JP2011099572A - Refrigerating cycle device and hot-water heating device using the same - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To provide a refrigerating cycle device and a hot-water heating device capable of improving capacity and performance under a high compression ratio condition of high load in a space heating (heating) operation at a low outside air temperature. <P>SOLUTION: This refrigerating cycle device includes a first bypass circuit 3a including a refrigerant circuit 2 configured by successively connecting a compressor 21, a condenser 22, a supercooling heat exchanger 23, a main expanding means 24 and an evaporator 25, and a control device 4, branched from between the supercooling heat exchanger 23 and the main expanding means 24, and connected to an intake side of the compressor 21 through the bypass expanding means 31 and the supercooling heat exchanger 23, and a second bypass circuit 4a branched from between the condenser 22 and the supercooling heat exchanger 23, and connected to an inlet side of the main expanding means 24 through a flow rate regulation means 41 and the evaporator 25. <P>COPYRIGHT: (C)2011,JPO&amp;INPIT

Description

  The present invention relates to a refrigeration cycle apparatus for supercooling refrigerant and a hot water heater using the refrigeration cycle apparatus.

  2. Description of the Related Art Conventionally, there has been provided a refrigeration cycle apparatus in which a supercooling heat exchanger is provided on the downstream side of a condenser in a refrigerant circuit, and the refrigerant flowing out of the condenser is supercooled by allowing the expanded refrigerant to flow into the supercooling heat exchanger. Are known. For example, Patent Document 1 discloses a refrigeration cycle apparatus 100 as shown in FIG.

  The refrigeration cycle apparatus 100 includes a refrigerant circuit 110 that circulates refrigerant and a bypass passage 120. The refrigerant circuit 110 is configured by connecting a compressor 111, a condenser 112, a part 116 of an evaporator 115, a supercooling heat exchanger 113, a main expansion valve 114, and an evaporator 115 in an annular shape by piping.

  The bypass 120 branches from the refrigerant circuit 110 between the supercooling heat exchanger 113 and the main expansion valve 114, and enters the refrigerant circuit 110 between the evaporator 115 and the compressor 111 via the supercooling heat exchanger 113. linked. The bypass passage 120 is provided with a bypass expansion valve 121 upstream of the supercooling heat exchanger 113.

  Further, in the refrigeration cycle apparatus 100, the high-pressure liquid refrigerant that has exited the condenser 112 is guided to the part 116 of the evaporator 115, and after heating the part 116 of the evaporator 115, flows into the supercooling heat exchanger 113. By this, the function which suppresses the freezing in an evaporator at the time of the heating operation in low external temperature conditions is fulfilled.

JP 2000-18737 A

  However, as described in Patent Document 1, during heating, although it is a part of the heat exchanger, the entire refrigerant flow rate (high-pressure liquid refrigerant) flows through the part 116 of the evaporator 115 to dissipate heat. Since it is used for preventing freezing of the evaporator 115, the heat absorption capacity of the evaporator 115 that is originally installed to absorb heat from the outside air is reduced, resulting in a decrease in heating capacity and COP.

  That is, although a part of the high-pressure liquid refrigerant flows into the part 116 of the evaporator, the surface temperature of the part 116 of the evaporator rises, so that the evaporation of the adjacent evaporator 115 occurs due to heat conduction. The surface temperature of the portion increases, the temperature difference from the air decreases, and the endothermic amount decreases.

  In view of such circumstances, the present invention provides a refrigeration cycle apparatus and hot water that can realize high performance and high performance under a high compression ratio condition that is a heavy load in heating (heating) operation at low outside air temperature. An object is to provide a heating device.

  In order to solve the above problems, a refrigeration cycle apparatus according to the present invention includes a refrigerant circuit formed by connecting a compressor, a condenser, a supercooling heat exchanger, a main expansion means, and an evaporator in this order, and a control device. , Branched from between the supercooling heat exchanger and the main expansion means, and connected to the suction side of the compressor via the bypass expansion means, the supercooling heat exchanger, and the condensation And a second bypass circuit which branches from between the supercooling heat exchanger and the supercooling heat exchanger and is connected to the inlet side of the main expansion means via the flow rate adjusting means and the evaporator. Therefore, not the total amount of refrigerant but some refrigerant (high-pressure liquid state) flows through a part of the evaporator, dissipates the heat held by the refrigerant, and a part of the evaporator, for example, the bottom of the outdoor heat exchanger Suction in an outdoor heat exchanger that functions as an evaporator while preventing freezing It is possible to prevent a decrease in capacity.

  According to the present invention, it is possible to provide a refrigeration cycle apparatus and a hot water heating apparatus that can realize high performance and high performance under high compression ratio conditions that are high loads in heating (heating) operation at low outside air temperature. .

Schematic configuration diagram of a refrigeration cycle apparatus according to Embodiment 1 of the present invention. Mollier diagram of the refrigeration cycle apparatus shown in FIG. Flowchart of operation control of the refrigeration cycle apparatus in Embodiment 1 of the present invention. Schematic configuration diagram of another refrigeration cycle apparatus according to Embodiment 1 of the present invention. Schematic configuration diagram of a refrigeration cycle apparatus according to Embodiment 2 of the present invention. Flow chart of operation control of the refrigeration cycle apparatus Schematic configuration diagram of a conventional refrigeration cycle apparatus

  A first invention includes a refrigerant circuit formed by connecting a compressor, a condenser, a supercooling heat exchanger, a main expansion unit, and an evaporator in order, and a control device, and the supercooling heat exchanger and the main cooling device Branching between the expansion means, a bypass expansion means, a first bypass circuit connected to the suction side of the compressor via the supercooling heat exchanger, and the condenser and the supercooling heat exchanger. A refrigeration cycle apparatus having a second bypass circuit branched from between and connected to the inlet side of the main expansion means via the flow rate adjusting means and the evaporator, not the total refrigerant amount, A part of the refrigerant (high-pressure liquid state) flows through a part of the evaporator, dissipates the heat held by the refrigerant, and prevents the freezing of a part of the evaporator, for example, the bottom of the outdoor heat exchanger. As a result, it is possible to prevent a decrease in heat absorption capacity.

  The second invention includes a temperature sensor for detecting the refrigerant temperature on the outlet side of the second bypass circuit, and condensing temperature detecting means for detecting the condensation temperature, and the refrigerant temperature on the outlet side of the second bypass circuit and the excess temperature. The amount of refrigerant flowing through the flow rate adjusting means is adjusted so that the temperature difference from the condensation temperature of the cooling heat exchanger is within a predetermined range. The amount of flowing refrigerant can be finely controlled, that is, the flow rate can be controlled so that the degree of subcooling at the outlet side of the second bypass circuit is within a predetermined range, so that the subcooling effect of a part of the evaporator is maximized. It can be pulled out.

  Further, the refrigerant gas component that does not contribute to evaporation can be bypassed to the suction side of the compressor via the first bypass circuit while simultaneously increasing the refrigerant enthalpy change amount in the evaporator by the first bypass circuit. An increase in meaningless pressure loss can be suppressed, that is, the suction pressure of the compressor can be increased, and the refrigerant flow rate can be increased and the condensation (heating) capacity can be increased.

  A third invention includes an outside air temperature sensor that detects an outside air temperature, and an evaporator temperature sensor that detects an evaporation temperature of a pre-evaporator, and the outside air temperature detected by the outside air temperature sensor and the evaporator temperature sensor. When at least one of the detected evaporating temperatures is equal to or lower than a predetermined temperature, the amount of refrigerant flowing through the flow rate adjusting means is increased, the outside air temperature detected by the outside air temperature sensor, and the evaporating temperature detected by the evaporator temperature sensor When at least one of them is equal to or higher than a predetermined temperature, the amount of refrigerant flowing through the flow rate adjusting means is reduced, and the degree of freezing phenomenon at the bottom of the evaporator is detected from the outside temperature or the evaporation temperature. When at least one of them is below a predetermined temperature, it is determined that the evaporator freezing phenomenon has progressed, and the amount of refrigerant flowing through the flow rate adjusting means is increased, and the bottom of the evaporator (outdoor heat exchanger) It can work to prevent freezing.

  On the other hand, if at least one of the detected outside air temperature and evaporation temperature is equal to or higher than a predetermined temperature, it is determined that the freezing phenomenon of the evaporator has not progressed, and the amount of refrigerant flowing through the flow rate adjusting means is reduced, It is possible to prevent a decrease in heat absorption capacity in the outdoor heat exchanger that functions as an evaporator.

  4th invention is a hot water heating apparatus which heats warm water with the condenser of the refrigerating cycle device of any one of claims 1-3, and is not only a case where a condenser is a refrigerant to air heat exchanger. The present invention can also be applied to a refrigerant-to-water heat exchanger, and the same effect as described above can be obtained.

  Hereinafter, embodiments of the present invention will be described with reference to the drawings. Note that the present invention is not limited to the embodiments.

(Embodiment 1)
FIG. 1 shows a refrigeration cycle apparatus 1A according to a first embodiment of the present invention. The refrigeration cycle apparatus 1A includes a refrigerant circuit 2 that circulates refrigerant, a first bypass circuit 3a, a first bypass circuit 3b, and a control device 4. As the refrigerant, for example, a non-azeotropic refrigerant mixture such as R407C, a pseudo-azeotropic refrigerant mixture such as R410A, or a single refrigerant can be used.

  The refrigerant circuit 2 is configured by connecting a compressor 21, a condenser 22, a supercooling heat exchanger 23, a main expansion valve (main expansion means) 24, and an evaporator 25 in an annular shape by piping. In the present embodiment, a sub-accumulator 26 and a main accumulator 27 that perform gas-liquid separation are provided between the evaporator 25 and the compressor 21. The refrigerant circuit 2 is provided with a four-way valve 28 for switching between normal operation and defrost operation.

  In the present embodiment, the refrigeration cycle apparatus 1A constitutes a heating means of a hot water heating apparatus that uses hot water generated by the heating means for heating, and the condenser 22 exchanges heat between the refrigerant and water. It is a heat exchanger that heats water. Specifically, a supply pipe 71 and a recovery pipe 72 are connected to the condenser 22. Water is supplied to the condenser 22 through the supply pipe 71, and water (hot water) heated by the condenser 22 is recovered in the recovery pipe 72. It has come to be collected through. The hot water collected by the collection pipe 72 is sent to a heater such as a radiator directly or via a hot water storage tank, and thereby heating is performed.

  The first bypass circuit 3 a branches from the refrigerant circuit 2 between the supercooling heat exchanger 23 and the main expansion valve 24, and passes through the secondary heat exchanger 23 b of the supercooling heat exchanger 23 and the evaporator 25. A refrigerant circuit 2 is connected between the compressors 21. In the present embodiment, the first bypass circuit 3 a is connected to the refrigerant circuit 2 between the accumulator 26 and the main accumulator 27. The first bypass circuit 3 a is provided with a bypass expansion valve (bypass expansion means) 31 on the upstream side of the supercooling heat exchanger 23.

  The second bypass circuit 3 b branches from the refrigerant circuit 2 between the condenser 22 and the supercooling heat exchanger 23, and passes through the evaporator part 42 and the flow rate adjustment valve 41, so that the supercooling heat exchanger 23. Connected to the refrigerant circuit 2 on the outlet side. Here, the junction point of the second bypass circuit 3b to the refrigerant circuit 2 is located between the branch point from the refrigerant circuit 2 of the first bypass circuit 3a and the supercooling heat exchanger 23.

  In the normal operation, the refrigerant discharged from the compressor 21 is sent to the condenser 22 via the four-way valve 28, and in the defrost operation, the refrigerant discharged from the compressor 21 is sent to the evaporator 25 via the four-way valve 28. It is done. In FIG. 1, the direction of refrigerant flow during normal operation is indicated by arrows.

  Regarding the refrigeration cycle apparatus configured as described above, the state change of the refrigerant in the normal operation will be described below. FIG. 2 shows a Mollier diagram (pressure-enthalpy diagram) of the refrigeration cycle apparatus according to the first embodiment of the present invention.

  The high-pressure gas refrigerant (point a in FIG. 2) discharged from the compressor 21 flows into the condenser 22 and heat-exchanges with water passing through the secondary side of the condenser 22 to heat the water. Dissipates heat and liquefies and condenses. The high-pressure liquid refrigerant flowing out from the condenser 22 (point b in FIG. 2) is branched into the supercooling heat exchanger 23 side and the evaporator 25 side on the inlet side of the supercooling heat exchanger 23.

  The refrigerant flowing through the refrigerant circuit 2 flows into the primary heat exchange section 23a on the supercooling heat exchanger 23 side, and is supercooled by the low-pressure refrigerant decompressed by the bypass expansion valve 31. And it branches to the main expansion valve 24 side and the bypass expansion valve 31 side at the outlet side of the supercooling heat exchanger 23. The high-pressure refrigerant that has flowed out from the primary heat exchange section 23a of the supercooling heat exchanger 23 and branched to the main expansion valve 24 side is decompressed and expanded by the main expansion valve 24 (point d in FIG. 2), and then evaporated. Flows into the vessel 25. The low-pressure two-phase refrigerant flowing into the evaporator 25 evaporates here and absorbs heat of vaporization from the air.

  On the other hand, on the inlet side of the supercooling heat exchanger 23, the high-pressure liquid refrigerant branched to the evaporator part 42 side flows into the evaporator part 42, and the inlet of the flow rate adjustment valve 41 by the flow rate adjustment valve 41. The supercooling degree on the side is adjusted to a flow rate that falls within a predetermined range. Here, the heat held by the high-pressure liquid refrigerant is dissipated to heat a part of the heat exchanging part constituting the evaporator 25, and the frost layer or ice adhering to the outer surface of the part 42 of the evaporator After the layers are melted and the refrigerant itself is supercooled, it joins the refrigerant circuit 2 at the outlet side of the supercooling heat exchanger 23 (point c in FIG. 2).

  On the outlet side of the supercooling heat exchanger 23, the high-pressure liquid refrigerant with increased supercooling, which is joined to the outlet side of the second bypass circuit 3b and the refrigerant circuit 2, is branched to the bypass expansion valve 31 side. After being decompressed and expanded (point e in FIG. 2), the refrigerant flows into the secondary heat exchange section 23b of the supercooling heat exchanger 23.

  The low-pressure two-phase refrigerant that has flowed into the secondary heat exchanger 23 b of the supercooling heat exchanger 23 is heated by the high-pressure liquid refrigerant that has flowed into the primary heat exchanger 23 a of the supercooling heat exchanger 23. Thereafter, the low-pressure refrigerant (point f in FIG. 2) flowing out from the secondary side heat exchanging portion 23b of the supercooling heat exchanger 23 merges with the low-pressure refrigerant (point g in FIG. 2) flowing out from the evaporator 25 (FIG. 2). 2), the air is sucked into the compressor 21 again.

  The refrigerant circuit 2 includes a first temperature sensor 61 that detects a refrigerant temperature (discharge temperature) T1 on the discharge side of the compressor 21, and a refrigerant pressure (discharge) on the outlet side of the supercooling heat exchanger 23 in the refrigerant circuit 2. A pressure sensor 51 for detecting (pressure) P1 is provided.

The first bypass circuit 3a includes a second temperature sensor 62 for detecting the refrigerant temperatures T2 and T3 on the inlet side and the outlet side of the secondary heat exchanger 23b of the subcooling heat exchanger 23, and a third temperature. The sensor 63 is provided, and the second bypass circuit 3b is provided with a fourth temperature sensor 64 for detecting the refrigerant temperature T4 between the part 42 of the evaporator and the flow rate adjusting valve 41.

  In the present embodiment, the control device 4 opens the main expansion valve 24, the bypass expansion valve 31, and the flow rate adjustment valve based on detection values detected by the various sensors 51, 61, 62, 63 and 64. Control the degree.

  In the control device 4, during normal operation, the amount of refrigerant flowing through the main expansion valve 24 so that the refrigerant discharge temperature T1 on the discharge side of the compressor 21 detected by the first temperature sensor 61 is within a predetermined range. To control.

  In addition, the refrigerant temperature T2 at the inlet side of the secondary heat exchanger 23b of the supercooling heat exchanger is reduced to the low pressure two-phase state because the high pressure liquid refrigerant is depressurized by the bypass expansion valve 31. The temperature difference between the outlet side refrigerant temperature T3 and the inlet side refrigerant temperature T2 of the secondary side heat exchange part 23b of the supercooling heat exchanger is substantially equal to the secondary side heat to express the evaporation temperature Te in the secondary side heat exchange part 23b. It represents the refrigerant superheat degree SH at the outlet of the exchange unit 23b.

  However, when the refrigerant is in a two-phase state at the outlet of the secondary side heat exchange section 23b, the refrigerant superheat degree SH is substantially zero. The amount of refrigerant flowing through the bypass expansion valve 31 is controlled by the control device 4 so that the refrigerant superheat degree SH in the secondary heat exchange section 23b of the supercooling heat exchanger becomes a predetermined value.

  Furthermore, in the control device 4, the saturation temperature Tc based on the inlet refrigerant pressure Ph of the main expansion valve 24 detected by the pressure sensor 51, and the flow rate adjustment valve 41 detected by the fourth temperature sensor 64 in the second bypass circuit 3b. The amount of refrigerant flowing through the flow rate adjustment valve 41 is controlled so that the temperature difference from the refrigerant temperature T4 on the inlet side, that is, the refrigerant supercooling degree SC falls within a predetermined range.

  Next, the control device 4 during normal operation repeatedly performs opening control of the main expansion valve 24, the flow rate adjustment valve 41, and the bypass expansion valve 31, and will be described below with reference to the flowchart shown in FIG. This will be described in detail.

  First, the control device 4 controls the opening degree of the main expansion valve 24. That is, the discharge temperature sensor 61 detects the discharge temperature T1 (step S1), and the opening degree of the main expansion valve 24 is adjusted so that the discharge temperature T1 becomes a target value (step S2).

  Next, the control device 4 controls the opening degree of the flow rate adjustment valve 41. That is, the pressure sensor 51 detects the high pressure Ph, and the fourth temperature sensor 64 detects the inlet temperature T4 of the flow rate adjustment valve 41 (step S3). Furthermore, the control device 4 calculates the refrigerant saturation temperature Tc at the detected high pressure Ph (Step S4). The calculation of the refrigerant saturation temperature Tc is performed using a refrigerant physical property formula.

  Then, the control device 4 calculates the temperature difference between the refrigerant saturation temperature Tc at the high pressure Ph and the inlet side temperature T4 of the flow rate adjustment valve 41, that is, the refrigerant subcooling degree SC on the inlet side of the flow rate adjustment valve 41 ( Step S5), it is determined whether or not the refrigerant supercooling degree SC is between a preset lower limit SC1 and upper limit SC2 (Step S6).

When the refrigerant supercooling degree SC on the inlet side of the flow rate adjusting valve 41 is not between the lower limit value SC1 and the upper limit value SC2 (in the case of NO in step S6), the control device 4 uses the refrigerant supercooling degree SC and the lower limit value. The magnitude relationship of SC1 is compared (step S7). When the refrigerant supercooling degree SC is smaller than the lower limit SC1, the controller 4 reduces the flow rate of the refrigerant flowing by reducing the opening degree of the flow rate adjusting valve 41 by a predetermined amount (step S8). When it is larger than the upper limit value SC2, the controller 4 increases the flow rate of the refrigerant flowing by increasing the opening degree of the flow rate adjustment valve 41 by a predetermined amount (step S9), and the process proceeds to step S10.

  On the other hand, if YES in step S6, the opening degree of the flow rate adjustment valve 41 is considered to be appropriate, and the control device 4 proceeds to the next step S10.

  Finally, the control device 4 controls the opening degree of the bypass expansion valve 31. That is, the control device 4 detects the outlet-side refrigerant temperature T3 and the inlet-side refrigerant temperature T2 of the secondary heat exchanger 23b of the supercooling heat exchanger, and detects the temperature difference T3-T2, that is, the refrigerant superheat degree SH. Is calculated (step S10), and it is determined whether the refrigerant superheat degree SH is between a preset lower limit value SH1 and an upper limit value SH2 (step S11).

  When the refrigerant superheat degree SH is not between the lower limit value SH1 and the upper limit value SH2 (NO in step S11), the controller 4 compares the magnitude relationship between the refrigerant superheat degree SH and the lower limit value SH1 (step S12). ). When the refrigerant superheat degree SH is smaller than the lower limit value SH1, the controller 4 reduces the flow rate of the refrigerant flowing by lowering the opening degree of the bypass expansion valve 31 by a predetermined amount (step S13), and conversely, the refrigerant superheat degree SH is the upper limit value. When larger than SH2, the controller 4 increases the flow rate of the refrigerant flowing by increasing the opening degree of the bypass expansion valve 31 by a predetermined amount (step S14), and returns to step S1.

  On the other hand, if YES in step S11, it is considered that the opening degree of the bypass expansion valve 31 is appropriate. Therefore, the control device 4 ends the control of the bypass expansion valve 31, returns to step S1, and then returns to step S1. -The operation of step S14 is repeated.

  As described above, in the present embodiment, during normal operation, not the total refrigerant amount, but a part of the refrigerant (high-pressure liquid state) flows through the part 42 of the evaporator and dissipates the heat held by the refrigerant. Thus, it is possible to prevent a decrease in the heat absorption capability of the evaporator 25 while preventing the bottom of the evaporator part 42 from freezing.

  Further, the amount of refrigerant branched from the refrigerant circuit 2 and flowing into the evaporator part 42 can be finely controlled, that is, the flow rate is set so that the degree of supercooling on the outlet side of the second bypass circuit 3b is within a predetermined range. Since it can be controlled, the supercooling effect of the evaporator part 42 can be maximized.

  In addition, the refrigerant gas component that does not contribute to evaporation can be bypassed to the suction side of the compressor 21 via the first bypass circuit 3a while simultaneously increasing the refrigerant enthalpy change amount in the evaporator 25 by the first bypass circuit 3a. Thus, it is possible to suppress a meaningless increase in pressure loss in the evaporator 25, that is, to increase the suction pressure of the compressor 21, and to increase the refrigerant flow rate and the condensation (heating) capacity.

  In FIG. 1, the pressure sensor 51 is provided between the position where the refrigerant circuit 2 branches from the refrigerant circuit 2 to the first bypass circuit 3 a and the inlet side of the main expansion valve 24, but the pressure sensor 51 is discharged from the compressor 21. As long as it is between the main expansion valve 24 and the main expansion valve 24, it may be provided at any position in the refrigerant circuit 2. Alternatively, the pressure sensor 51 may be provided on the upstream side of the bypass expansion valve 31 of the first bypass circuit 3a or in the second bypass circuit 3b.

  In the second bypass circuit in FIG. 1, the position of the flow rate adjusting means 41 is installed on the downstream side of the evaporator part 24, but may be installed on the upstream side of the evaporator part 24. Good.

  Further, in FIG. 1, the junction point of the second bypass circuit 3b to the refrigerant circuit 2 is located between the branch point from the refrigerant circuit 2 of the first bypass circuit 3a and the supercooling heat exchanger 23. However, as shown in FIG. 4, it may be located between the branch position of the first bypass circuit 3 a and the bypass expansion valve 31.

(Embodiment 2)
FIG. 5 shows a refrigeration cycle apparatus 1B according to the second embodiment of the present invention. In the present embodiment, the same components as those in the first embodiment are denoted by the same reference numerals, and the description thereof is omitted.

  In this embodiment, the basic configuration is the same as that of the first embodiment, but the installation of the temperature sensor and the control device 4 associated therewith are different. That is, the pressure sensor 51 for detecting the high pressure Ph provided in the refrigerant circuit 2 of the first embodiment is not necessary, and a part of the evaporator is used in the second bypass circuit 3b of the first embodiment. In order to detect the refrigerant evaporation temperature Te of the evaporator 25 in place of the fourth temperature sensor 64 for detecting the refrigerant temperature T4 provided between the valve 42 and the flow rate adjustment valve 41, the main expansion valve 24 and the evaporation In order to detect the 5th temperature sensor 65 and the outside temperature To between the containers 25, the outside temperature sensor 71 is provided.

  As the temperature sensor is installed differently, the control device 4 has a predetermined temperature at least one of the outside air temperature To detected by the outside air temperature sensor 71 and the evaporation temperature Te detected by the fifth temperature sensor 65 during normal operation. In the following cases, the amount of refrigerant flowing through the flow rate adjustment valve 41 is increased, and when at least one of the outside air temperature To and the evaporation temperature Te is equal to or higher than a predetermined temperature, the amount of refrigerant flowing through the flow rate adjustment valve 41 is decreased. Is different from the control device 4 in the first embodiment.

  Next, the control of the control device 4 during normal operation will be described in detail with reference to the flowchart shown in FIG.

  First, in the control device 4, the opening degree control of the main expansion valve 24 is the same as that in the control device 4, and thus the description thereof is omitted.

  Next, the control device 4 differs from the control device 4 in the degree of opening control of the flow rate adjustment valve 41. That is, the opening degree control of the flow rate adjustment valve 41 is not performed by detecting the refrigerant supercooling degree SC on the inlet side of the flow rate adjustment valve 41, but is evaporated by the outside temperature sensor 71 and the fifth temperature sensor 65. The temperature Te is detected (step S21). Then, the control device 4 determines the magnitude relationship between the outside air temperature To and the predetermined outside air temperature To1, and determines the magnitude relationship between the evaporation temperature Te and the predetermined evaporation temperature Te1 (step S22).

  When the outside air temperature To is lower than the predetermined outside air temperature To1, or when the evaporating temperature Te is lower than the predetermined evaporating temperature Te1 (in the case of YES at step S22), the controller 4 controls the opening degree of the flow rate adjusting valve 41. Increase the flow rate of refrigerant flowing by a predetermined amount (step S23). If NO in step S22, the control device 4 determines the magnitude relationship between the outside air temperature To and the predetermined outside air temperature To1, and determines the magnitude relationship between the evaporation temperature Te and the predetermined evaporation temperature Te1 (step S24).

  When the outside air temperature To is higher than the predetermined outside air temperature To1, or when the evaporating temperature Te is higher than the predetermined evaporating temperature Te1 (in the case of YES in step S24), the controller 4 controls the opening degree of the flow rate adjustment valve 41. The flow rate of refrigerant flowing by lowering the predetermined amount is decreased (step S25).

  Subsequent opening degree control of the bypass expansion valve 31 is the same as that of the control device 4, and the operations of steps S1 to S2, S22 to S25, and S10 to S14 are repeated.

  As described above, in the present embodiment, during normal operation, the magnitude of the heating operation load is detected from the outside air temperature 71 and the evaporation temperature 65, and when the heating operation load is large, a freezing phenomenon occurs in the evaporator 25. Therefore, it is possible to prevent freezing by increasing the flow rate of the refrigerant (high-pressure liquid state) flowing through the part 42 of the evaporator to increase the heat radiation amount at the bottom of the part 42 of the evaporator.

  Conversely, when the heating operation load is small, the freezing phenomenon in the evaporator 25 is less likely to occur, so the flow rate of the refrigerant (high-pressure liquid state) flowing through part of the evaporator 42 is reduced, and the heat absorption in the evaporator 25 is reduced. Capability reduction can be prevented.

  The present invention is particularly useful for a hot water heating apparatus in which water is heated by a refrigeration cycle apparatus and the water is used for heating.

1A, 1B Refrigeration cycle device 2 Refrigerant circuit 4 Control device 21 Compressor 22 Condenser 23 Supercooling heat exchanger 24 Main expansion valve (main expansion means)
25 Evaporator 3a First bypass circuit 3b Second bypass circuit 31 Bypass expansion valve (bypass expansion means)
41 Flow control valve (flow control means)
51 Pressure sensor (condensation temperature detection means)
64 Fourth temperature sensor 65 Fifth temperature sensor 71 Outside air temperature sensor

Claims (4)

A refrigerant circuit formed by sequentially connecting a compressor, a condenser, a supercooling heat exchanger, a main expansion means, and an evaporator, and a control device, and between the supercooling heat exchanger and the main expansion means Branching, bypass expansion means, branching from between the first bypass circuit connected to the suction side of the compressor via the supercooling heat exchanger, between the condenser and the supercooling heat exchanger, A refrigeration cycle apparatus comprising: a flow rate adjusting means; and a second bypass circuit connected to the inlet side of the main expansion means via the evaporator. A temperature sensor for detecting a refrigerant temperature on the outlet side of the second bypass circuit; and a condensation temperature detecting means for detecting a condensation temperature, wherein the refrigerant temperature on the outlet side of the second bypass circuit and the condensation of the supercooling heat exchanger are provided. The refrigeration cycle apparatus according to claim 1, wherein the amount of refrigerant flowing through the flow rate adjusting means is adjusted so that the temperature difference from the temperature is within a predetermined range. An outside air temperature sensor that detects an outside air temperature; and an evaporator temperature sensor that detects an evaporation temperature of the pre-evaporator, the outside air temperature detected by the outside air temperature sensor, and the evaporation temperature detected by the evaporator temperature sensor. When at least one of them is equal to or lower than a predetermined temperature, the amount of refrigerant flowing through the flow rate adjusting means is increased, and at least one of the outside air temperature detected by the outside air temperature sensor and the evaporation temperature detected by the evaporator temperature sensor is a predetermined temperature. 2. The refrigeration cycle apparatus according to claim 1, wherein in the above case, the amount of refrigerant flowing through the flow rate adjusting means is reduced. The hot water heating apparatus which heats warm water with the condenser of the refrigerating-cycle apparatus of any one of Claims 1-3.