchanger 22, and a refrigeration or refrigeration receiver 24. The refrigerant refrigerant heat exchanger 41a, the refrigerant refrigerant heat exchanger 51, the refrigeration or refrigeration throttle means 25a, 25b, and the refrigeration or refrigeration indoor heat exchangers 27a, 27b. The refrigerant pipe 20 is used for connection.

  The refrigeration or refrigeration refrigerant exiting the refrigeration or refrigeration compressor 21 radiates heat to the outdoor air by the refrigeration or refrigeration outdoor heat exchanger 22 and acts as a refrigerant refrigerant. The heat exchanger 41a exchanges heat with the low-temperature air-conditioning refrigerant flowing through the air-conditioning refrigeration cycle 1 to increase the degree of supercooling, and the refrigerant-refrigerant heat exchanger 51 further reduces the low-temperature air flowing through the subcooling refrigeration cycle 3. Exchanges heat with the supercooling refrigerant to increase the degree of supercooling, expands in the refrigeration or refrigeration throttle means 25a, 25b to become a low-temperature and low-pressure refrigerant, and by the action of the refrigeration or refrigeration indoor fans 26a, 26b Heat is absorbed by the indoor heat exchangers 27a and 27b for refrigeration or freezing, and cold is supplied into the room.

  The supercooling refrigeration cycle 3 in which the supercooling refrigerant circulates includes a supercooling compressor 31, a supercooling outdoor heat exchanger 32, a supercooling receiver 34, a supercooling throttling means 35, The refrigerant refrigerant heat exchanger 51 is connected by a supercooling refrigerant pipe 30.

  The supercooling refrigerant that has exited the supercooling compressor 31 radiates heat to the outdoor air by the action of the supercooling outdoor fan 33 in the supercooling outdoor heat exchanger 32, and expands in the supercooling throttle means 35. The refrigerant becomes a low-temperature and low-pressure refrigerant, evaporates by exchanging heat with the high-temperature refrigeration or refrigeration refrigerant flowing through the refrigeration or refrigeration cycle 2 in the refrigerant refrigerant heat exchanger 51, and returns to the supercooling compressor 31.

  In FIG. 8, the air conditioning throttle means 19b and 19c are used as the flow path switching means of the air conditioning refrigerant pipes 10b and 10c. Therefore, even if a cheaper flow path switching means is used, the energy saving is greatly deteriorated. Therefore, a solenoid valve or a check valve may be used. In addition, a part of the air-conditioning refrigerant exiting the air-conditioning throttle means 15a and 15b during the heating is branched from the air-conditioning refrigerant pipe 10a. However, by fully closing the air-conditioning throttle means 15c, all of the air-conditioning refrigerant is removed. You may flow through the refrigerant piping 10a for air conditioning. The air conditioning throttle means 15a, 15b, 15c, 19a, the refrigeration or refrigeration throttle means 25a, 25b, and the supercooling throttle means 35 are low-cost refrigerant flow rate adjusting means such as capillaries, or precise flow rates by electronic expansion valves. Any of the control means may be used.

  The air-conditioning compressor 11, the refrigeration or refrigeration compressor 21, and the supercooling compressor 31 may be any of various types such as reciprocating, rotary, scroll, and screw, and the number of rotations can be varied. Or a fixed number of revolutions.

  The refrigerant flowing in the air-conditioning refrigeration cycle 1, the refrigeration or refrigeration refrigeration cycle 2, and the supercooling refrigeration cycle 3 may be any refrigerant, such as natural refrigerants such as carbon dioxide, hydrocarbons, helium, HFC410A, Any of refrigerants that do not contain chlorine, such as alternative refrigerants such as HFC407C and HFC404A, or fluorocarbon refrigerants such as R22 and R134a that are used in existing products may be used.

  In addition, the air-conditioning refrigeration cycle 1, the refrigeration or refrigeration refrigeration cycle 2, and the supercooling refrigeration cycle 3 are independent refrigerant circuits, and the refrigerants flowing through them may be of the same type or different. However, the refrigerant refrigerant heat exchangers 41a and 51 exchange heat with each other without being mixed with each other.

  Moreover, although the case where each refrigerant | coolant absorbs heat from air in the outdoor heat exchanger 12 for an air conditioning, the outdoor heat exchanger 22 for refrigeration or freezing, and the outdoor heat exchanger 32 for supercooling is shown, it does not restrict to this Alternatively, heat may be absorbed from water, refrigerant, brine, or the like. Further, the outdoor air blower 13 for air conditioning, the outdoor blower 23 for refrigeration or freezing, and the outdoor blower 33 for supercooling may be a pump or the like. FIG. 8 shows an example of the configuration in which there are two indoor heat exchangers for air conditioning and two indoor heat exchangers for refrigeration or freezing. However, the number of units may be three or more or one. They may be different, or the capacity of each indoor unit may vary from large to small, or all of them may have the same capacity. Moreover, although the case where the excess refrigerant | coolant was each stored by a liquid receiver in the refrigerating cycle 1 for air-conditioning, the refrigerating cycle 2 for refrigeration or freezing, and the refrigerating cycle 3 for supercooling was shown, it does not restrict to this but each refrigeration You may store with the heat exchanger used as a heat radiator in a cycle.

  FIG. 9 shows the refrigeration cycle 1 for air conditioning, the refrigeration cycle 2 for refrigerating or refrigeration 2, and the refrigeration cycle 3 for supercooling shown in the Ph diagram. FIG. 9A shows a Ph diagram in the cooling mode, and FIG. 9B shows a Ph diagram in the heating mode. In FIG. 9, the Ph diagram of the refrigeration cycle apparatus according to the present invention is shown by a solid line, and the Ph diagram when the refrigeration or refrigeration cycle does not exchange heat with the air conditioning refrigeration cycle or the supercooling refrigeration cycle. Is a dotted line, and a Ph diagram when the air conditioner does not exchange heat with the refrigeration or refrigeration cycle is indicated by a two-dot chain line.

  As can be seen from FIG. 9, in the refrigeration cycle apparatus according to the present invention, the temperature of the refrigerant at the inlet of the refrigeration or freezing throttling means 25a, 25b is lower by ΔTc2 than when operating alone without performing heat exchange, The enthalpy difference Δh of the refrigerant increases by this temperature difference between the inlet side and the outlet side of the refrigeration or refrigeration indoor heat exchangers 26a and 26b, and per unit refrigerant flow rate in the refrigeration or refrigeration indoor heat exchangers 26a and 26b. The amount of heat absorbed by the refrigerant, the so-called refrigeration effect, increases, and the refrigeration capacity of the refrigeration cycle 2 for refrigeration or refrigeration increases.

  At this time, the circulation amount of the refrigeration or freezing refrigerant with respect to the same refrigeration or freezing heat load is reduced, and less power is required for circulation of the refrigeration or freezing refrigerant. The COP of the refrigeration cycle 2 becomes higher than when operating alone without performing heat exchange, thus saving energy. In addition, since the pressure loss in the piping is reduced by reducing the refrigerant circulation amount, the piping size of the refrigeration cycle 2 for refrigeration or freezing can be reduced, the workability is improved, and the heat loss in the piping is reduced to save energy. It becomes.

  Further, since the supercooling refrigeration cycle 3 is operated so that the outlets of the refrigeration or freezing squeezing means 25a and 25b have two phases, the evaporation temperature is usually higher than the evaporation temperature of the refrigeration or refrigeration cycle 2 for refrigeration. Also gets higher. Further, as shown in FIG. 8, when the radiator is constituted by the air-cooled heat exchanger using the outside air for both the supercooling refrigeration cycle 3 and the refrigeration or freezing refrigeration cycle 2, the condensation temperature becomes approximately the same. The COP of No. 3 is higher than the COP when the refrigeration or refrigeration cycle operates alone without performing heat exchange.

  In the cooling mode, the air-conditioning refrigeration cycle 1 is often used with an evaporation temperature of at least 0 ° C. or more, and the refrigeration or freezing refrigeration cycle 2 used for article cooling has an evaporation temperature of The evaporating temperature is higher in the air-conditioning refrigeration cycle 1 than in the refrigeration or freezing refrigeration cycle 2 because it is often used at about −10 ° C. for refrigeration and about −40 ° C. for refrigeration. Further, as shown in FIG. 8, when the radiator is configured by an air-cooled heat exchanger using outside air for both the air-conditioning refrigeration cycle 1 and the refrigeration or refrigeration cycle 2, the condensing temperature is approximately the same. The COP of the refrigeration or the refrigeration cycle for refrigeration is higher than that when the refrigeration cycle for refrigeration is operated alone without performing heat exchange.

  Further, the heat received when the air-conditioning refrigeration cycle 1 increases the degree of supercooling of the refrigeration or refrigeration cycle 2 becomes a cooling load when the air-conditioning refrigeration cycle 1 is in the cooling mode. Although mechanical input is required, it becomes a heat source for the evaporator in the heating mode, leading to an increase in the evaporation temperature or a reduction in the input to the blower for the evaporator. Therefore, the refrigeration cycle 1 for air conditioning, the refrigeration cycle 2 for refrigeration, or refrigeration In both cases, the COP is higher than when heat exchange is not performed.

Therefore, the COP of the refrigeration cycle apparatus according to the present invention does not perform heat exchange between the air-conditioning refrigeration cycle and the refrigeration or refrigeration cycle regardless of whether the air-conditioning refrigeration cycle is in the cooling mode or the heating mode. It becomes higher than the COP in the case of operating independently each, and it becomes energy saving.
Even when the air-conditioning refrigeration cycle 1 is stopped due to power-off, thermo-off, replacement for replacing refrigerant or oil, maintenance for replacing or repairing equipment, etc., Since the degree of supercooling of the refrigeration or freezing refrigeration cycle 2 can be increased by heat exchange, the refrigeration effect or COP is higher than when the refrigeration or freezing refrigeration cycle 2 operates alone without heat exchange. Both can maintain large operation and save energy.

  Further, when the outside air temperature is high and the air conditioning load is high, and the evaporation temperature of the air conditioning refrigeration cycle 1 is high, a refrigeration cycle apparatus configured only by a conventional air conditioning refrigeration cycle and a refrigeration or refrigeration cycle. In the refrigeration cycle apparatus according to the present invention, the degree of supercooling of the refrigeration cycle for refrigeration or freezing could not be increased sufficiently. Since the degree of supercooling of the refrigeration cycle 2 can be increased, energy can be saved more than when the refrigeration or refrigeration cycle is operated alone without heat exchange.

  10 shows, in addition to the refrigeration cycle apparatus shown in FIG. 8, a refrigeration or freezing refrigerant pipe 20a arranged in parallel so as to bypass the refrigeration or freezing outdoor heat exchanger 22, and a refrigeration or freezing Refrigerating or refrigeration throttling means 29a and 29b for controlling distribution of the refrigeration or refrigeration refrigerant flowing to the refrigerant pipe 20a, the refrigeration or refrigeration outdoor heat exchanger 22, and the upstream of the refrigeration or refrigeration receiver 24. The refrigerant / refrigerant heat exchange in which the air-conditioning refrigerant and the refrigeration / refrigeration refrigerant exchange heat with the refrigerant for refrigeration / refrigeration refrigerant that bypasses the refrigeration / refrigeration outdoor heat exchanger 22. The refrigerating cycle apparatus characterized by including the vessel 41b.

  In FIG. 10, the air-conditioning refrigeration cycle 1, the refrigeration or refrigeration cycle 2 and the supercooling refrigeration cycle 3 with the refrigeration or refrigeration throttling means 29b opened and the refrigeration or refrigeration throttling means 29a closed. The basic operation is the same as in FIG.

  In FIG. 10, when the air-conditioning refrigeration cycle 1 performs heating operation, the refrigeration or refrigeration throttle means 29b of the refrigeration or refrigeration refrigeration cycle 2 is closed, and the refrigeration or refrigeration throttle means 29a is opened. In this case, in the refrigeration cycle apparatus of FIG. 8, all the heat that has been radiated to the outside air in the refrigeration or refrigeration outdoor heat exchanger 22 is not radiated, and the evaporation heat source of the air-conditioning refrigeration cycle 1 via the refrigerant refrigerant heat exchanger 41b. Therefore, the evaporating temperature of the air-conditioning refrigeration cycle 1 can be increased or the input of the evaporator fan can be reduced more than in the refrigeration cycle apparatus shown in FIG. 8, thereby improving the COP and realizing energy saving. .

  FIG. 11 shows a refrigeration cycle apparatus in which the refrigeration or refrigeration receiver 24 and the refrigerant / refrigerant heat exchanger 41b are removed from the refrigeration cycle apparatus shown in FIG.

  In FIG. 11, the air-conditioning refrigeration cycle 1, the refrigeration or refrigeration refrigeration cycle 2, and the supercooling refrigeration cycle 3 with the refrigeration or refrigeration throttling means 29b opened and the refrigeration or refrigeration throttling means 29a closed. The basic operation is the same as in FIG. 8 except that the surplus refrigerant is stored in the heat radiator rather than the liquid receiver, and is therefore omitted.

  In FIG. 11, when the air-conditioning refrigeration cycle 1 performs heating operation, the refrigeration or refrigeration throttle means 29b of the refrigeration or refrigeration cycle 2 is closed, and the refrigeration or refrigeration throttle means 29a is opened. In this case, in the refrigeration cycle apparatus of FIG. 8, the heat that has been radiated to the outside air in the refrigeration or refrigeration outdoor heat exchanger 22 can be used as the evaporation heat source of the air-conditioning refrigeration cycle 1 via the refrigerant refrigerant heat exchanger 41a. Further, the evaporating temperature of the air-conditioning refrigeration cycle 1 can be increased or the evaporator blower input can be reduced more than in the refrigeration cycle apparatus shown in FIG. 8, thereby improving the COP and realizing energy saving.

  Moreover, in FIG. 11, since there is no liquid receiver like FIG. 10, the refrigerant | coolant refrigerant | coolant heat exchanger as a heat sink is upstream of a liquid receiver, and the degree of supercooling is increased downstream of a liquid receiver. Since it is not necessary to use a configuration in which the refrigerant / refrigerant heat exchanger is arranged, the number of refrigerant / refrigerant heat exchangers can be reduced, so that energy saving can be realized at a lower cost.

  FIG. 12 shows, in addition to the refrigeration cycle apparatus shown in FIG. 8, an air conditioning refrigerant pipe 10d arranged in parallel so as to bypass the air conditioning outdoor heat exchanger 12, an air conditioning refrigerant pipe 10d, and an air conditioning outdoor heat exchange. 1 shows a refrigeration cycle apparatus comprising air conditioning throttling means 19d, 19e for controlling the distribution of air conditioning refrigerant flowing into the vessel 12.

  In FIG. 12, the state in which the air conditioning throttle means 19e is opened and the air conditioning throttle means 19d is closed is substantially the same as in the refrigeration cycle apparatus shown in FIG.

When the air-conditioning refrigeration cycle 1 shown in FIG. 12 performs heating operation with the air-conditioning throttle means 19e opened and the air-conditioning throttle means 19d closed, the amount of heat exchange in the refrigerant refrigerant heat exchanger 41a is refrigeration for air-conditioning. If it is less than the amount of heat of evaporation required by cycle 1, the air-conditioning outdoor heat exchanger 12 must function as an evaporator, so the evaporation temperature needs to be lower than the temperature of the outside air. If the amount of heat exchange in the exchanger 41a is equal to or greater than the amount of heat of evaporation required by the air-conditioning refrigeration cycle 1, the air-conditioning outdoor heat exchanger 12 does not need to function as an evaporator, so the evaporation temperature is set higher than the outside air temperature. I can do it.
However, in this case, the air-conditioning outdoor heat exchanger 12 functions as a radiator and acts in a direction that hinders increase in evaporation temperature.
In such a case, in FIG. 12, when the air conditioning throttle means 19e of the air conditioning refrigeration cycle 1 is closed and the air conditioning throttle means 19d is opened, the air conditioning refrigerant exchanges heat with the outside air in the air conditioning outdoor heat exchanger 12. Therefore, the evaporating temperature of the air-conditioning refrigeration cycle 1 can be increased or the evaporator blower input can be reduced more than the refrigeration cycle apparatus shown in FIG. realizable.

  In addition to the refrigeration cycle apparatus shown in FIG. 8, FIG. 12 shows an air conditioning refrigerant pipe 10d arranged in parallel so as to bypass the air conditioning outdoor heat exchanger 12, an air conditioning refrigerant pipe 10d, and the air conditioning outdoor. Air-conditioning throttling means 19d and 19e for controlling the distribution of the air-conditioning refrigerant flowing to the heat exchanger 12, but for the refrigeration cycle apparatus shown in FIGS. A circuit that bypasses the heat exchanger 12 may be added, and in this case, the same effect can naturally be expected.

  8 and 10 to 14, the refrigerant / refrigerant heat exchanger 41a is arranged on the upstream side of the refrigerant / refrigerant heat exchanger 51, but the same effect can be obtained even if arranged on the downstream side. The refrigeration or refrigeration refrigerant exiting the refrigeration outdoor heat exchanger is cooled by the supercooling refrigeration cycle 3, and the degree of supercooling of the refrigeration or refrigeration cycle 2 is increased. Furthermore, the degree of supercooling of the refrigeration or freezing refrigeration cycle 2 increases, and the refrigeration effect of the refrigeration or freezing refrigeration cycle increases. At this time, the amount of refrigeration or refrigeration refrigerant circulated for the same refrigeration or refrigeration heat load is reduced, and less power is required to circulate the refrigeration or refrigeration refrigerant. The COP of 2 becomes higher than the case of operating alone without performing heat exchange, thus saving energy. In addition, since the pressure loss in the piping is reduced by reducing the refrigerant circulation amount, the piping size of the refrigeration cycle 2 for refrigeration or freezing can be reduced, the workability is improved, and the heat loss in the piping is reduced to save energy. It becomes.

  Of the refrigerant / refrigerant heat exchanger 41a and the refrigerant / refrigerant heat exchanger 51, the refrigerant refrigerant heat exchanger on the upstream side overcools the refrigeration or refrigeration refrigerant, and the evaporation temperature of the refrigerant refrigerant heat exchanger on the downstream side If the temperature decreases, the heat flows into the refrigerant for refrigeration or freezing, contrary to the purpose of the present invention, which results in counteracting energy saving. Therefore, refrigerant refrigerant heat exchange that exchanges heat with a refrigerant having a lower evaporation temperature. It is certainly energy saving to arrange the vessel downstream.

  In addition, the air-conditioning refrigeration cycle 1 is constrained by the lower limit of the evaporating temperature depending on the outside air temperature and the air-conditioning load, and is generally less than 0 ° C., whereas the supercooling refrigeration cycle 3 is used for refrigeration. Alternatively, if the outlet of the refrigeration or freezing throttling means 25a, 25b of the freezing refrigeration cycle 2 is two-phase, it can be lowered to any number of times. It can be made lower than the evaporation temperature of cycle 1.

  Therefore, the refrigerant refrigerant heat exchanger 41a that exchanges heat with the subcooling refrigeration cycle 3 is more reliably disposed downstream of the refrigerant refrigerant heat exchanger 51 that exchanges heat with the air conditioning refrigeration cycle 1. It becomes energy saving.

  In addition, a control device that controls the refrigeration cycle 1 for air conditioning, a control device that controls the refrigeration cycle 2 for refrigeration or refrigeration, and a control device that controls the refrigeration cycle 3 for supercooling are each provided with communication means and wired. Alternatively, if mutual information can be exchanged by wireless communication, control can be performed in cooperation with each other, so that a more advanced and more stable energy saving system can be constructed.

  For example, in the refrigeration cycle apparatus shown in FIGS. 8 and 10 to 12, the operating state of the refrigeration or refrigeration cycle 2 is changed from the control apparatus for the refrigeration or refrigeration cycle 2 to the control apparatus for the supercooling refrigeration cycle 3. If the system is configured so that the refrigeration cycle 2 for refrigeration or refrigeration for refrigeration 2 is turned on / off, the ON / OFF timing of the refrigeration cycle 3 for supercooling can be controlled, eliminating unnecessary operation and saving energy. Become.

  Further, in the refrigeration cycle apparatus shown in FIG. 8 and FIGS. 10 to 12, for example, when the outside air temperature is low, if the supercooling refrigeration cycle 3 is operated while the air conditioning refrigeration cycle 1 is operating in the heating mode, In some cases, the evaporation temperature of the refrigeration cycle 3 is significantly lowered, the COP of the subcooling refrigeration cycle 3 is lowered, and the COP of the entire system is also lowered. When the refrigerant / refrigerant heat exchanger 41a is arranged on the downstream side of the refrigerant / refrigerant heat exchanger 51, if the air-cooling refrigeration cycle 1 is operating in the heating mode and the supercooling refrigeration cycle 3 is operated, the refrigeration or refrigeration is performed. Since the subcooling refrigeration cycle 3 collects the exhaust heat of the refrigeration cycle 2 upstream of the air conditioning refrigeration cycle 1 and dissipates heat to the outside air, the system COP decreases.

  In such a case, if the system is configured such that the operating state of the air conditioning refrigeration cycle 1 is transmitted from the control device of the air conditioning refrigeration cycle 1 to the control device of the supercooling refrigeration cycle 3, the air conditioning refrigeration cycle 1 is When the heating mode is entered, the operation of the supercooling refrigeration cycle 3 can be reliably stopped at an appropriate timing, thereby saving energy.

  The refrigerant refrigerant heat exchanger 41a or 41b is provided with an evaporating temperature detecting means for the air conditioning refrigerant so that the detected value and the outside air temperature are transmitted to the control device of the supercooling refrigeration cycle 3. For example, the operating state of the air-conditioning refrigeration cycle 1 can be estimated without communicating with the control device of the air-conditioning refrigeration cycle 1, and energy saving can be realized at a lower cost as described above.

  Further, in the refrigeration cycle apparatus shown in FIG. 10 or FIG. 11, if the system is configured such that the operation mode of the air-conditioning refrigeration cycle 1 is transmitted to the control device of the refrigeration or refrigeration cycle 2, the air-conditioning refrigeration cycle When the refrigeration or refrigeration throttling means 29b is closed and the refrigeration or refrigeration throttling means 29a is opened when 1 enters the heating mode, the high temperature refrigeration or refrigeration discharged from the refrigeration or refrigeration compressor is opened. By bypassing the refrigerant for operation, the operation is controlled so that all of this heat is used as the evaporation heat source of the air-conditioning refrigeration cycle 1 without being exhausted by the refrigeration or refrigeration cycle 2 reliably at an appropriate timing. Can save energy.

  The refrigerant refrigerant heat exchanger 41a or 41b is provided with an evaporating temperature detecting means for the air conditioning refrigerant, and the detected value and the outside air temperature are transmitted to the control device of the refrigeration or freezing refrigeration cycle 2. Since the operation state of the air-conditioning refrigeration cycle 1 can be estimated without communicating with the control device for the air-conditioning refrigeration cycle 1, it is possible to realize energy saving at a lower cost as described above. It is.

  FIG. 13 shows a refrigeration cycle apparatus in which the air conditioning refrigerant pipe 10c and the air conditioning throttle means 19c are removed from the refrigeration cycle apparatus shown in FIG. 8, and this refrigeration cycle apparatus also has the same effect as FIG. Can be obtained.

  When the air conditioning refrigeration cycle 1 is in the heating mode, the refrigerant flowing through the refrigerant refrigerant heat exchanger 41a flows from the air conditioning throttle means 19a toward the air conditioning throttle means 19b in both FIGS. When 1 is in the cooling mode, in FIG. 8, as in the heating mode, it flows from the air conditioning throttle means 19a toward the air conditioning throttle means 19b, whereas in FIG. It flows in the direction of the throttle means 19a.

  In the refrigeration cycle apparatus shown in FIG. 6, the raw material cost can be reduced by the amount excluding the air conditioning refrigerant pipe 10c and the air conditioning throttle means 19c, and the number of piping construction work steps connected to the air conditioning refrigeration cycle is reduced. Since the cost can be reduced, energy saving can be realized at a lower cost.

  FIG. 14 shows a part of the air-conditioning refrigerant pipe 10 that passes through the air-conditioning throttle means 15c and is arranged in parallel with the air-conditioning refrigerant pipes 10a and 10b, and the air-conditioning throttle means 15c from the refrigeration cycle apparatus shown in FIG. The refrigeration cycle in which, is removed is shown, and in this refrigeration cycle apparatus, the same effect as in FIG. 13 can be obtained.

  When the air-conditioning refrigeration cycle 1 is in the heating mode, the amount of refrigerant circulating in the air-conditioning refrigerant pipe 10a can be adjusted by adjusting the air-conditioning throttle means 19a and the air-conditioning throttle means 15c in FIG. In FIG. 14, all the refrigerant circulates through the air conditioning refrigerant pipe 10a.

  In the refrigeration cycle apparatus shown in FIG. 14, since the air conditioning throttle means 15c can be reduced, energy saving can be realized at a lower cost.

Embodiment 3 FIG.
FIG. 15 shows a refrigeration cycle apparatus showing Embodiment 3 of the present invention. FIG. 15 is different from FIG. 1 in that the refrigeration cycle on the higher stage side is changed from the air-conditioning refrigeration cycle to the refrigeration or refrigeration cycle. In FIG. 15, the configuration and operation of the refrigeration cycle will be described. As shown in FIG. 15, the refrigeration cycle apparatus includes a first refrigeration or refrigeration cycle 8, a second refrigeration or refrigeration cycle 9, and a supercooling refrigeration cycle 3. The first refrigeration or freezing refrigeration cycle 8 and the supercooling refrigeration cycle 3 are refrigerant refrigerant heat exchangers 41a, and the second refrigeration or freezing refrigeration cycle 9 and the supercooling refrigeration cycle 3 are refrigerants. The refrigerant heat exchanger 51 is configured to perform heat exchange without mixing both refrigerants.

  The first refrigeration or refrigeration cycle 8 in which the first refrigeration or refrigeration refrigerant circulates includes a first refrigeration or refrigeration compressor 81, and a first refrigeration or refrigeration outdoor heat exchanger. 82, first refrigeration or refrigeration receiver 84, refrigerant refrigerant heat exchanger 41a, first refrigeration or refrigeration squeezing means 85a, 85b, and first refrigeration or refrigeration indoor heat. The exchangers 87a and 87b are connected by a first refrigeration or freezing refrigerant pipe 80.

  The first refrigeration or refrigeration refrigerant exiting the first refrigeration or refrigeration compressor 81 is used as the first refrigeration or refrigeration outdoor blower in the first refrigeration or refrigeration outdoor heat exchanger 82. 83 radiates heat to the outdoor air, expands in the first refrigeration or refrigeration throttling means 85a and 85b, and becomes a low-temperature and low-pressure refrigerant. The first refrigeration or refrigeration indoor fans 86a and 86b One refrigeration or freezing indoor heat exchangers 87a and 87b absorb heat and supply cold heat into the room. On the other hand, a part of the first refrigeration or refrigeration refrigerant exiting the first refrigeration or refrigeration outdoor heat exchanger 82 branches and becomes low temperature and low pressure by the first refrigeration or refrigeration throttle means 89a. The refrigerant refrigerant heat exchanger 41a evaporates by exchanging heat with the high-temperature supercooling refrigerant flowing in the supercooling refrigeration cycle 3, passing through the first refrigeration or refrigeration refrigerant pipe 80b, The refrigeration or freezing indoor heat exchangers 87a and 87b merge with the first refrigeration or freezing refrigerant. At this time, the flow rate to the branch circuit is adjusted by the opening degree of the first refrigeration or freezing throttling means 89a.

  The second refrigeration or refrigeration refrigeration cycle 9 in which the second refrigeration or refrigeration refrigerant circulates includes a second refrigeration or refrigeration compressor 91 and a second refrigeration or refrigeration outdoor heat exchanger. 92, a second refrigeration or refrigeration receiver 94, a refrigerant refrigerant heat exchanger 51, second refrigeration or refrigeration throttle means 95a, 95b, and second refrigeration or refrigeration indoor heat. The exchangers 97 a and 97 b are connected by a second refrigeration or freezing refrigerant pipe 90.

  The second refrigeration or refrigeration refrigerant exiting the second refrigeration or refrigeration compressor 91 is supplied to the second refrigeration or refrigeration outdoor heat exchanger 92 by the second refrigeration or refrigeration outdoor heat exchanger 92. 93 radiates heat to the outdoor air by the action of the refrigerant 93, heat-exchanges with the low-temperature supercooling refrigerant flowing through the supercooling refrigeration cycle 3 in the refrigerant refrigerant heat exchanger 51 to increase the degree of supercooling, and for the second refrigeration Alternatively, the refrigerant is expanded by the refrigeration throttle means 95a and 95b to become a low-temperature and low-pressure refrigerant, and the second refrigeration or refrigeration indoor fans 96a and 96b act to the second refrigeration or refrigeration indoor heat exchangers 97a and 97b. The heat is absorbed and cold is supplied to the room.

  The supercooling refrigeration cycle 3 in which the supercooling refrigerant circulates includes a supercooling compressor 31, a supercooling outdoor heat exchanger 32, a supercooling liquid receiver 34, a refrigerant refrigerant heat exchanger 41a, The subcooling throttling means 35 and the refrigerant refrigerant heat exchanger 51 are connected by a supercooling refrigerant pipe 30.

  The supercooling refrigerant that has exited the supercooling compressor 31 radiates heat to the outdoor air by the action of the supercooling outdoor fan 33 in the supercooling outdoor heat exchanger 32, and the first refrigerant refrigerant heat exchanger 41a Heat is exchanged with the first low-temperature refrigeration or refrigeration refrigerant flowing through the refrigeration or refrigeration cycle 8 to increase the degree of supercooling, and expands in the subcooling throttling means 35 to become a low-temperature and low-pressure refrigerant. The refrigerant refrigerant heat exchanger 51 evaporates by exchanging heat with the high-temperature second refrigeration or refrigeration refrigerant flowing through the second refrigeration or refrigeration refrigeration cycle 9, and returns to the supercooling compressor 31. .

  The first refrigeration or refrigeration squeezing means 85a, 85b, 89a, the second refrigeration or refrigeration squeezing means 95a, 95b, and the supercooling squeezing means 35 are inexpensive refrigerant flow rate adjusting means such as capillaries, Alternatively, any precise flow rate control means using an electronic expansion valve may be used.

  The first refrigeration or refrigeration compressor 81, the second refrigeration or refrigeration compressor 91, and the supercooling compressor 31 may be any of various types such as reciprocating, rotary, scroll, and screw. It may be used, and may be variable in number of rotations or fixed in number.

  Further, any refrigerant may flow in the first refrigeration or refrigeration cycle 8, the second refrigeration or refrigeration cycle 9, and the supercooling refrigeration cycle 3, such as carbon dioxide, hydrocarbon, helium. , Natural refrigerants such as HFC410A, HFC407C, HFC404A, and other refrigerants that do not contain chlorine, or chlorofluorocarbon refrigerants such as R22 and R134a that are used in existing products.

  In addition, the first refrigeration or refrigeration cycle 8, the second refrigeration or refrigeration cycle 9 and the supercooling refrigeration cycle 3 are independent refrigerant circuits, and the refrigerant flowing inside The same type or different types may be used, but the refrigerant refrigerant heat exchangers 41a and 51 exchange heat with each other without mixing.

  In FIG. 15, in the first refrigeration or refrigeration outdoor heat exchanger 82, the second refrigeration or refrigeration outdoor heat exchanger 92, and the supercooling outdoor heat exchanger 32, each refrigerant is converted from air. Although the case where heat is absorbed is shown, the present invention is not limited to this, and the heat may be absorbed from water, refrigerant, brine, or the like. The first refrigeration or refrigeration outdoor blower 83, the second refrigeration or refrigeration outdoor blower 93, and the supercooling outdoor blower 33 may be a pump or the like. FIG. 15 shows a configuration example in which there are two first refrigeration or refrigeration indoor heat exchangers and two second refrigeration or refrigeration indoor heat exchangers. Alternatively, the number of units may be one, the number of units may be different, or the capacity of each indoor unit may vary from large to small, or all may have the same capacity. In addition, in the first refrigeration or refrigeration cycle 8, the second refrigeration or refrigeration cycle 9, and the supercooling refrigeration cycle 3, the case where excess refrigerant is stored by the liquid receiver is shown. It is not restricted to this, You may remove a liquid receiver as storing in the heat exchanger used as a heat radiator in a refrigerating cycle.

  In the refrigeration cycle apparatus according to the present invention, the operation of each refrigeration cycle as described above increases the degree of supercooling of the second refrigeration or refrigeration cycle 9 and increases the refrigeration effect. You can increase your ability. At this time, since the circulation amount of the second refrigeration or freezing refrigerant with respect to the same second refrigeration or freezing heat load is reduced, less power is used to circulate the second refrigeration or freezing refrigerant. I'll do it. For this reason, the COP of the second refrigeration or freezing refrigeration cycle 9 is higher than that when operating alone without performing heat exchange, thus saving energy. Further, since the pressure loss in the piping is reduced by reducing the refrigerant circulation amount, the piping size of the second refrigeration or freezing refrigeration cycle 9 can be reduced, the workability is improved, and the heat loss in the piping is reduced. Reduced and energy saving.

  In addition, the supercooling refrigeration cycle 3 can increase the degree of supercooling and increase the refrigeration capacity by heat exchange with the first refrigeration or refrigeration refrigeration cycle 8 than when there is no heat exchange. The energy is saved compared to the case where there is no heat exchange with the first refrigeration or refrigeration cycle 8.

  In addition, since the supercooling refrigeration cycle 3 is operated so that the outlets of the second refrigeration or freezing squeezing means 95a, 95b are two-phase, the evaporation temperature is usually the second refrigeration or freezing refrigeration. It becomes higher than the evaporation temperature of cycle 9. Further, as shown in FIG. 15, when the radiator is constituted by the air-cooling heat exchanger using the outside air in both the subcooling refrigeration cycle 3 and the second refrigeration cycle or the refrigeration cycle 9, the condensation temperature becomes approximately the same. The COP of the refrigeration cycle 3 is higher than the COP when the second refrigeration or refrigeration cycle is operated alone without performing heat exchange.

  Further, when the radiator is constituted by an air-cooled heat exchanger using outside air in both the first refrigeration or refrigeration cycle 8 and the second refrigeration or refrigeration cycle 9 as shown in FIG. Therefore, when the evaporating temperature of the first refrigeration or refrigeration cycle 8 is higher than that of the second refrigeration or refrigeration cycle 9, the first refrigeration or refrigeration cycle 8 The COP becomes higher than the COP when the second refrigeration or refrigeration cycle 9 is operated alone without performing heat exchange.

  Therefore, the COP of the refrigeration cycle apparatus according to the present invention is more than the COP in the case where the first refrigeration or refrigeration cycle and the second refrigeration or refrigeration cycle operate independently without performing heat exchange. Higher and energy saving.

  Even when the operation of the first refrigeration or refrigeration cycle 8 is stopped due to power-off, thermo-off, replacement to replace refrigerant or oil, or maintenance to perform equipment replacement or repair, etc. Since the degree of supercooling of the second refrigeration or freezing refrigeration cycle 9 can be increased by heat exchange with the refrigeration cycle 3 for refrigeration, the second refrigeration or freezing refrigeration cycle 9 does not perform heat exchange. In addition, both the refrigeration effect and the COP can be maintained larger than when operating alone, thereby saving energy.

Embodiment 4 FIG.
FIG. 16 shows a refrigeration cycle apparatus showing Embodiment 4 of the present invention. FIG. 16 is different from FIG. 8 in that the refrigeration cycle on the higher stage side is changed from the air-conditioning refrigeration cycle to the refrigeration or refrigeration cycle. In FIG. 16, the configuration and operation of the refrigeration cycle will be described. As shown in FIG. 16, the refrigeration cycle apparatus includes a first refrigeration or refrigeration cycle 8, a second refrigeration or refrigeration cycle 9, and a supercooling refrigeration cycle 3. The first refrigeration or freezing refrigeration cycle 8 and the second refrigeration or freezing refrigeration cycle 9 are refrigerant refrigerant heat exchangers 41a, and the second refrigeration or freezing refrigeration cycle 9 and supercooling refrigeration. The cycle 3 is a refrigerant / refrigerant heat exchanger 51, and is configured to perform heat exchange without mixing both refrigerants.

  The first refrigeration or refrigeration cycle 8 in which the first refrigeration or refrigeration refrigerant circulates includes a first refrigeration or refrigeration compressor 81, and a first refrigeration or refrigeration outdoor heat exchanger. 82, first refrigeration or refrigeration receiver 84, refrigerant refrigerant heat exchanger 41a, first refrigeration or refrigeration squeezing means 85a, 85b, and first refrigeration or refrigeration indoor heat. The exchangers 87a and 87b are connected by a first refrigeration or freezing refrigerant pipe 80.

  The first refrigeration or refrigeration refrigerant exiting the first refrigeration or refrigeration compressor 81 is used as the first refrigeration or refrigeration outdoor blower in the first refrigeration or refrigeration outdoor heat exchanger 82. 83 radiates heat to the outdoor air, expands in the first refrigeration or refrigeration throttling means 85a and 85b, and becomes a low-temperature and low-pressure refrigerant. The first refrigeration or refrigeration indoor fans 86a and 86b One refrigeration or freezing indoor heat exchangers 87a and 87b absorb heat and supply cold heat into the room. On the other hand, a part of the first refrigeration or refrigeration refrigerant exiting the first refrigeration or refrigeration outdoor heat exchanger 82 branches and becomes a low-temperature and low-pressure refrigerant by the first refrigeration or refrigeration throttle means 89a. The refrigerant refrigerant heat exchanger 41a evaporates by exchanging heat with the high-temperature second refrigeration or refrigeration refrigerant flowing through the second refrigeration or refrigeration refrigeration cycle 9, and the first refrigeration or refrigeration It merges with the first refrigeration or freezing refrigerant that has passed through the first refrigeration or freezing indoor heat exchangers 87a and 87b through the refrigerant pipe 80b. At this time, the flow rate to the branch circuit is adjusted by the opening degree of the first refrigeration or freezing throttling means 89a.

  The second refrigeration or refrigeration refrigeration cycle 9 in which the second refrigeration or refrigeration refrigerant circulates includes a second refrigeration or refrigeration compressor 91 and a second refrigeration or refrigeration outdoor heat exchanger. 92, second refrigeration or refrigeration receiver 94, refrigerant refrigerant heat exchanger 41a, refrigerant refrigerant heat exchanger 51, second refrigeration or refrigeration throttling means 95a, 95b, second Are connected by a second refrigeration or refrigeration refrigerant pipe 90 to the refrigeration or freezing indoor heat exchangers 97a and 97b.

  The second refrigeration or refrigeration refrigerant exiting the second refrigeration or refrigeration compressor 91 is supplied to the second refrigeration or refrigeration outdoor heat exchanger 92 by the second refrigeration or refrigeration outdoor heat exchanger 92. Heat is dissipated to the outdoor air by the action of 93, and is supercooled by exchanging heat with the low-temperature first refrigeration or refrigeration refrigerant flowing through the first refrigeration or refrigeration cycle 8 in the refrigerant refrigerant heat exchanger 41a. In addition, the refrigerant refrigerant heat exchanger 51 exchanges heat with the low-temperature supercooling refrigerant flowing in the supercooling refrigeration cycle 3 to increase the supercooling degree, and the second refrigeration or refrigeration throttle The refrigerant expands in the means 95a and 95b to become a low-temperature and low-pressure refrigerant, and absorbs heat in the second refrigeration or freezing indoor heat exchangers 97a and 97b by the action of the second refrigeration or freezing indoor fans 96a and 96b. To supply cold energy.

  The supercooling refrigeration cycle 3 in which the supercooling refrigerant circulates includes a supercooling compressor 31, a supercooling outdoor heat exchanger 32, a supercooling receiver 34, a supercooling throttling means 35, The refrigerant refrigerant heat exchanger 51 is connected by a supercooling refrigerant pipe 30.

  The supercooling refrigerant that has exited the supercooling compressor 31 radiates heat to the outdoor air by the action of the supercooling outdoor fan 33 in the supercooling outdoor heat exchanger 32, and expands in the supercooling throttle means 35. The refrigerant becomes a low-temperature and low-pressure refrigerant, evaporates by exchanging heat with the high-temperature second refrigeration or refrigeration refrigerant flowing in the second refrigeration or refrigeration cycle 9 in the refrigerant refrigerant heat exchanger 51, for supercooling Return to the compressor 31.

  The first refrigeration or refrigeration squeezing means 85a, 85b, 89a, the second refrigeration or refrigeration squeezing means 95a, 95b, and the supercooling squeezing means 35 are inexpensive refrigerant flow rate adjusting means such as capillaries, Alternatively, any precise flow rate control means using an electronic expansion valve may be used.

  The first refrigeration or refrigeration compressor 81, the second refrigeration or refrigeration compressor 91, and the supercooling compressor 31 may be any of various types such as reciprocating, rotary, scroll, and screw. It may be used, and may be variable in number of rotations or fixed in number.

  Further, any refrigerant may flow in the first refrigeration or refrigeration cycle 8, the second refrigeration or refrigeration cycle 9, and the supercooling refrigeration cycle 3, such as carbon dioxide, hydrocarbon, helium. , Natural refrigerants such as HFC410A, HFC407C, HFC404A, and other refrigerants that do not contain chlorine, or chlorofluorocarbon refrigerants such as R22 and R134a that are used in existing products.

  In addition, the first refrigeration or refrigeration cycle 8, the second refrigeration or refrigeration cycle 9 and the supercooling refrigeration cycle 3 are independent refrigerant circuits, and the refrigerant flowing inside The same type or different types may be used, but the refrigerant refrigerant heat exchangers 41a and 51 exchange heat with each other without mixing.

  In FIG. 16, in the first refrigeration or refrigeration outdoor heat exchanger 82, the second refrigeration or refrigeration outdoor heat exchanger 92, and the supercooling outdoor heat exchanger 32, each refrigerant is converted from air. Although the case where heat is absorbed is shown, the present invention is not limited to this, and the heat may be absorbed from water, refrigerant, brine, or the like. The first refrigeration or refrigeration outdoor blower 83, the second refrigeration or refrigeration outdoor blower 93, and the supercooling outdoor blower 33 may be a pump or the like. FIG. 16 shows a configuration example in which there are two first refrigeration or refrigeration indoor heat exchangers and two second refrigeration or refrigeration indoor heat exchangers. Alternatively, the number of units may be one, the number of units may be different, or the capacity of each indoor unit may vary from large to small, or all may have the same capacity. In addition, in the first refrigeration or refrigeration cycle 8, the second refrigeration or refrigeration cycle 9, and the supercooling refrigeration cycle 3, the case where excess refrigerant is stored by the liquid receiver is shown. It is not restricted to this, You may remove a liquid receiver as storing in the heat exchanger used as a heat radiator in a refrigerating cycle.

  In the refrigeration cycle apparatus according to the present invention, the operation of each refrigeration cycle as described above increases the degree of supercooling of the second refrigeration or refrigeration cycle 9 and increases the refrigeration effect. You can increase your ability. At this time, since the circulation amount of the second refrigeration or freezing refrigerant with respect to the same second refrigeration or freezing heat load is reduced, less power is used to circulate the second refrigeration or freezing refrigerant. I'll do it. For this reason, the COP of the second refrigeration or freezing refrigeration cycle 9 is higher than that when operating alone without performing heat exchange, thus saving energy. Further, since the pressure loss in the piping is reduced by reducing the refrigerant circulation amount, the piping size of the second refrigeration or freezing refrigeration cycle 9 can be reduced, and workability is improved. In addition, the pipe size can be reduced, the workability is improved, and heat loss in the pipe is reduced, resulting in energy saving.

  In addition, since the supercooling refrigeration cycle 3 is operated so that the outlets of the second refrigeration or freezing squeezing means 95a, 95b are two-phase, the evaporation temperature is usually the second refrigeration or freezing refrigeration. It becomes higher than the evaporation temperature of cycle 9. Further, as shown in FIG. 16, when the radiator is constituted by the air-cooled heat exchanger using the outside air in both the subcooling refrigeration cycle 3 and the second refrigeration cycle or the refrigeration cycle 9, the condensation temperature becomes approximately the same. The COP of the refrigerating cycle 3 is higher than the COP when the second refrigeration or refrigerating cycle is operated alone without heat exchange.

  In addition, when the radiator is constituted by an air-cooled heat exchanger using outside air in both the first refrigeration or refrigeration cycle 8 and the second refrigeration or refrigeration cycle 9 as shown in FIG. Therefore, when the evaporating temperature of the first refrigeration or refrigeration cycle 8 is higher than that of the second refrigeration or refrigeration cycle 9, the first refrigeration or refrigeration cycle 8 The COP becomes higher than the COP when the second refrigeration or refrigeration cycle 9 is operated alone without performing heat exchange.

  Therefore, the COP of the refrigeration cycle apparatus according to the present invention is more than the COP in the case where the first refrigeration or refrigeration cycle and the second refrigeration or refrigeration cycle operate independently without performing heat exchange. Higher and energy saving.

  Even when the operation of the first refrigeration or refrigeration cycle 8 is stopped due to power-off, thermo-off, replacement to replace refrigerant or oil, or maintenance to perform equipment replacement or repair, etc. Since the degree of supercooling of the second refrigeration or freezing refrigeration cycle 9 can be increased by heat exchange with the refrigeration cycle 3 for refrigeration, the second refrigeration or freezing refrigeration cycle 9 does not perform heat exchange. In addition, both the refrigeration effect and the COP can be maintained larger than when operating alone, thereby saving energy.

  In FIG. 16, the refrigerant / refrigerant heat exchanger 41a is arranged on the upstream side of the refrigerant / refrigerant heat exchanger 51, but the same effect can be expected even if arranged on the downstream side. Further, as shown in the second embodiment, energy can be reliably realized by disposing a refrigerant refrigerant heat exchanger that performs heat exchange with a refrigerant having a lower evaporation temperature downstream.

Embodiment 5 FIG.
FIG. 17 shows a refrigeration cycle apparatus showing Embodiment 5 of the present invention. The subcooling refrigeration cycle casing 300 shows a part that houses each device in the region surrounded by a two-dot chain line in FIG. 17 in the same casing. By configuring the supercooling refrigeration cycle housing 300 in this manner, the refrigeration cycle apparatus according to the present invention can be configured using the general-purpose air-conditioning refrigeration cycle 1 and the general-purpose refrigeration or refrigeration cycle 9. It is possible to suppress development investment for a dedicated air-conditioning refrigeration cycle, refrigeration or refrigeration refrigeration cycle, and the existing refrigeration cycle and refrigeration or refrigeration cycle constitute the refrigeration cycle apparatus according to the present invention. Can save energy.

Embodiment 6 FIG.
FIG. 18 shows a refrigeration cycle apparatus showing Embodiment 6 of the present invention. The supercooling refrigeration cycle housing 300 shows a portion in which each device in the region surrounded by a two-dot chain line in FIG. 18 is housed in the same housing. By configuring the supercooling refrigeration cycle housing 300 in this manner, the refrigeration cycle apparatus according to the present invention can be configured using the general-purpose air-conditioning refrigeration cycle 1 and the general-purpose refrigeration or refrigeration cycle 9. It is possible to suppress development investment for a dedicated air-conditioning refrigeration cycle, refrigeration or refrigeration refrigeration cycle, and the existing refrigeration cycle and refrigeration or refrigeration cycle constitute the refrigeration cycle apparatus according to the present invention. Can save energy.

1 is a refrigerant circuit diagram of a refrigeration cycle apparatus showing a first embodiment. It is a Ph diagram which shows operation | movement of the refrigeration air conditioning apparatus which concerns on Embodiment 1. FIG. FIG. 4 is a refrigerant circuit diagram of another refrigeration cycle apparatus showing the first embodiment. FIG. 4 is a refrigerant circuit diagram of another refrigeration cycle apparatus showing the first embodiment. FIG. 4 is a refrigerant circuit diagram of another refrigeration cycle apparatus showing the first embodiment. FIG. 4 is a refrigerant circuit diagram of another refrigeration cycle apparatus showing the first embodiment. FIG. 4 is a refrigerant circuit diagram of another refrigeration cycle apparatus showing the first embodiment. 6 is a refrigerant circuit diagram of a refrigeration cycle apparatus showing Embodiment 2. FIG. It is a Ph diagram which shows operation | movement of the refrigeration air conditioning apparatus which concerns on Embodiment 2. FIG. FIG. 6 is a refrigerant circuit diagram of another refrigeration cycle apparatus showing Embodiment 2. FIG. 6 is a refrigerant circuit diagram of another refrigeration cycle apparatus showing Embodiment 2. FIG. 6 is a refrigerant circuit diagram of another refrigeration cycle apparatus showing Embodiment 2. FIG. 6 is a refrigerant circuit diagram of another refrigeration cycle apparatus showing Embodiment 2. FIG. 6 is a refrigerant circuit diagram of another refrigeration cycle apparatus showing Embodiment 2. FIG. 6 is a refrigerant circuit diagram of a refrigeration cycle apparatus showing a third embodiment. 6 is a refrigerant circuit diagram of a refrigeration cycle apparatus showing a fourth embodiment. FIG. FIG. 10 is a refrigerant circuit diagram of a refrigeration cycle apparatus showing a fifth embodiment. FIG. 10 is a refrigerant circuit diagram of a refrigeration cycle apparatus showing a sixth embodiment.

Explanation of symbols

  1 Refrigeration cycle for air conditioning, 2 refrigeration cycle for refrigeration or refrigeration, 3 refrigeration cycle for supercooling, 8 refrigeration cycle for first refrigeration or freezing, 9 refrigeration cycle for second refrigeration or freezing, 10 refrigerant for air conditioning Piping, 10a Air conditioning refrigerant piping, 10b Air conditioning refrigerant piping, 10c Air conditioning refrigerant piping, 10d Air conditioning refrigerant piping, 11 Air conditioning compressor, 12 Air conditioning outdoor heat exchanger, 13 Air conditioning outdoor fan, 14 Air conditioning receiver Liquid unit, 15a Air-conditioning throttle means, 15b Air-conditioning throttle means, 15c Air-conditioning throttle means, 16a Air-conditioning indoor fan, 16b Air-conditioning indoor fan, 17a Air-conditioning indoor heat exchanger, 17b Air-conditioning indoor heat exchanger, 18 Air-conditioning four-way valve, 19a Air-conditioning throttling means 19b Air-conditioning throttling means, 19c Air-conditioning throttling means, 19d Air-conditioning throttling means, 19e Empty Squeezing means, 20 refrigeration or refrigeration refrigerant piping, 20a refrigeration or refrigeration refrigerant piping, 21 refrigeration or refrigeration compressor, 22 refrigeration or refrigeration outdoor heat exchanger, 23 refrigeration or refrigeration outdoor blower 24 Refrigeration or refrigeration receiver, 25a Refrigeration or refrigeration throttle means, 25b Refrigeration or refrigeration throttle means, 26a Refrigeration or refrigeration indoor fan, 26b Refrigeration or refrigeration indoor fan, 27a Or refrigeration indoor heat exchanger, 27b refrigeration or refrigeration indoor heat exchanger, 29a refrigeration or refrigeration throttling means, 29b refrigeration or refrigeration throttling means, 30 supercooling refrigerant piping, 30a supercooling refrigerant piping 31 Supercooling compressor 32 Supercooling outdoor heat exchanger 33 Supercooling outdoor fan 34 Supercooling receiver 35 Supercooling Throttle means 39a supercooling throttle means 39b supercooling throttle means 41a refrigerant refrigerant heat exchanger 41b refrigerant refrigerant heat exchanger 51 refrigerant refrigerant heat exchanger 80 first refrigerant refrigerant pipe for refrigeration or refrigeration 80a First refrigeration or refrigeration refrigerant piping, 80b First refrigeration or refrigeration refrigerant piping, 81 First refrigeration or refrigeration compressor, 82 First refrigeration or refrigeration outdoor heat exchanger 83 First refrigeration or refrigeration outdoor fan, 84 First refrigeration or refrigeration receiver, 85a First refrigeration or refrigeration squeezing means, 85b First refrigeration or refrigeration squeezing means, 86a First refrigeration or freezing indoor blower, 86b First refrigeration or freezing indoor blower, 87a First refrigeration or freezing indoor heat exchanger, 87b First refrigeration or freezing room Heat exchanger, 89a first refrigeration or refrigeration throttling means, 90 second refrigeration or refrigeration refrigerant piping, 90a second refrigeration or refrigeration refrigerant piping, 90b second refrigeration or refrigeration refrigerant Piping, 91 Second refrigeration or refrigeration compressor, 92 Second refrigeration or refrigeration outdoor heat exchanger, 93 Second refrigeration or refrigeration outdoor fan, 94 Second refrigeration or refrigeration receiver 95a Second refrigeration or freezing squeezing means, 95b Second refrigeration or freezing squeezing means, 96a Second refrigeration or freezing indoor blower, 96b Second refrigeration or freezing indoor blower 97a Second refrigeration or refrigeration indoor heat exchanger, 97b Second refrigeration or refrigeration indoor heat exchanger, 99a Second refrigeration or refrigeration throttle means, 300 Supercooling refrigeration cycle housing , 601 connection valve, 602 connection valve, 603 connection valve, 604 connection valve, 605 connection valve, 606 connection valve, 607 connection valve, 608 connection valve, 609 connection valve, 610 connection valve , 611 connection valve, 612 connection valve.

Claims (15)

The first refrigerant circulates, the first compressor, the four-way valve, the outdoor heat exchanger for air conditioning, the indoor heat exchanger for air conditioning, the outdoor heat exchanger for air conditioning, and the indoor heat exchanger for air conditioning. A first refrigeration cycle having a plurality of first air conditioning throttle means disposed between the first refrigerant and the first refrigerant so as to flow in series.
A second refrigeration cycle in which the second refrigerant circulates, and has a second compressor, an outdoor cooling heat exchanger for cooling articles, a throttle means for cooling the cooling articles, and an indoor heat exchanger for cooling the cooling articles,
A third refrigerant that circulates, a third compressor, a subcooling outdoor heat exchanger, a first refrigerant refrigerant heat exchanger that exchanges heat between the first refrigerant and the third refrigerant; A third refrigeration cycle having a first supercooling throttle means, and a second refrigerant refrigerant heat exchanger that exchanges heat between the second refrigerant and the third refrigerant,
One end connected to the flow path between the first refrigeration cycle plurality provided said first air conditioning throttle hand stage, the outdoor heat exchanger for the air conditioner and the other end the first air conditioning throttle means A bypass circuit having a second air conditioning throttle means connected to the air conditioner,
The first refrigerant / refrigerant heat exchanger is connected to the air-conditioning outdoor heat exchanger side from the second air-conditioning throttling means of the bypass circuit and the outlet side of the subcooling outdoor heat exchanger and the Connected between the inlet side of the first subcooling throttle means,
The second refrigerant / refrigerant heat exchanger is connected between an outlet side of the article cooling outdoor heat exchanger and an inlet side of the article cooling throttle means, and A refrigeration cycle apparatus connected between an outlet side and an inlet side of the third compressor.   A second subcooling throttle means provided between the third compressor and the subcooling outdoor heat exchanger; and between the third compressor and the second subcooling throttle means. And between the subcooling outdoor heat exchanger and the first refrigerant refrigerant heat exchanger, and a pipe arranged to bypass the subcooling outdoor heat exchanger, and the pipe The refrigeration cycle apparatus according to claim 1, further comprising a third subcooling throttle means provided. The first refrigerant circulates, the first compressor, the four-way valve, the outdoor heat exchanger for air conditioning, the indoor heat exchanger for air conditioning, the outdoor heat exchanger for air conditioning, and the indoor heat exchanger for air conditioning. A first refrigeration cycle having a plurality of first air conditioning throttle means disposed between the first refrigerant and the first refrigerant so as to flow in series.
A second refrigerant circulating, a second compressor, an article cooling outdoor heat exchanger, a first refrigerant refrigerant heat exchanger in which the first refrigerant and the second refrigerant exchange heat. A second refrigeration cycle having a first article cooling squeezing means and an article cooling indoor heat exchanger;
The third refrigerant circulates, and the third compressor, the subcooling outdoor heat exchanger, the first subcooling throttle means, the second refrigerant, and the third refrigerant exchange heat. A second refrigerant refrigerant heat exchanger to perform, a third refrigeration cycle having,
One end connected to the flow path between the first refrigeration cycle plurality provided said first air conditioning throttle hand stage, the outdoor heat exchanger for the air conditioner and the other end the first air conditioning throttle means A bypass circuit having a second air conditioning throttle means connected to the air conditioner,
The first refrigerant / refrigerant heat exchanger is connected to the air-conditioning outdoor heat exchanger side from the second air-conditioning throttle means of the bypass circuit and the article cooling outdoor heat exchanger and the first The second refrigerant refrigerant heat exchanger is connected between the outlet side of the article cooling outdoor heat exchanger and the inlet side of the first article cooling throttle means. is connected, the refrigeration cycle apparatus characterized by being connected between the entrance side of the exit side of the third compressor of the first supercooling throttle means.   The refrigeration cycle apparatus according to claim 3, wherein the second refrigerant refrigerant heat exchanger is connected to a downstream side of the first refrigerant refrigerant heat exchanger.   Between the second compressor and the second article cooling squeezing means provided between the second compressor and the article cooling outdoor heat exchanger, and between the second compressor and the second article cooling squeezing means. Between the outdoor cooling heat exchanger for cooling the article and the first refrigerant refrigerant heat exchanger, and a pipe disposed so as to bypass the outdoor cooling heat exchanger for cooling the article. The refrigeration cycle apparatus according to claim 3, further comprising a third article cooling squeezing unit provided.   The second air conditioning throttle means is provided, and the second air conditioning throttle means is connected so that the refrigerant flows in parallel with the first air conditioning throttle means. The refrigeration cycle apparatus according to any one of the above. Third air conditioning throttle means connected to the air conditioning outdoor heat exchanger side from the second air conditioning throttle means of the bypass circuit, and the second air conditioning one end of the bypass circuit A pipe connected between the throttle means and the third air conditioning throttle means, the other end connected between the four-way valve and the air conditioning indoor heat exchanger, and a fourth provided in the pipe. The refrigeration cycle apparatus according to any one of claims 1 to 6, further comprising an air conditioning throttle means. The first refrigerant circulates, and includes a first compressor, a first article cooling outdoor heat exchanger, a first article cooling throttle means, and a first article cooling indoor heat exchanger. A first refrigeration cycle having
A second refrigerant circulates, and a second compressor, a second article cooling outdoor heat exchanger, a second article cooling throttle means, and a second article cooling indoor heat exchanger, A second refrigeration cycle having;
A third refrigerant that circulates, a third compressor, a subcooling outdoor heat exchanger, a first refrigerant refrigerant heat exchanger that exchanges heat between the first refrigerant and the third refrigerant; A third refrigeration cycle having supercooling throttle means, and a second refrigerant refrigerant heat exchanger that exchanges heat between the second refrigerant and the third refrigerant,
One end is connected to the flow path between the outlet side of the first article cooling outdoor heat exchanger and the inlet side of the first article cooling throttle means, and the other end is the first article cooling chamber. A detour circuit connected between the outlet side of the heat exchanger and the inlet side of the first compressor and having a third article cooling throttling means,
The first refrigerant / refrigerant heat exchanger is connected downstream of the third article cooling squeezing means in the bypass circuit, and the outlet side of the supercooling outdoor heat exchanger and the supercooling squeezing means. Connected to the entrance side of
The second refrigerant / refrigerant heat exchanger is connected between the outlet side of the second article cooling outdoor heat exchanger and the inlet side of the second article cooling throttle means, and is used for the supercooling. A refrigeration cycle apparatus connected between the outlet side of the throttle means and the inlet side of the third compressor. The first refrigerant circulates, the first compressor, the four-way valve, the outdoor heat exchanger for air conditioning, the indoor heat exchanger for air conditioning, the outdoor heat exchanger for air conditioning, and the indoor heat exchanger for air conditioning. A first refrigeration cycle having a plurality of first air conditioning throttle means disposed between the first refrigerant and the first refrigerant so as to flow in series.
A second refrigeration cycle in which the second refrigerant circulates, and has a second compressor, an outdoor cooling heat exchanger for cooling articles, a throttle means for cooling the cooling articles, and an indoor heat exchanger for cooling the cooling articles,
A third refrigerant that circulates, a third compressor, a subcooling outdoor heat exchanger, a first refrigerant refrigerant heat exchanger that exchanges heat between the first refrigerant and the third refrigerant; A third refrigeration cycle having a first supercooling throttle means, and a second refrigerant refrigerant heat exchanger that exchanges heat between the second refrigerant and the third refrigerant,
The first refrigerant / refrigerant heat exchanger is connected to a flow path between the first air-conditioning throttle means provided in the first refrigeration cycle, and is connected to the subcooling outdoor heat exchanger. Connected to the inlet side of the first supercooling throttle means,
The second refrigerant / refrigerant heat exchanger is connected between an outlet side of the article cooling outdoor heat exchanger and an inlet side of the article cooling throttle means, and A refrigeration cycle apparatus connected between an outlet side and an inlet side of the third compressor . A plurality of first air conditioning throttle means provided between the first air conditioning throttle means and the air conditioning outdoor heat exchanger provided in the first refrigeration cycle; and the first air conditioning throttle. And the third air-conditioning throttle means, and the first compressor and the air-conditioning outdoor heat exchanger are connected so as to bypass the air-conditioning outdoor heat exchanger. The refrigeration cycle apparatus according to claim 1, 2 or 9, further comprising: a pipe to be provided; and a fourth air conditioning throttle means provided in the pipe . The first refrigeration cycle has information indicating an operation state of the first refrigeration cycle, and includes first control means having first communication means,
The third refrigeration cycle includes second control means having second communication means for communicating with the first control means,
The first control means transmits information indicating an operating state of the first refrigeration cycle to the second control means via the first communication means, and the second control means The refrigeration according to any one of claims 1 to 10, wherein an operation of the third refrigeration cycle is controlled based on information received from the first control means via a second communication means. Cycle equipment. The first refrigeration cycle has information indicating an operation state of the first refrigeration cycle, and includes first control means having first communication means,
The second refrigeration cycle includes second control means having second communication means for communicating with the first control means,
The first control means transmits information indicating an operating state of the first refrigeration cycle to the second control means via the first communication means, and the second control means The operation of the second refrigeration cycle is controlled based on information received from the first control means via two communication means. The refrigeration according to any one of claims 1 to 10, Cycle equipment. First temperature detection means for detecting the outside air temperature, and second temperature detection means for detecting the temperature of the first refrigerant flowing through the first refrigerant refrigerant heat exchanger,
The first control means for controlling the operation of the third refrigeration cycle is configured to operate the first refrigeration cycle based on the output of the first temperature detection means and the output of the second temperature detection means. The refrigeration cycle apparatus according to any one of claims 1 to 10, wherein the state is estimated. First temperature detection means for detecting the outside air temperature, and second temperature detection means for detecting the temperature of the first refrigerant flowing through the first refrigerant refrigerant heat exchanger,
The first control means for controlling the operation of the second refrigeration cycle is configured to operate the first refrigeration cycle based on the output of the first temperature detection means and the output of the second temperature detection means. The refrigeration cycle apparatus according to any one of claims 1 to 10, wherein the state is estimated.   The third refrigeration cycle, the first refrigerant refrigerant heat exchanger, and the second refrigerant refrigerant heat exchanger are housed in the same casing. The refrigeration cycle apparatus according to any one of the above.

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