JP2007303806A - Refrigerating cycle device and its operation method - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To provide a refrigerating cycle device and an operation method therefor, further heightening efficiency by improving the heat transfer characteristic of a refrigerant in an evaporator. <P>SOLUTION: A compressor 11, a heat radiator 12, an expansion valve 13, a second refrigerant-water heat exchanger 14 and the evaporator 15 are connected to each other by a refrigerating circuit 16 taking carbon dioxide, for example, as a refrigerant. The second refrigerant-water heat exchanger 14 is provided in the midway of the passage of refrigerant between the expansion valve 13 and the evaporator 15, and connected to a water circuit 18 where water passes. The refrigerant is depressurised by the expansion valve 13, then heated by heat exchange with water of the water circuit 18 by the second refrigerant-water head exchanger 14, and further it is vaporized by depriving heat from the air in the evaporator 15 to become overheat steam. It returns to the compressor 11. <P>COPYRIGHT: (C)2008,JPO&INPIT

Description

  The present invention relates to a refrigeration cycle apparatus used as a water heater and an operation method thereof.

  A refrigeration cycle apparatus that uses a compressor, a radiator, an expander, and an evaporator as main components and connects them through a refrigerant path, that is, a hot water supply apparatus using a so-called heat pump cycle has been put into practical use. In a water heater using a heat pump cycle, hot water is obtained by performing heat exchange between a high-temperature refrigerant and water in a radiator.

  In the refrigeration cycle apparatus, efforts have been made to improve the efficiency of various system performances such as improving the performance of components and optimizing control. As one of the system performance improving means, a configuration in which a sub heat exchanger is provided between refrigerant paths of an evaporator and a compressor has been proposed (for example, see Patent Document 1).

In Patent Document 1, as shown in FIG. 4, the refrigeration cycle apparatus 50 includes a compressor 51, a heat exchanger 52, an expansion valve 53, an evaporator 54, and an auxiliary heat exchanger 55, and includes a hot water storage tank 56. . Then, the hot water in the hot water storage tank 56 is sent to the flow passage 58 by the pump 57, and is transferred from the hot water to the heat receiving part 60 by the auxiliary heat exchanger 55 from the hot water to the refrigerant. Further, in the heat exchanger 52, heat is transferred from the condenser 61 to the heat receiving unit 62, and returns to the hot water storage tank 56. That is, the hot water taken out from the hot water storage tank 56 is subjected to heat exchange with a low-temperature refrigerant from the evaporator 54 toward the compressor 51 to lower the temperature, and then the hot water discharged from the compressor 51 by the heat exchanger 52 It is heated by exchanging heat with the refrigerant and returned to the hot water tank 56. By setting it as such a structure, compared with the case where there is no sub heat exchanger 55, although it changes with water temperature conditions with which the heat exchanger 52 heat-exchanges, a coefficient of performance is raised around 1.
JP 2002-98429 A

  However, firstly, the evaporator of the refrigeration cycle apparatus having the above-described configuration does not use a region where the refrigerant has a large heat transfer coefficient, and therefore has poor heat transfer characteristics in the evaporator. In the evaporator of the refrigeration cycle apparatus, the low-pressure refrigerant discharged from the expansion mechanism is vaporized by ambient heat from the gas-liquid mixed phase state. Here, when the refrigerant in the evaporator occupies a large area in the liquid phase, the refrigerant has a high density and flows through the pipe at a low flow rate, so the heat transfer coefficient is small and the volume of the heat exchanger is large. there were. Secondly, since the low-pressure refrigerant discharged from the expansion mechanism passes through the auxiliary heat exchanger in a state where the refrigerant is close to the gas state and the volume flow rate is large because the refrigerant is connected to the auxiliary heat exchanger through the evaporator. When the number of passes of the refrigerant pipe is small, the pressure loss increases and the coefficient of performance decreases, so that it is inevitably necessary to increase the number of passes of the refrigerant pipe, and the auxiliary heat exchanger becomes large.

  Therefore, the present invention provides a sub heat exchanger at the outlet of the expansion mechanism, and allows a low-pressure loss to be achieved even in a state where the number of passes of the refrigerant pipe is small by circulating a high-density refrigerant and is dried by the evaporator. The purpose of the present invention is to improve the heat transfer performance in the evaporator by using a large amount of refrigerant having a high degree and to provide a highly efficient refrigeration cycle apparatus and its operation method.

The refrigeration cycle apparatus of the present invention includes a compressor that compresses a refrigerant, a radiator that functions as a first refrigerant-water heat exchanger that radiates heat and heats the refrigerant compressed by the compressor, An expansion mechanism for reducing the pressure of the refrigerant radiated by the radiator, and a second refrigerant-water heat exchanger for exchanging heat between the refrigerant whose pressure has been reduced by the expansion mechanism and water having a temperature higher than that of the refrigerant. And an evaporator for evaporating the refrigerant after heat exchange with the second refrigerant-water heat exchanger, and a refrigerant circuit connected so as to circulate in a path through which the refrigerant flows,
The second refrigerant-water heat exchanger in which water supplied from a water supply source is cooled by exchanging heat with the refrigerant, and the radiator in which the water is heated by exchanging heat with the refrigerant. A water path for flowing the water in the connected flow path;
It is set as the structure provided with.

  In the refrigeration cycle apparatus having such a configuration, since the low-pressure refrigerant whose degree of dryness of the refrigerant has been increased by the refrigerant-water heat exchanger enters the evaporator, the refrigerant in the evaporator pipe should use a region having high heat transfer characteristics. Thus, a small and highly efficient refrigeration cycle apparatus can be configured.

The operation method of the refrigeration cycle apparatus of the present invention includes a compressor that compresses a refrigerant, and a radiator that functions as a first refrigerant-water heat exchanger that radiates heat from the refrigerant compressed by the compressor and heats water. And an expansion mechanism for reducing the pressure of the refrigerant radiated by the radiator, and a second refrigerant-water for exchanging heat between the refrigerant whose pressure has been reduced by the expansion mechanism and water having a temperature higher than that of the refrigerant A refrigerant circuit connected in a form in which a heat exchanger and an evaporator that evaporates the refrigerant after heat exchange with the second refrigerant-water heat exchanger circulates in a path through which the refrigerant flows;
The second refrigerant-water heat exchanger, in which water supplied from a water supply source is cooled by exchanging heat with the refrigerant, and the radiator, in which the water is heated by exchanging heat with the refrigerant, are connected in this order. An operation method of a refrigeration cycle apparatus comprising a water path for flowing the water through the flow path,
Heat is exchanged between the refrigerant and the water in the second refrigerant-water heat exchanger so that the refrigerant sucked by the compressor becomes superheated steam.

  With such a refrigeration cycle apparatus operating method, the first is the second refrigerant-water heat exchanger, which increases the dryness of the refrigerant and improves the heat transfer characteristics. Second, since superheated steam can be easily formed at the outlet of the evaporator, liquid compression in the compressor can be prevented and reliability can be improved. Third, the amount of exchange heat of the low-pressure refrigerant can be increased, and the superheated steam at a higher temperature can be obtained. Therefore, the efficiency of the refrigeration cycle apparatus can be improved.

  Further, the operation method of the refrigeration cycle apparatus of the present invention is such that the temperature of water that exchanges heat with the refrigerant in the refrigerant-water heat exchanger can be made constant by mixing the hot water of the hot water storage tank with water, and the dryness of the refrigerant Since the refrigerant outlet enthalpy of the radiator can be made constant, it is possible to control the refrigeration cycle to be stable and optimal.

Further, another refrigeration cycle apparatus operating method of the present invention functions as a compressor that compresses a refrigerant, and a first refrigerant-water heat exchanger that radiates heat from the refrigerant compressed by the compressor and heats water. Heat exchanger, an expansion mechanism that reduces the pressure of the refrigerant radiated by the radiator, and a second heat exchanger that exchanges heat between the refrigerant whose pressure is reduced by the expansion mechanism and water having a temperature higher than that of the refrigerant. A refrigerant circuit connected in a form in which a refrigerant-water heat exchanger and an evaporator for evaporating the refrigerant after heat exchange with the second refrigerant-water heat exchanger are circulated in a path through which the refrigerant flows;
The second refrigerant-water heat exchanger, in which water supplied from a water supply source is cooled by exchanging heat with the refrigerant, and the radiator, in which the water is heated by exchanging heat with the refrigerant, are connected in this order. An operation method of a refrigeration cycle apparatus comprising a water path for flowing the water through the flow path,
The flow rate of the water is controlled so that the temperature of the refrigerant and water before heat exchange by the radiator is detected and the refrigerant exiting the radiator reaches a predetermined temperature.

With such an operation method, the amount of heat exchange between the refrigerant and water in the radiator can be reliably controlled, so that a necessary amount of heat radiation can be obtained in the radiator. At this time, since a heat radiation amount exceeding a certain level can be obtained even with a seasonal change by the radiator, a more efficient operation method of the refrigeration cycle apparatus can be achieved.

  According to the refrigeration cycle apparatus of the present invention and the operation method thereof, the heat transfer coefficient of the refrigerant in the evaporator is increased, and a highly efficient refrigeration cycle apparatus and the operation method thereof can be obtained.

  Hereinafter, embodiments of the present invention will be described with reference to the drawings.

(Embodiment)
As shown in FIG. 1, a refrigeration cycle apparatus 10 according to an embodiment of the present invention circulates a refrigerant to form a heat pump cycle and water for heating water using the refrigerant circuit 16. It has a path 18. The refrigerant circuit 16 includes a compressor 11 that compresses the refrigerant, a radiator 12 that is a first refrigerant-water heat exchanger that radiates heat from the refrigerant compressed by the compressor 11 and heats water in the water path 18, An expansion valve 13 that is an expansion mechanism for reducing the pressure of the refrigerant radiated by the radiator 12, a refrigerant-water heat exchanger 14 for exchanging heat between the refrigerant whose pressure is reduced by the expansion valve 13 and water, and a refrigerant The evaporator 15 which evaporates the refrigerant | coolant after heat-exchanged with the water heat exchanger 14 is connected in order. The refrigerant used here is, for example, carbon dioxide. Further, the water path 19 on the supply side is connected to clean water through water flow control valves 31, 147 and 25 as a water supply source. The water supplied from the water supply source flows through the water path 19 and is branched into a first branch path 180 passing through the second refrigerant-water heat exchanger and a second branch path 181 bypassing it. The water path 18 is integrated again, passes through the radiator 12, is heated by the refrigerant, and hot water is supplied to the hot water tank 17. Here, tap water is tap water. Further, as shown in FIG. 1, the water path 19 is connected to the hot water tank 17 via a water flow rate control valve 31 in order to reheat the water whose temperature has been lowered in the hot water tank 17 as necessary.

  The feature of the hot water supply apparatus of the present embodiment is that it has a second refrigerant-water heat exchanger 14, thereby cooling water and heating the refrigerant. In the conventional hot water supply apparatus, only the first refrigerant-water heat exchanger of the present embodiment, that is, the radiator 12, is used as the heat exchanger for water and refrigerant. Since the hot water supply apparatus of the present embodiment has such a configuration, the compressor power can be reduced and a highly efficient system can be configured. The reason for this will be described later with reference to FIG.

  Next, description of other configurations of the present embodiment will be continued. The evaporator 15 is provided with a fan 21. The refrigerant circuit 16 is provided with a temperature sensor 22 and a temperature sensor 23 that measure the temperature of each refrigerant before entering the radiator 12 and the second refrigerant-water heat exchanger 14. In the water path 19, a temperature sensor 24 that measures the temperature of tap water such as tap water, a flow rate adjustment valve 25, a flow rate adjustment valve 27 provided in the path from the water path 19 to the first branch path 180, and its opening degree. Is provided with a signal line 44 for adjusting. The water path 19 is a temperature sensor 29 that measures the outlet temperature of the hot water tank 17, a water supply pump 30, a flow rate adjustment valve 31, and a temperature sensor that measures the temperature of clean water before entering the second refrigerant-water heat exchanger 14. 26, a flow rate adjusting valve 27, and a temperature sensor 28 for measuring the temperature of clean water before entering the radiator 12 are provided. The second branch path 181 is provided with a flow rate adjustment valve 33.

  The temperature sensors 24, 29, 22, 28, 23, and 26 are connected to the control device 34 by signal lines 35, 36, 37, 38, 39, and 40, respectively. Further, the control device 34 is connected to the flow rate adjusting valves 31 and 25, the fan 21, and the flow rate adjusting valves 27 and 33 through signal lines 41, 42, 43, 44, and 45, respectively. The hot water in the hot water tank 17 is supplied to a hot water supply load unit 46 such as a bathtub.

Next, operation | movement of the refrigerating-cycle apparatus 10 of FIG. 1 is demonstrated. The refrigerant is discharged at a high temperature and high pressure by the compressor 11 in the refrigerant circuit 16 and is radiated by exchanging heat with the water in the water circuit 18 by the radiator 12 which is the first refrigerant-water heat exchanger. Here, since the refrigerant is cooled by the water of the water circuit 18, the outlet enthalpy can be sufficiently lowered and the heat radiation amount can be increased. Furthermore, since the refrigerant | coolant of the heat radiator 12 should just be heat exchange with a low temperature clean water, the pressure of a refrigerant | coolant can be made low.

  Then, after the pressure of the refrigerant is reduced by the expansion valve 13, the refrigerant is heated by exchanging heat with the water in the water circuit 18 by the second refrigerant-water heat exchanger 14, thereby increasing the dryness of the refrigerant and evaporating. In the vessel 15, heat is further taken from the atmosphere and vaporized and returned to the compressor 11. Here, if the degree of superheat of the refrigerant is increased and sucked into the compressor 11, when the refrigerant discharge temperature of the compressor 11 is constant, the discharge pressure of the refrigerant can be reduced, and the compression The compression power of the machine 11 can be reduced. This adjustment of the amount of superheat is performed in the evaporation process by adjusting the fan air volume of the fan 21 and the opening of the valve 33 provided in the bypass passage 181 and the valve 27 provided in front of the second refrigerant-water heat exchanger 14. This is done by adjusting the evaporation amount of a certain refrigerant.

  After the water is cooled by exchanging heat with the refrigerant in the second refrigerant-water heat exchanger 14 in the water circuit 180, the water is heated by exchanging heat with the refrigerant in the radiator 12 and stored in the hot water tank 17. .

  Next, a method for controlling the amount of water in the first branch path 180 and the second branch path 181 will be described in detail.

  In principle, after controlling the amount of water in the first branch path 180, the amount of water in the water paths 18 and 19 is controlled by controlling the amount of water in the second branch path 181.

  The amount of water in the first branch path is controlled in the following procedure as shown in FIG. In step S <b> 101, the temperature of the refrigerant entering the second refrigerant-water heat exchanger 14 is measured by the temperature sensor 23. Next, in step S102, the control device 34 sets the target dryness of the refrigerant achieved by the second refrigerant-water heat exchanger 14, and based on the refrigerant inlet temperature of the heat exchanger 14 measured in step S101. The heat exchange amount of the heat exchanger 14 is determined. Next, in step S <b> 103, the temperature of water entering the second refrigerant-water heat exchanger 14 is measured by the temperature sensor 26 and input to the control device 34. Next, in step S104, the controller 34 determines the first temperature based on the refrigerant temperature at the entrance side of the heat exchanger 14 measured in step S101, the amount of heat exchange determined in step S102, and the temperature of water supplied from clean water. An appropriate amount of water flowing through the branch path 180 is determined. In step S105, the amount of water flowing through the first branch circuit 180 is controlled by controlling the opening of the water amount control valve 27 of the first branch circuit 180 and / or the flow control valve 25 of the water path. Further, if necessary, the air volume of the fan 21 of the evaporator can be adjusted to control the degree of superheat appropriately.

  Next, the flow rate of the second branch path 181 is controlled by the procedure shown in FIG. In step S <b> 201, the temperature of the refrigerant entering the radiator (first refrigerant-water heat exchanger) 12 is measured by the temperature sensor 22. The measured value is input to the control device 34. In step S202, the heat exchanger heat exchange amount is determined based on the radiator inlet refrigerant temperature measured in step S201 so that the coefficient of performance of the refrigeration cycle is maximized. Next, in step S <b> 203, the radiator-side water temperature is measured by the temperature sensor 28 and input to the control device 34. Next, in S204, the flow rate of the water flowing through the radiator is determined based on the refrigerant temperature entering the radiator 12 measured in S201, the heat exchanger heat exchange amount calculated in S202, and the water temperature entering the radiator. In S205, the opening degree of the flow control valve 33 of the second branch path 181 and the flow control valve 25 of the water path are adjusted based on that.

As described above, by repeatedly performing the control shown in FIGS. 5 and 6,
Optimal device control is possible.

In the above description, the case of having the second branch path (bypass path) 181 has been described with respect to the water path. With the second branch circuit, it is possible to adjust the amount of heat exchange between the first refrigerant-water heat exchanger and the second refrigerant-water heat exchanger. However, the present invention is also effective when there is no second branch circuit (second refrigerant-by-water heat exchanger bypass path). That is, the heat exchange amount of the second refrigerant-water heat exchanger can be adjusted by increasing / decreasing the evaporator fan air volume, using hot water stored in the hot water storage tank, and the like.

Next, the operation of the second refrigerant-water heat exchanger 14 will be described. FIG. 2 shows the relationship between heat transfer coefficient and dryness in a general evaporator (for example, see Air Conditioning and Refrigeration Union Papers, 2003, Vol. 37, p. 123). The horizontal axis represents the dryness of the refrigerant, and the vertical axis represents the heat transfer coefficient with respect to the dryness. Here, the dryness is a ratio of the liquid phase contained in the saturated vapor of the refrigerant, and is a case where the dryness 0 is all liquid phase and the dryness 1 is all gas phase. That is, the low dryness corresponds to the vicinity of the inlet of the evaporator in the refrigerant flow direction, and the high dryness corresponds to the vicinity of the outlet of the evaporator. As is clear from FIG. 2, the heat transfer coefficient of the refrigerant increases as the dryness increases, and reaches a maximum when the dryness is around 0.8. Therefore, the average heat transfer coefficient in the evaporator is improved by allowing the refrigerant having a high dryness to flow into the evaporator rather than putting the refrigerant having a dryness of nearly zero.

  Therefore, when the dryness of the refrigerant is raised by the second refrigerant-water heat exchanger 14 and then put into the evaporator 15, the heat transfer characteristics in the evaporator 15 are improved. And since the refrigerant heated with water in the second refrigerant-water heat exchanger 14 can be easily heated to superheated steam in the evaporator 15, liquid compression in the compressor 11 can be prevented, and The compressor power can be reduced, and the coefficient of performance of the refrigeration cycle apparatus can be improved.

  Next, improvement in efficiency of the refrigeration cycle apparatus 10 according to the embodiment of the present invention will be described with reference to FIG. 3 compared with a conventional refrigeration cycle apparatus. FIG. 3 is a Mollier diagram in which the vertical axis indicates the refrigerant pressure and the horizontal axis indicates the refrigerant enthalpy.

The Mollier diagram of FIG. 3 shows the case where the refrigerant is carbon dioxide, and the saturation curve 47 shows a line connecting the saturated liquid line of the refrigerant and the saturated vapor line. The closed cycle A ₁ B ₁ C ₁ D ₁ 48 is a Mollier diagram of the refrigeration cycle apparatus 10 according to the embodiment of the present invention, and the closed cycle A ₂ B ₂ C ₂ D ₂ 49 is a conventional second refrigerant-water. It is a Mollier diagram of a water heater (refrigeration cycle apparatus) that does not use a heat exchanger.

The closed cycle A ₁ B ₁ C ₁ D ₁ 48 of FIG. 3 will be described in detail in comparison with the configuration diagram of FIG. Refrigerant in the compressor 11, is changed to the point B ₁ from the point A ₁ in FIG. 3, the pressure and enthalpy is increased. Further, the heat radiator 12 changes the point B ₁ to the point C ₁ to decrease the enthalpy while keeping the refrigerant pressure constant. In the expansion valve 13 is changed from the point B ₁ to the point C _1, while the enthalpy of the refrigerant is constant, decreasing the pressure. Then, with the pressure kept constant, the second refrigerant-water heat exchanger 14 and the evaporator 15 are changed from the point D ₁ to the point A ₁ to increase the enthalpy.

Here, in the evaporator of the conventional refrigeration cycle apparatus, the refrigerant only changes from the point D ₂ to the point A ₂ , but in the refrigeration cycle apparatus 10 according to the embodiment of the present invention, the second refrigerant-water heat due to the provision of the exchanger 14 can be a point a ₁ of easily overheated steam by simultaneously evaporator 15 when the outlet enthalpy can be reduced in the radiator 12. By reducing the refrigerant outlet enthalpy in the radiator 12, a region with a high heat transfer coefficient below the pseudocritical temperature can be used. In addition, since the refrigerant can exchange heat with low-temperature water in the radiator 12 and can increase the degree of superheat at the outlet of the evaporator, the point is higher than the heat radiation pressure at points B ₂ and C _{2 in} the conventional radiator. The heat radiation pressure at B ₁ and point C ₁ can be lowered. As a result, the power of the compressor 11 can be reduced. Then, in the radiator 12, it is possible by the difference between the point C ₂ and the point C ₁ from the conventional radiator can take the enthalpy increased to increase the heat radiation amount utilized is the enthalpy quantity in the radiator.

  Thus, the refrigeration cycle apparatus 10 according to the embodiment of the present invention can increase the heat transfer performance in the evaporator 15 by increasing the dryness of the refrigerant in the second refrigerant-water heat exchanger 14.

In addition, since the refrigerant can be easily converted into superheated steam by the evaporator 15, the compressor 11 does not suck the liquid refrigerant and cause liquid compression. Moreover, since the refrigerant is superheated steam, the power of the compressor 11 can be reduced.
Further, since the refrigerant of the radiator 12 exchanges heat with water having a high air temperature in winter, the degree of superheat in the evaporation process can be increased, leading to improved reliability of the compressor 11.

  According to the embodiment of the present invention, when the temperature of tap water or the like is low, the hot water in the hot water storage tank is mixed to increase the water temperature, and the refrigerant in the second refrigerant-water heat exchanger can be heated. it can. On the other hand, in the intermediate period and summer period when the tap water temperature is high, the incoming water temperature increases, so the amount of heat received in the second refrigerant-water heat exchanger 14 increases, and the coefficient of performance of the refrigeration cycle apparatus improves.

  The refrigeration cycle apparatus and its operating method according to the present invention relate to a vapor compression refrigeration cycle and are useful when applied to a heat pump type hot water supply apparatus or the like.

The block diagram of the refrigerating-cycle apparatus of embodiment of this invention Diagram showing the relationship between heat transfer coefficient and dryness in a typical evaporator Mollier diagram of the refrigeration cycle apparatus according to the embodiment of the present invention Configuration diagram of conventional refrigeration cycle equipment The flowchart explaining the method of controlling the water quantity of a 1st branch path | route in the refrigerating cycle of embodiment of this invention. The flowchart explaining the method of controlling the water quantity of a 2nd branch path in the refrigerating cycle of embodiment of this invention.

Explanation of symbols

10, 50 Refrigeration cycle apparatus 11, 51 Compressor 12 Radiator (first refrigerant-water heat exchanger)
13, 53 Expansion valve 14 Second refrigerant-water heat exchanger 15, 54 Evaporator 16 Refrigerant circuit 17, 56 Hot water tank 18 Water path 19 Water path
21 Fan 22, 23, 24, 26, 28, 29 Temperature sensor 25, 27, 31, 32, 33, 147 Flow control valve 30 Water pump 34 Controller 35, 36, 37, 38, 39, 40, 41, 42 , 43, 44, 45, 148 Signal line 46 Hot water supply load unit 47 Saturation curve 48 Closed cycle A ₁ B ₁ C ₁ D ₁
49 Closed cycle A ₂ B ₂ C ₂ D ₂
52 Heat Exchanger 55 Sub Heat Exchanger 57 Pump 58 Flow Path 59 Heat Transfer Unit 60, 62 Heat Receiving Unit
61 Gas cooler

Claims (7)

A compressor that compresses the refrigerant; a radiator that functions as a first refrigerant-water heat exchanger that radiates heat of the refrigerant compressed by the compressor and heats the water; and the refrigerant that is radiated by the radiator An expansion mechanism that lowers the pressure of the refrigerant, a second refrigerant that exchanges heat between the refrigerant whose pressure has been reduced by the expansion mechanism and water having a higher temperature than the refrigerant, and the second refrigerant. A refrigerant circuit connected in such a manner that an evaporator for evaporating the refrigerant after heat exchange with the water heat exchanger circulates in a path through which the refrigerant flows;
The second refrigerant-water heat exchanger in which water supplied from a water supply source is cooled by exchanging heat with the refrigerant, and the radiator in which the water is heated by exchanging heat with the refrigerant. A water path for flowing the water in the connected flow path;
A refrigeration cycle apparatus comprising: A hot water storage tank is provided as the water supply source,
The refrigeration cycle apparatus according to claim 1, wherein the water path supplies water from the hot water storage tank to the second refrigerant-water heat exchanger and supplies water heated by the radiator to the hot water storage tank. The water supply source includes a water supply source different from the hot water storage tank and the hot water storage tank,
3. The refrigeration cycle apparatus according to claim 2, wherein the water path mixes water from the hot water storage tank and water from a water supply source different from the hot water storage tank and supplies the mixed water to the second refrigerant-water heat exchanger.   The refrigeration cycle apparatus according to claim 1, wherein the water path includes a path that bypasses the second refrigerant-water heat exchanger. A compressor that compresses the refrigerant; a radiator that functions as a first refrigerant-water heat exchanger that radiates heat of the refrigerant compressed by the compressor and heats the water; and the refrigerant that is radiated by the radiator An expansion mechanism that lowers the pressure of the refrigerant, a second refrigerant that exchanges heat between the refrigerant whose pressure has been reduced by the expansion mechanism and water having a higher temperature than the refrigerant, and the second refrigerant. A refrigerant circuit connected in a form in which an evaporator for evaporating the refrigerant after heat exchange with the water heat exchanger circulates in a path through which the refrigerant flows;
The second refrigerant-water heat exchanger, in which water supplied from a water supply source is cooled by exchanging heat with the refrigerant, and the radiator, in which the water is heated by exchanging heat with the refrigerant, are connected in this order. An operation method of a refrigeration cycle apparatus comprising a water path for flowing the water through the flow path,
A method for operating a refrigeration cycle apparatus in which heat is exchanged between the refrigerant and the water in the second refrigerant-water heat exchanger so that the refrigerant sucked by the compressor becomes superheated steam.   The temperature or flow rate of the water or the evaporator is such that the temperature of the refrigerant and water before the heat exchange with the second refrigerant-water heat exchanger is detected and the refrigerant sucked into the compressor becomes superheated steam. The operating method of the refrigerating cycle apparatus of Claim 5 which controls the air volume of the fan which ventilates to. A compressor that compresses the refrigerant; a radiator that functions as a first refrigerant-water heat exchanger that radiates heat of the refrigerant compressed by the compressor and heats the water; and the refrigerant that is radiated by the radiator An expansion mechanism that lowers the pressure of the refrigerant, a second refrigerant that exchanges heat between the refrigerant whose pressure has been reduced by the expansion mechanism and water having a higher temperature than the refrigerant, and the second refrigerant. A refrigerant circuit connected in a form in which an evaporator for evaporating the refrigerant after heat exchange with the water heat exchanger circulates in a path through which the refrigerant flows;
The second refrigerant-water heat exchanger, in which water supplied from a water supply source is cooled by exchanging heat with the refrigerant, and the radiator, in which the water is heated by exchanging heat with the refrigerant, are connected in this order. An operation method of a refrigeration cycle apparatus comprising a water path for flowing the water through the flow path,
The operating method of the refrigerating-cycle apparatus which detects the temperature of the refrigerant | coolant and water before making it heat-exchange with the said heat radiator, and controls the flow volume of the said water so that the refrigerant | coolant which leaves the said heat exchanger may become predetermined | prescribed temperature.

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