JP2020012610A - Air conditioner - Google Patents

Abstract

To provide an air conditioner which can enhance a cooling capacity, and be suppressed in enlargement of a physique, complication or cost increase.SOLUTION: An ebullition cooling type air conditioner 1 comprises a plurality of cycles 10, 20. An outdoor blower 30 sequentially sends atmospheric air to a plurality of condensers 12, 22 possessed by the plurality of cycles 10, 20. An indoor blower 40 sequentially sends indoor air to a plurality of evaporators 11, 21 possessed by the plurality of cycles 10, 20. The first cycle 10 of the plurality of cycles is arranged at a side at which a temperature difference between the atmospheric air supplied to the condensers 12, 22 and the indoor air supplied to the evaporators 11, 21 becomes large as compared with the second cycle 20. Then, the first cycle 10 is constituted so that pressure losses of refrigerants circulating in the cycles become small when heat moving amounts between the evaporators 11, 21 and the condensers 12, 22 are set to the same condition as compared with the second cycle 20.SELECTED DRAWING: Figure 1

Description

  The present invention relates to a boiling cooling type air conditioner.

  2. Description of the Related Art A boil-cooling type air conditioner that cools a room in which a DC / AC exchange device and communication devices are stored has been known.

  The boiling cooling type air conditioner described in Patent Document 1 uses a plurality of sets of boiling cooling cycles. The boiling cooling cycle includes an evaporator in which a refrigerant evaporates by heat exchange with room air, a condenser in which the refrigerant evaporated in the evaporator condenses by heat exchange with the outside air, and a gas connecting the evaporator and the condenser. It is a closed circuit that has a pipe and a liquid pipe and in which the refrigerant circulates naturally. The indoor air is blown to the evaporator by an indoor blower, and the outside air is blown to the condenser by an outdoor blower. The boiling cooling cycle is also called a loop type thermosiphon.

  This air conditioner is equipped with a sound insulation plate in the air passage to prevent the noise of the outdoor blower from increasing when the rotation speed of the outdoor blower is increased to increase the amount of air blown to the condenser in order to increase the indoor cooling capacity. Is arranged.

JP-A-2006-96354

  However, the air conditioner described in Patent Literature 1 does not mention the optimal specifications of the boiling cooling cycle for the airflow of the outdoor blower and the indoor blower.

  Generally, in the boiling cooling cycle, the cooling capacity increases as the temperature difference between the outside air supplied to the condenser and the room air supplied to the evaporator increases. However, when the temperature difference becomes larger than a predetermined value, a so-called cooling capacity peaking phenomenon occurs in which the rate of increase of the cooling capacity with respect to the temperature difference decreases. This is because, if the volumetric flow rate of the refrigerant circulating in the boiling cooling cycle becomes larger than a predetermined flow rate, the pressure loss of the refrigerant circulating in the cycle increases, and sufficient cooling performance cannot be exhibited.

  Therefore, in an air conditioner using a plurality of boiling cooling cycles as described in Patent Literature 1, the number of rotations of the outdoor blower is increased, and the flow path of a member constituting the flow path in all boiling cooling cycles. It is conceivable to increase the area. However, in such a case, it is necessary to ensure the pressure resistance of the members constituting the flow path in all boiling and cooling cycles. Therefore, the physique becomes large, the configuration becomes complicated, and the cost increases as the whole air conditioner.

  SUMMARY OF THE INVENTION In view of the above, an object of the present invention is to provide an air conditioner capable of increasing cooling capacity and suppressing an increase in size, complexity, or cost.

In order to achieve the above object, the invention according to claim 1 is:
In boiling cooling type air conditioners,
Evaporators (11, 21) for evaporating the refrigerant, condensers (12, 22) for condensing the refrigerant evaporated in the evaporator, gas pipes (13, 23) for flowing the refrigerant evaporated in the evaporator to the condenser, and A plurality of boiling cooling cycles (10, 20) each having a liquid pipe (14, 24) through which the refrigerant condensed by the condenser flows to the evaporator, and constituting a closed circuit in which the refrigerant circulates naturally;
An outdoor blower (30) for sequentially blowing outside air to a plurality of condensers of the plurality of boiling cooling cycles, respectively;
An indoor blower (40) for sequentially blowing indoor air to a plurality of evaporators each of the plurality of boiling cooling cycles,
Among the plurality of boiling cooling cycles, the predetermined boiling cooling cycle (10) is different from the other boiling cooling cycles (20) in the temperature difference between the outside air supplied to the condenser and the room air supplied to the evaporator. Is installed on the side where
The predetermined boiling cooling cycle is configured such that the pressure loss of the refrigerant circulating through the cycle is smaller when the heat transfer amount between the evaporator and the condenser is the same as that of the other boiling cooling cycles. Have been.

  In the following description, a boiling cooling cycle is simply referred to as a “cycle”, a predetermined boiling cooling cycle is referred to as a “first cycle”, and other boiling cooling cycles are referred to as a “second cycle”. The temperature difference between the outside air supplied to the condenser and the room air supplied to the evaporator is simply referred to as “temperature difference”.

  In the invention according to claim 1, instead of reducing the pressure loss of the refrigerant circulating in all the cycles provided in the air conditioner, the pressure loss of the refrigerant circulating in the first cycle installed on the side where the temperature difference increases. Is smaller. Thereby, even if the temperature difference becomes large in the first cycle, a decrease in the rate of increase in the cooling capacity with respect to the temperature difference is prevented. Then, in the second cycle, an increase in size, complexity, or cost increase of the physique is suppressed. Therefore, this air conditioner can increase the cooling capacity and suppress an increase in size, complexity, or cost.

  In addition, the reference numerals in parentheses attached to the respective components and the like indicate an example of a correspondence relationship between the components and the like and specific components and the like described in the embodiments described later.

It is a lineblock diagram of an air conditioner concerning a 1st embodiment. FIG. 2 is an enlarged sectional view of a portion II in FIG. 1. FIG. 3 is an enlarged sectional view of a portion III in FIG. 1. It is explanatory drawing which showed an example of the temperature of the air supplied to the condenser with which the air conditioner of 1st Embodiment is provided, and the temperature of the air supplied to an evaporator. It is explanatory drawing which showed an example of the temperature of the air supplied to the condenser with which the air conditioner of a reference example is provided, and the temperature of the air supplied to an evaporator. 5 is a graph showing a relationship between a temperature difference between air supplied to a condenser and an evaporator and a cooling capacity. It is a perspective view showing a part of evaporator with which an air conditioner of a 3rd embodiment is provided. It is a lineblock diagram of an air conditioner concerning a 4th embodiment. It is a lineblock diagram of an air conditioner concerning a 5th embodiment.

  Hereinafter, embodiments of the present invention will be described with reference to the drawings. In the following embodiments, the same or equivalent parts are denoted by the same reference numerals and description thereof will be omitted.

(1st Embodiment)
The first embodiment will be described with reference to the drawings. As shown in FIG. 1, the air conditioner 1 of the first embodiment is, for example, a boiling-cooling type air conditioner 1 that cools a room of a base station in which a DC / AC exchange device or a communication device (not shown) is stored. . The air conditioner 1 is a device for radiating exhaust heat generated from a DC / AC exchange device or a communication device to the outside air. In FIG. 1, the indoor space to be cooled by the air conditioner 1 is indicated by a dashed line denoted by reference numeral 2.

  The air conditioner 1 includes a plurality of boiling / cooling cycles 10, 20, an outdoor blower 30, and an indoor blower 40. In the following description, the boiling cooling cycles 10 and 20 are simply referred to as “cycles 10 and 20”.

  In the description of the first embodiment, of the plurality of cycles 10 and 20, one in which the condenser 12 is disposed on the upstream side where the outdoor blower 30 blows outside air is referred to as a first cycle 10, and the outdoor blower 30 discharges outside air. One in which the condenser 22 is disposed on the downstream side of the blower is referred to as a second cycle 20. The first cycle 10 corresponds to a “predetermined boiling cooling cycle” described in the claims, and the second cycle 20 corresponds to “another boiling cooling cycle”.

  Hereinafter, the configuration of the first cycle 10 will be described.

  The first cycle 10 has an evaporator 11, a condenser 12, a gas pipe 13, and a liquid pipe 14. The evaporator 11, the condenser 12, the gas pipe 13 and the liquid pipe 14 are connected in a ring shape to form a closed circuit in which the refrigerant naturally circulates. The first cycle 10 is filled with a predetermined amount of refrigerant. A refrigerant that changes its phase so as to evaporate at room temperature and condense at outside temperature is employed. In the first embodiment, for example, a chlorofluorocarbon-based refrigerant is employed as the refrigerant.

  The evaporator 11 is a heat exchanger for exchanging heat between the refrigerant flowing inside and the indoor air blown by the indoor blower 40. The evaporator 11 includes a plurality of tubes 111 having a flow path through which a refrigerant flows, and header tanks 112 and 113 connected to both ends of the plurality of tubes 111, respectively. The gas pipe 13 is connected to the upper header tank 112 of the evaporator 11 via a connector 114, and the liquid pipe 14 is connected to the lower header tank 113 of the evaporator 11 via a connector 115.

  The condenser 12 is a heat exchanger for exchanging heat between the refrigerant flowing inside and the outside air blown by the outdoor blower 30. The condenser 12 also includes a plurality of tubes 121 having a flow path through which the refrigerant flows, and header tanks 122 and 123 connected to both ends of the plurality of tubes 121, respectively. The gas pipe 13 is connected to the upper header tank 122 of the condenser 12 via a connector 124, and the liquid pipe 14 is connected to the lower header tank 123 of the condenser 12 via a connector 125.

  The liquid-phase refrigerant flowing inside the evaporator 11 absorbs heat from indoor air blown by the indoor blower 40 and evaporates (boils). On the other hand, the room air radiates heat to the liquid-phase refrigerant flowing inside the evaporator 11 and is cooled. The vapor-phase refrigerant evaporated in the evaporator 11 flows to the condenser 12 via the gas pipe 13.

  The gas-phase refrigerant flowing inside the condenser 12 radiates heat to the outside air blown by the outdoor blower 30 and condenses. On the other hand, the outside air passing through the condenser 12 is heated by absorbing heat from the gas-phase refrigerant flowing inside the condenser 12. The liquid refrigerant condensed in the condenser 12 flows to the evaporator 11 via the liquid pipe 14 by its own weight.

  The configurations of the evaporator 21, the condenser 22, the gas pipe 23, the liquid pipe 24, and the like included in the second cycle 20 are basically the same as the configuration of the above-described first cycle 10, and a description thereof will be omitted. The plurality of cycles 10 and 20 included in the air conditioner 1 can perform indoor cooling by radiating heat in the indoor space to the outside air by natural circulation of the phase-changing refrigerant.

  The outdoor blower 30 sequentially blows outside air to the plurality of condensers 12 and 22 included in the plurality of cycles 10 and 20, respectively. The outdoor blower 30 blows outside air in the order of the condenser 12 included in the first cycle 10 and the condenser 22 included in the second cycle 20. That is, the condenser 12 of the first cycle 10 is arranged on the upstream side in the flow direction of the outside air blown by the outdoor blower 30, and the condenser 22 of the second cycle 20 is arranged on the downstream side.

  On the other hand, the indoor blower 40 blows indoor air to the plurality of evaporators 11 and 21 included in the plurality of cycles 10 and 20, respectively. The indoor blower 40 blows outside air in the order of the evaporator 21 of the second cycle 20 and the evaporator 11 of the first cycle 10. That is, the evaporator 21 of the second cycle 20 is arranged on the upstream side in the flow direction of the indoor air blown by the indoor blower 40, and the evaporator 11 of the first cycle 10 is arranged on the downstream side.

In the first embodiment, the amount of air that passes through the condensers 12 and 22 by the blower of the outdoor blower 30 (hereinafter, referred to as “the blower amount B _OUT of the indoor blower 40”) causes the evaporators 11 and 21 to blow through the indoor blower 40. It is configured to be smaller than the amount of air passing therethrough (hereinafter, referred to as “air blown amount B _IN of indoor blower 40”). This is because, for example, the rotation speed of the outdoor blower 30 may be restricted by the external environment in which the base station is installed.

Here, due to the difference between the blown air amount B _OUT of the indoor blower 40 and the blown air amount B _IN of the indoor blower 40, the temperature difference between the outside air supplied to the condensers 12 and 22 and the indoor air supplied to the evaporators 11 and 21. Is changed between the first cycle 10 and the second cycle 20. In the following description, the temperature difference between the outside air supplied to the condensers 12 and 22 and the room air supplied to the evaporators 11 and 21 is simply referred to as “temperature difference”.

FIG. 5 shows an air conditioner 3 of a reference example. This reference example is based on the assumption that the blower amount B _OUT of the indoor blower 40 and the blower amount B _IN of the indoor blower 40 are the same, and the temperatures T _OUT1 and T _{OUT2 of the} outside air supplied to the condensers 12 and 22 and the evaporator. The temperatures T _IN1 and T _IN2 of the room air supplied to 11, 11 are calculated. In this reference example, any blowing amount _{B IN} of air volume _{B OUT} and the indoor fan 40 of the outdoor blower 30, and 2400 m ³ / h. The temperature T _OUT1 of the outside air is 0 ° C., and the temperature T _{IN1 of the} room air is 40 ° C.

In the case of this reference example, the temperature T _OUT1 of the outside air supplied to the condenser 12 of the first cycle 10 is 0 ° C., and after passing through the condenser 12 of the first cycle 10, the condenser 22 of the second cycle 20 temperature _{T OUT2} of the outside air supplied to the is 10.3 ° C.. On the other hand, the temperature T _{IN1 of the} room air supplied to the evaporator 21 in the second cycle 20 is 40 ° C., and after passing through the evaporator 21 in the second cycle 20, the temperature T _IN1 is supplied to the evaporator 11 in the first cycle 10. The indoor air temperature T _IN2 is 27.4 ° C. Therefore, the temperature difference in the first cycle 10 is Δ27.4 ° C., and the temperature difference in the second cycle 20 is Δ29.7 ° C. Therefore, it can be seen that the temperature difference in the first cycle 10 and the temperature difference in the second cycle 20 are similar.

On the other hand, FIG. 4 shows an example of the first embodiment in which the condensers 12 and 22 are configured such that the blower amount B _OUT of the indoor blower 40 is smaller than the blown amount B _IN of the indoor blower 40. The temperatures T _OUT1 and T _{OUT2 of the} supplied outside air and the temperatures T _IN1 and T _IN2 of the room air supplied to the evaporators 11 and 21 are calculated. In this example, the air volume B _OUT of the indoor blower 40 is 1200 m ³ / h, and the air volume B _IN of the indoor fan 40 is 2400 m ³ / h. The temperature T _OUT1 of the outside air is 0 ° C., and the temperature T _{IN1 of the} room air is 40 ° C.

In this example, the temperature T _OUT1 of the outside air supplied to the condenser 12 in the first cycle 10 is 0 ° C., and after passing through the condenser 12 in the first cycle 10, the temperature T _OUT1 is supplied to the condenser 22 in the second cycle 20. The temperature T _OUT2 of the supplied outside air is 17.5 ° C. On the other hand, the temperature T _{IN1 of the} room air supplied to the evaporator 21 in the second cycle 20 is 40 ° C., and after passing through the evaporator 21 in the second cycle 20, the temperature T _IN1 is supplied to the evaporator 11 in the first cycle 10. The indoor air temperature T _IN2 is 33.7 ° C. Therefore, the temperature difference in the first cycle 10 is Δ33.7 ° C., and the temperature difference in the second cycle 20 is Δ22.5 ° C. Therefore, as in the first embodiment, when the blower amount B _OUT of the indoor blower 40 is configured to be smaller than the blower amount B _IN of the indoor blower 40, the temperature difference in the first cycle 10 is reduced in the second cycle 20. It turns out that it becomes larger than the temperature difference in.

  By the way, in the cycle in which the refrigerant circulates, as the temperature difference increases, the cooling capacity increases. However, when the temperature difference becomes larger than a predetermined value, a so-called cooling capacity peaking phenomenon occurs in which the rate of increase of the cooling capacity with respect to the temperature difference decreases. This is because, when the volume flow rate of the refrigerant circulating in the cycle is larger than a predetermined flow rate, the pressure loss of the refrigerant circulating in the cycle becomes large, and sufficient cooling performance cannot be exhibited.

  Therefore, in the first embodiment, the first cycle 10 is different from the second cycle 20 when the heat transfer amount between the evaporators 11 and 21 and the condensers 12 and 22 is set to the same condition. The pressure loss of the circulating refrigerant is configured to be small. Specifically, the first cycle 10 has a larger flow passage area in the cycle than the second cycle 20 so that the pressure loss of the refrigerant circulating in the cycle is reduced.

  In general, in a cycle in which a refrigerant circulates, a header tank and a connector of a heat exchanger (that is, an evaporator and a condenser) may control the pressure loss. Therefore, in the first embodiment, as shown in FIGS. 1 to 3, the flow path areas of the header tanks 112 and 113 and the flow paths of the connectors 114 and 115 of the evaporator 11 in the first cycle 10 are changed in the second cycle. The passage area of the header tanks 212 and 213 of the evaporator 21 and the passage areas of the connectors 214 and 215 of the evaporator 21 are formed to be larger. As shown in FIG. 1, the flow passage areas of the header tanks 122 and 123 of the condenser 12 of the first cycle 10 and the flow passage areas of the connectors 124 and 125 are also the same as those of the condenser 22 of the second cycle 20. It is formed larger than the flow path area of 222, 223 and the flow path area of the connectors 224, 225. Thereby, the pressure loss of the refrigerant circulating in the first cycle 10 is smaller than the pressure loss of the refrigerant circulating in the second cycle 20.

  In order to make the pressure loss of the refrigerant circulating in the first cycle 10 smaller than the pressure loss of the refrigerant circulating in the second cycle 20, it is sufficient to increase the area of the flow path at the rate-limiting part. Further, not only the flow path area of the heat exchanger but also the flow path area of the gas pipe 13 and the liquid pipe 14 of the first cycle It may be formed larger than the road area.

  Next, characteristics of the first cycle 10 and the second cycle 20 in the configuration of the first embodiment will be described with reference to FIG.

6 shows the relationship between the temperature difference and the cooling capacity in the first cycle 10, and the broken line B shows the relationship between the temperature difference and the cooling capacity in the second cycle 20. The temperature difference in the first cycle 10 is defined as a temperature T _{OUT1 of the} outside air supplied to the condenser 12 in the first cycle 10 and a temperature T _{IN2 of the} room air supplied to the evaporator 11 in the first cycle 10. Is the temperature difference. The temperature difference in the second cycle 20 refers to the temperature between the temperature T _{OUT2 of the} outside air supplied to the condenser 22 of the second cycle 20 and the temperature T _{IN1 of the} room air supplied to the evaporator 21 of the second cycle 20. Is the difference.

  In the first cycle 10 and the second cycle 20, the rate of increase in the cooling capacity with respect to the temperature difference is substantially the same between T1 and T2. However, when the temperature difference is T2 to T3, in the first cycle 10, the increase rate of the cooling capacity with respect to the temperature difference is not different from the increase rate of T1 to T2, whereas in the second cycle 20, the cooling capacity with respect to the temperature difference is different. The rise rate is lower than the rise rates of T1 and T2.

  That is, in the first cycle 10, since the pressure loss of the refrigerant circulating in the cycle is small, the temperature difference is substantially constant over T1 to T3. On the other hand, in the second cycle 20, since the pressure loss of the refrigerant circulating in the cycle is larger than that in the first cycle 10, when the temperature difference becomes T2 or more, the rate of increase in the cooling capacity with respect to the temperature difference in the first cycle 10 is increased. It is lower than.

  For this reason, in a configuration in which the air flow rate of the outdoor blower 30 and the air flow rate of the indoor blower 40 are different, it is possible to arrange the first cycle 10 on the side where the temperature difference is large and arrange the second cycle 20 on the side where the temperature difference is small. It is preferable. This is because the first cycle 10 has a configuration in which the rate of increase in cooling capacity does not decrease even when the temperature difference increases. This allows the air conditioner 1 to increase the cooling capacity in a configuration in which the air flow rate of the outdoor blower 30 and the air flow rate of the indoor blower 40 are different.

  However, in the first cycle 10, the evaporator 11, the condenser 12, and the like are provided because the flow path area in the cycle is formed larger than the second cycle 20, and the pressure resistance of the members constituting the flow path is ensured. There is a possibility that the pipes 13 and 14 become large or complicated. Therefore, in the first embodiment, the pressure loss of the refrigerant is reduced only in the first cycle 10 instead of reducing the pressure loss of the refrigerant in both the first cycle 10 and the second cycle 20. As a result, in the second cycle 20, an increase in size, complexity, or cost of the physique is suppressed. Therefore, the air conditioner 1 can increase the cooling capacity and suppress an increase in size, complexity, or cost.

(2nd Embodiment)
A second embodiment will be described. The second embodiment is different from the first embodiment in that the refrigerant to be charged in each of the first cycle 10 and the second cycle 20 is changed, and the other components are the same as those in the first embodiment. Only parts different from the embodiment will be described.

  Also in the second embodiment, similarly to the first embodiment, in a configuration in which the air flow rate of the outdoor blower 30 and the air flow rate of the indoor blower 40 are different, the first cycle 10 is arranged on the side where the temperature difference is large, and the side where the temperature difference is small. , The second cycle 20 is arranged.

In the second embodiment, the refrigerant circulating in the first cycle 10 has a higher gas density (kg / m ³ ) when compared with the refrigerant circulating in the second cycle 20 under the same temperature and pressure conditions. Used. Thereby, also in the second embodiment, the first cycle 10 has the same heat transfer amount between the evaporators 11 and 21 and the condensers 12 and 22 as the second cycle 20, It is possible to reduce the pressure loss of the refrigerant circulating in the cycle.

  For example, R410 can be used as the refrigerant charged in the first cycle 10, and R134a can be used as the refrigerant filled in the second cycle 20, for example. The amount of heat transfer between the evaporators 11, 21 and the condensers 12, 22 is proportional to the mass flow of the refrigerant circulating in the cycle. Therefore, if the first cycle 10 is filled with a refrigerant having a higher gas density than in the second cycle 20, if the heat transfer amounts between the evaporators 11, 21 and the condensers 12, 22 are the same, The volume flow rate of the refrigerant circulating in one cycle 10 is smaller than the volume flow rate of the refrigerant circulating in the second cycle 20. Therefore, in that case, the pressure loss of the refrigerant circulating in the first cycle 10 is smaller than the pressure loss of the refrigerant circulating in the first cycle 10. Thereby, in the first cycle 10, even when the temperature difference becomes large, it is possible to prevent a decrease in the rate of increase in the cooling capacity with respect to the temperature difference.

  However, when R410 is used as the refrigerant to be charged into the first cycle 10, for example, it is necessary to join the joints of the connector and the pipe by welding or the like because the molecular density of the refrigerant is low. Therefore, in the second embodiment, a refrigerant having a high gas density is used for the refrigerant in the first cycle 10 instead of using a refrigerant having a high gas density for all the cycles included in the air conditioner 1. Thereby, in the second cycle 20, complication of the configuration or increase in cost is suppressed. Therefore, the air conditioner 1 can increase the cooling capacity and suppress an increase in size, complexity, or cost.

(Third embodiment)
A third embodiment will be described. In the third embodiment, a part of the configuration of the first cycle 10 is changed from the first embodiment and the like, and the others are the same as the first embodiment and the like. Only the parts different from the above will be described.

  Also in the third embodiment, as in the first embodiment and the like, in a configuration in which the air flow rate of the outdoor blower 30 and the air flow rate of the indoor blower 40 are different, the first cycle 10 is arranged on the side where the temperature difference is large, and the temperature difference is small. The second cycle 20 is arranged on the side.

  As shown in FIG. 7, in the third embodiment, the number of connectors 114 provided in the header tank 112 of the evaporator 11 in the first cycle 10 is increased. That is, the number of connectors 114 provided in the header tank 112 of the evaporator 11 in the first cycle 10 is greater than the number of connectors 214 provided in the header tank 212 of the evaporator 21 in the second cycle 20. The gas pipes 13 are connected to the plurality of connectors 114, respectively.

  Although not shown, the number of connectors 124 and 125 connected to the header tanks 122 and 123 of the condenser 12 in the first cycle 10 is also changed with respect to the condensers 22 and 22 in the second cycle 20. It is preferable to increase the number of connectors 224 and 225 connected to the header tanks 222 and 223. Thereby, the pressure loss of the refrigerant circulating in the first cycle 10 is smaller than the pressure loss of the refrigerant circulating in the second cycle 20. Therefore, in the first cycle 10, even when the temperature difference becomes large, it is possible to prevent a decrease in the rate of increase in the cooling capacity with respect to the temperature difference.

  However, in the first cycle 10, the configuration of the evaporator 11, the condenser 12, the pipes 13 and 14, and the like may be complicated because the number of connectors is larger than in the second cycle 20. Therefore, in the third embodiment, the pressure loss of the refrigerant is reduced only in the first cycle 10 instead of reducing the pressure loss of the refrigerant in both the first cycle 10 and the second cycle 20. Thereby, in the second cycle 20, complication of the configuration or increase in cost is suppressed. Therefore, the air conditioner 1 can increase the cooling capacity and suppress an increase in size, complexity, or cost.

(Fourth embodiment)
A fourth embodiment will be described. The fourth embodiment is different from the first embodiment and the like in the arrangement of the outdoor blower 30 and the indoor blower 40 and the air volume, and the other configurations are the same as those of the first embodiment. Only the parts different from the above will be described.

As shown in FIG. 8, in the fourth embodiment, the blower amount B _IN of the indoor blower 40 is configured to be smaller than the blower amount B _OUT of the indoor blower 40.

  In the description of the fourth embodiment, of the plurality of cycles 10 and 20, the one in which the condenser is disposed on the upstream side where the outdoor blower 30 blows the outside air is referred to as the second cycle 20, and the outdoor blower 30 blows the outside air. The one in which the condenser is arranged on the downstream side is referred to as a first cycle 10. That is, the outdoor blower 30 blows outside air in the order of the condenser 22 included in the second cycle 20 and the condenser 12 included in the first cycle 10. That is, the condenser 22 of the second cycle 20 is arranged on the upstream side in the flow direction of the outside air blown by the outdoor blower 30, and the condenser 12 of the first cycle 10 is arranged on the downstream side.

  On the other hand, the indoor blower 40 blows outside air in the order of the evaporator 11 of the first cycle 10 and the evaporator 21 of the second cycle 20. That is, the evaporator 11 of the first cycle 10 is arranged on the upstream side in the flow direction of the indoor air blown by the indoor blower 40, and the evaporator 21 of the second cycle 20 is arranged on the downstream side.

As described above, in the fourth embodiment, the blower amount B _IN of the indoor blower 40 is configured to be smaller than the blower amount B _OUT of the indoor blower 40. Thereby, in the fourth embodiment, the air on the upstream side of the evaporator 11 included in the first cycle 10 is compared with the case where the blowing amount B _OUT of the indoor blower 40 and the blowing amount B _IN of the indoor blower 40 are the same. the difference between the temperature _{T IN1} and the downstream temperature _{T IN2} of the air becomes large. Therefore, the temperature T _IN2 of the air supplied to the evaporator 21 of the second cycle 20 after passing through the evaporator 11 of the first cycle 10 comes closer to the outside air temperature. Therefore, the difference between the temperature T _{OUT1 of the} outside air supplied to the condenser 22 included in the second cycle 20 and the temperature T _{IN2 of the} room air supplied to the evaporator becomes small. As a result, the difference between the temperature T _{OUT2 of the} outside air supplied to the condenser 12 in the first cycle 10 and the temperature T _{IN1 of the} room air supplied to the evaporator 11 is supplied to the condenser 22 in the second cycle 20. The temperature is larger than the difference between the outside air temperature T _OUT1 and the room air temperature T _IN2 supplied to the evaporator 21.

  Also in the fourth embodiment, the first cycle 10 circulates the cycle when the amount of heat transfer between the evaporators 11 and 21 and the condensers 12 and 22 is the same as that in the second cycle 20. The pressure loss of the refrigerant is reduced. The first cycle 10 is arranged on the side where the temperature difference is large, and the second cycle 20 is arranged on the side where the temperature difference is small. Therefore, also in the fourth embodiment, the air conditioner 1 can increase the cooling capacity and suppress an increase in size, complexity, or cost.

(Fifth embodiment)
A fifth embodiment will be described. The fifth embodiment also differs from the first embodiment in the arrangement and the air volume of the outdoor blower 30 and the indoor blower 40, and the other configurations are the same as those in the first embodiment. Only the parts different from the above will be described.

  As shown in FIG. 9, in the fifth embodiment, the indoor blower 40 and the outdoor blower 30 blow air from the same direction to the evaporators 11 and 21 and the condensers 12 and 22 included in the plurality of cycles 10 and 20, respectively. are doing.

  In the description of the fifth embodiment, of the plurality of cycles 10 and 20, the one in which the condenser 12 is arranged on the upstream side where the outdoor blower 30 blows the outside air is called the first cycle 10, and the condenser on the downstream side is the first cycle 10. The one in which 22 are arranged is called a second cycle 20. That is, the outdoor blower 30 blows outside air in the order of the condenser 12 included in the first cycle 10 and the condenser 22 included in the second cycle 20.

On the other hand, the indoor blower 40 also blows outside air in the order of the evaporator 11 of the first cycle 10 and the evaporator 21 of the second cycle 20. In the fifth embodiment, the air flow amount B _IN of the indoor blower 40 and the air flow amount B _OUT of the indoor blower 40 may be the same or different.

According to such a configuration, since the room temperature is higher than the outside air temperature in the cooling of the base station, the temperature T _OUT1 of the air on the upstream side of the condenser 12 in the first cycle 10 is compared with the temperature T _OUT2 of the air on the downstream side. Will approach the temperature of the indoor air. Further, the temperature T _IN2 of the air on the downstream side of the first cycle 10 is closer to the outside air temperature than the temperature T _IN1 of the air on the upstream side of the evaporator 11. Therefore, the difference between the temperature T _{OUT1 of the} outside air supplied to the condenser 12 included in the first cycle 10 and the temperature T _{IN1 of the} room air supplied to the evaporator 11 is determined by the difference supplied to the condenser 22 included in the second cycle 20. _Is larger than the difference between the outside air temperature T _OUT2 and the room air temperature T _IN2 supplied to the evaporator 21.

  Also in the fifth embodiment, the first cycle 10 circulates the cycle when the amount of heat transfer between the evaporators 11 and 21 and the condensers 12 and 22 is the same as that in the second cycle 20. The pressure loss of the refrigerant is reduced. The first cycle 10 is arranged on the side where the temperature difference is large, and the second cycle 20 is arranged on the side where the temperature difference is small. Therefore, also in the fifth embodiment, the air conditioner 1 can increase the cooling capacity and suppress an increase in size, complexity, or cost.

(Other embodiments)
The present invention is not limited to the embodiments described above, and can be appropriately modified within the scope described in the claims. In addition, the above embodiments are not irrelevant to each other, and can be appropriately combined unless a combination is clearly impossible. In each of the above embodiments, it is needless to say that the elements constituting the embodiment are not necessarily essential, unless otherwise clearly indicated as essential or in principle considered to be clearly essential. No. In each of the above embodiments, when a numerical value such as the number, numerical value, amount, range, or the like of the constituent elements of the exemplary embodiment is referred to, it is particularly limited to a specific number when it is clearly stated that it is essential and in principle. The number is not limited to the specific number unless otherwise specified. In each of the above embodiments, when referring to the shape of components and the like, positional relationship, and the like, unless otherwise specified and in principle limited to a specific shape, positional relationship, etc., the shape, It is not limited to a positional relationship or the like.

  For example, in each of the above embodiments, the air conditioner 1 has a configuration including two sets of cycles 10 and 20. On the other hand, in another embodiment, the air conditioner 1 may be configured to include three or more sets of cycles. Even in this case, of the plurality of cycles, the cycle installed on the side where the temperature difference is large, compared with other cycles, when the amount of heat transfer between the evaporator and the condenser is the same condition, The pressure loss of the refrigerant circulating in the cycle is configured to be small.

  For example, in each of the above-described embodiments, the air conditioner 1 has been described as performing cooling in the room of a base station in which a DC / AC switching device or a communication device (not shown) is stored. On the other hand, in other embodiments, the air conditioner 1 can be used not only as a base station but also as an air conditioner for various uses.

(Summary)
According to a first aspect of some or all of the above-described embodiments, a boiling-cooling air conditioner includes a plurality of cycles, an outdoor blower, and an indoor blower. The multiple cycles include an evaporator in which the refrigerant evaporates, a condenser in which the refrigerant evaporated in the evaporator condenses, a gas pipe through which the refrigerant evaporated in the evaporator flows to the condenser, and a refrigerant condensed in the condenser to the evaporator. Each has a flowing liquid pipe and constitutes a closed circuit in which the refrigerant naturally circulates. The outdoor blower sequentially blows outside air to a plurality of condensers included in a plurality of cycles. The indoor blower sequentially blows indoor air to a plurality of evaporators included in a plurality of cycles. Of the plurality of cycles, the first cycle is provided on the side where the temperature difference between the outside air supplied to the condenser and the room air supplied to the evaporator becomes larger than in the second cycle. And the 1st cycle is comprised so that the pressure loss of the refrigerant | coolant which circulates through a cycle may become small when the heat transfer amount between an evaporator and a condenser is made into the same conditions compared with a 2nd cycle. I have.

  According to the second aspect, in the first cycle, the flow path area in the cycle is formed larger than that in the second cycle so that the pressure loss of the refrigerant circulating in the cycle is reduced.

  According to this, instead of enlarging the configuration of all the cycles included in the air conditioner, instead of enlarging the configuration of the first cycle, etc., the cooling capacity is increased, and the physique is increased in size or complexity. Cost increase can be suppressed.

  According to the third aspect, as the refrigerant circulating in the first cycle, a refrigerant having a higher gas density when the temperature and the pressure are compared under the same conditions as compared with the refrigerant circulating in the second cycle is used.

  According to this, instead of using the refrigerant having a large gas density for all the cycles included in the air conditioner, the refrigerant having the large gas density is used for the refrigerant in the first cycle, thereby increasing the cooling capacity, It is possible to suppress an increase in size, complexity, or cost of the physique.

  According to the fourth aspect, the outdoor blower blows outside air in the order of the condenser of the first cycle and the condenser of the second cycle. The indoor blower blows the indoor air in the order of the evaporator of the second cycle and the evaporator of the first cycle. The amount of air that passes through the condenser due to the air blown by the outdoor blower is configured to be smaller than the amount of air that passes through the evaporator by air blown by the indoor blower.

  According to this, compared to the case where the amount of air passing through the condenser by the blower of the outdoor blower is the same as the amount of air passing through the evaporator by the blower of the indoor blower, the upstream side of the condenser included in the first cycle is provided. The temperature difference between the air and the downstream air increases. That is, the temperature of the air supplied to the condenser in the second cycle after passing through the condenser in the first cycle approaches the temperature of the room air. Therefore, the temperature difference between the outside air supplied to the condenser included in the first cycle and the room air supplied to the evaporator is determined by the difference between the outside air supplied to the condenser included in the second cycle and the indoor air supplied to the evaporator. Is larger than the temperature difference. Therefore, the air conditioner can increase the cooling capacity by suppressing the pressure loss of the refrigerant circulating in the first cycle, and can suppress an increase in size, complexity, or cost.

  According to the fifth aspect, the outdoor blower blows outside air in the order of the condenser of the second cycle and the condenser of the first cycle. The indoor blower blows indoor air in the order of the evaporator of the first cycle and the evaporator of the second cycle. The amount of air passing through the evaporator due to the air blown by the indoor blower is configured to be smaller than the amount of air passing through the condenser due to the air blown by the outdoor blower.

  According to this, compared to the case where the air volume passing through the condenser due to the blowing of the outdoor blower is the same as the air volume passing through the evaporator due to the blowing of the indoor blower, the upstream side of the evaporator in the first cycle is provided. The temperature difference between the air and the downstream air increases. That is, the temperature of air supplied to the evaporator of the second cycle after passing through the evaporator of the first cycle approaches the temperature of the outside air. Therefore, the temperature difference between the outside air supplied to the condenser included in the first cycle and the room air supplied to the evaporator is determined by the difference between the outside air supplied to the condenser included in the second cycle and the indoor air supplied to the evaporator. Is larger than the temperature difference. Therefore, the air conditioner can increase the cooling capacity by suppressing the pressure loss of the refrigerant circulating in the first cycle, and can suppress an increase in size, complexity, or cost.

  According to the sixth aspect, the outdoor blower blows outside air in the order of the condenser of the first cycle and the condenser of the second cycle. The indoor blower is configured to blow indoor air in the order of the evaporator of the first cycle and the evaporator of the second cycle.

  According to this, the temperature difference between the outside air supplied to the condenser included in the first cycle and the room air supplied to the evaporator is supplied to the outside air supplied to the condenser included in the second cycle and the evaporator. It is larger than the temperature difference with the room air. Therefore, the air conditioner can increase the cooling capacity by suppressing the pressure loss of the refrigerant circulating in the first cycle, and can suppress an increase in size, complexity, or cost.

DESCRIPTION OF SYMBOLS 1 Air conditioner 10, 20 Boiling cooling cycle 11, 21 Evaporator 12, 22 Condenser 13, 23 Gas piping 14, 24 Liquid piping 30 Outdoor blower 40 Indoor blower

Claims (6)

In a boiling cooling type air conditioner,
Evaporators (11, 21) for evaporating the refrigerant, condensers (12, 22) for condensing the refrigerant evaporated in the evaporator, and gas pipes (13, 23) for flowing the refrigerant evaporated in the evaporator to the condenser. And a plurality of boiling cooling cycles (10, 20) each having a liquid pipe (14, 24) through which the refrigerant condensed in the condenser flows to the evaporator, and constituting a closed circuit in which the refrigerant circulates naturally. ,
An outdoor blower (30) that sequentially blows outside air to the plurality of condensers included in the plurality of boiling cooling cycles,
An indoor blower (40) for sequentially blowing indoor air to the plurality of evaporators included in each of the plurality of boiling cooling cycles,
Among the plurality of boiling cooling cycles, the predetermined boiling cooling cycle (10) is different from the other boiling cooling cycles (20) in the outside air supplied to the condenser and the room supplied to the evaporator. It is installed on the side where the temperature difference with air is large,
The predetermined boiling cooling cycle has a smaller pressure loss of the refrigerant circulating in the cycle when the heat transfer amount between the evaporator and the condenser is the same as that of the other boiling cooling cycles. An air conditioner configured to be.   2. The predetermined boiling cooling cycle according to claim 1, wherein a flow passage area in the cycle is formed larger than other boiling cooling cycles so that a pressure loss of a refrigerant circulating in the cycle is reduced. 3. Air conditioner.   The refrigerant circulating in the predetermined boiling cooling cycle is a refrigerant having a larger gas density when the temperature and the pressure are compared under the same condition with respect to the refrigerant circulating in the other boiling cooling cycle. Or the air conditioner according to 2. The outdoor blower blows outside air in the order of the condenser having the predetermined boiling cooling cycle and the condenser having the other boiling cooling cycle,
The indoor blower blows the indoor air in the order of the evaporator that the other boiling cooling cycle has, the evaporator that the predetermined boiling cooling cycle has,
The air flow passing through the condenser due to the air blow from the outdoor blower is configured to be smaller than the air flow passing through the evaporator due to the air blow from the indoor blower. Air conditioner. The outdoor blower blows outside air in the order of the condenser of another boiling cooling cycle, the condenser of a predetermined boiling cooling cycle,
The indoor blower blows indoor air in the order of the evaporator having a predetermined boiling cooling cycle and the evaporator having the other boiling cooling cycle,
The air flow passing through the evaporator by the air blower of the indoor blower is configured to be smaller than the air flow passing through the condenser by the blower of the outdoor blower. Air conditioner. The outdoor blower blows outside air in the order of the condenser having the predetermined boiling cooling cycle and the condenser having the other boiling cooling cycle,
The indoor blower is configured to blow indoor air in the order of the evaporator of a predetermined boiling cooling cycle and the evaporator of another boiling cooling cycle. An air conditioner according to one.

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