JP4254532B2 - Heat pump type water heater - Google Patents

Description

  The present invention relates to a heat pump hot water supply apparatus.

  The heat pump type hot water supply apparatus includes a heat pump unit in which a compressor, a water heat exchanger, a pressure reducing mechanism, and an air heat exchanger are sequentially connected, and unheated water is supplied to a heat exchange path constituted by the water heat exchanger. Some have a boiling operation that supplies and heats the unheated water (for example, see Patent Document 1). That is, as shown in FIG. 5, a tank unit 51 having a hot water storage tank 50 and a heat pump unit 53 having a refrigeration cycle 52 are provided. The refrigeration cycle 52 is configured by sequentially connecting a compressor 54, a water heat exchanger 55, a decompression mechanism (electric valve) 56, and an air heat exchanger 57. The tank unit 51 includes the hot water storage tank 50 and a circulation path 60 in which a circulation pump 58 and a heat exchange path 59 are interposed. In this case, the heat exchange path 59 can be configured by the water heat exchanger 55.

In the heat pump hot water supply apparatus, when the compressor 54 of the refrigeration cycle 52 is driven and the circulation pump 58 of the circulation path 60 is driven, the hot water storage tank 50 is not connected to the intake port provided at the bottom of the hot water storage tank 50. Heated water flows out into the circulation path 60, and this flows through the heat exchange path 59. At this time, unheated water is heated (boiled up) by the water heat exchanger 55 and returned to the hot water storage tank 50 from the hot water inlet provided at the upper part of the hot water storage tank 50. As a result, hot water is stored in the hot water storage tank 50.
JP 2002-139257 A (FIG. 1)

  However, in recent years, a natural refrigerant such as carbon dioxide gas may be used as the refrigerant of the refrigeration cycle 52 in consideration of the natural environment. For this reason, the Mollier diagram when using refrigerants such as HCFC and HFC is as shown in FIG. 4B, whereas the Mollier diagram when using carbon dioxide (CO2) is as shown in FIG. It becomes like this. At this time, in the class of the same capacity, the refrigerant circulation rate is almost the same (for example, 70 kg / h in the 4500 W class). However, if a carbon dioxide refrigerant is used, the differential pressure before and after the motor-operated valve increases, so that the motor valve having the same diameter as that used for a normal refrigerant increases the amount of refrigerant circulation and cannot be adjusted. That is, when a carbon dioxide refrigerant is used, the diameter of the motor-operated valve needs to be smaller than when a normal refrigerant is used. As described above, if the aperture of the motor-operated valve is reduced, noise (refrigerant sound) generated when the refrigerant passes through the motor-operated valve increases.

  Moreover, in the said heat pump type hot-water supply apparatus, in order to remove the frost adhering to an air heat exchanger, the defrost operation which makes an electrically operated valve an open state (fully opened state) may be performed. In such operation, an increase in flow velocity due to a decrease in refrigerant density at the inlet of the motor-operated valve generated a louder refrigerant sound than in normal boiling operation. That is, in the middle of operation from the start of the defrosting operation, the frost is removed by applying heat to the frost of the air heat exchanger, but in the final stage of the defrosting operation, the frost is almost melted, so the overheating operation is gradually performed. It becomes a state. For this reason, the inlet temperature of the electric valve rises. If the inlet temperature of the motor-operated valve increases, the refrigerant density will decrease, increasing the flow velocity and increasing the refrigerant passing sound.

  Furthermore, a fan is attached to the air heat exchanger for capacity adjustment. However, when frost is formed on the air heat exchanger, the air resistance of the blast when passing through the air heat exchanger increases, and a large noise is generated.

  The present invention has been made to solve the above-described conventional drawbacks, and an object thereof is to provide a heat pump type hot water supply apparatus that can achieve low noise and is optimal for operation at midnight or the like. .

The heat pump type hot water supply apparatus of claim 1 includes a heat pump unit 4 in which a compressor 13, a water heat exchanger 14, a decompression mechanism 15, and an air heat exchanger 16 are sequentially connected, and is configured by the water heat exchanger 14. A heat pump type hot water supply apparatus that is capable of a boiling operation for supplying unheated water to the heat exchange path 11 and heating the unheated water. the valve 12 in the open state from the water heat exchanger 15 allows the defrosting operation for supplying the refrigerant to the air heat exchanger 16, just before the defrosting completion of the defrosting operation, the frequency and above the compressor 13 It is characterized in that the flow rate of the refrigerant is reduced by reducing the opening degree of the motor-operated valve 12.

In the heat pump type hot water supply apparatus of the first aspect, immediately before the defrosting completion of defrosting operation, by reducing the opening degree of the frequency and the electric valve 12 of the compressor 13, it is possible to reduce the flow rate of the refrigerant.

The heat pump type hot water supply apparatus of claim 2 includes a heat pump unit 4 in which a compressor 13, a water heat exchanger 14, a decompression mechanism 15, and an air heat exchanger 16 are sequentially connected, and is configured by the water heat exchanger 16. A heat pump type hot water supply apparatus that is capable of a boiling operation for supplying unheated water to the heat exchange path 11 and heating the unheated water. The defrosting operation with the valve 12 in the open state is enabled, and immediately before the defrosting operation is started after frosting, the rotational speed of the fan 22 that blows air to the air heat exchanger 16 is set in the normal operation in the non-frosting state. It is characterized by lowering than.

In the heat pump type hot water supply apparatus according to the second aspect , immediately before the defrosting operation is started, the rotational speed of the fan 22 (fan that blows air to the air heat exchanger 16) is decreased as compared with the normal operation in the non-frosting state. Therefore, it is possible to achieve noise reduction due to fan blowing. That is, in the frosting state of the air heat exchanger 16, air resistance against blowing is increased due to frost, so that a large amount of noise is generated at a blowing amount as in normal operation. For this reason, the noise by fan ventilation can be reduced by reducing the rotation speed of the fan 22 before the defrosting operation.

The heat pump hot water supply apparatus according to claim 3 is characterized in that the high pressure side of the refrigeration cycle of the heat pump unit 4 is operated at a supercritical pressure.

In the heat pump hot water supply apparatus according to the third aspect , since the high pressure side operates at a supercritical pressure, a supercritical refrigerant used in a supercritical state is used as the refrigerant, and the heat pump unit 4 is friendly to the global environment. Further, since the high pressure side operates at a supercritical pressure, the pressure difference across the motor-operated valve 12 increases, so that the motor-operated valve 12 having a small diameter is used, and the refrigerant passes through the motor-operated valve 12. The sound is loud and the effects of claims 1 to 3 are particularly effectively exhibited.

According to the heat pump type hot water supply apparatus of claim 1 , the flow rate of the refrigerant is reduced by reducing the frequency of the compressor and the opening degree of the electric valve immediately before the end of frost removal in the defrosting operation. Thereby, the increase in the refrigerant | coolant sound from immediately before completion | finish of frost removal in a defrost operation can be prevented, and the noise at the time of a defrost operation can be reduced reliably. In addition, the control for reducing the noise is simple because the frequency of the compressor and the opening of the motor-operated valve may be reduced. For this reason, cost reduction can be achieved and the reliability of noise reduction is improved .

According to the heat pump type hot water supply apparatus of the second aspect , it is possible to reduce the noise caused by fan blowing by reducing the rotational speed of the fan 22 before the defrosting operation.

According to the heat pump hot water supply apparatus of claim 3 , a supercritical refrigerant used in a supercritical state is used as the refrigerant, and the heat pump unit is friendly to the global environment. In addition, since the high pressure side operates at supercritical pressure, the differential pressure before and after the motor-operated valve increases, so that the motor-operated valve has a small diameter, and the passing sound when the refrigerant passes through the motor-operated valve is large. The effects of claim 1 or claim 2 can be exhibited particularly effectively.

  Next, specific embodiments of the heat pump type hot water supply apparatus of the present invention will be described in detail with reference to the drawings. FIG. 1 is a simplified diagram of a heat pump type hot water supply apparatus. The heat pump hot water supply apparatus includes a tank unit 2 having a hot water storage tank 1 and a heat pump unit 4 having a refrigeration cycle 3. The hot water storage tank 1 of the tank unit 2 is provided with a water supply port 5 on its bottom wall and a hot water outlet 6 on its upper wall. Tap water is supplied from the water supply port 5 to the hot water storage tank 1, and hot hot water is discharged from the hot water outlet 6. In addition, the hot water storage tank 1 has a water intake 7 at the bottom wall and a hot water inlet 8 at the top of the side wall (peripheral wall), and the water intake 7 and the hot water inlet 8 are connected by a circulation path 9. Has been. The circulation path 9 is provided with a water circulation pump 10 and a heat exchange path 11. That is, when the water circulation pump 10 is driven, unheated water in the hot water storage tank 1 flows out from the water intake 7 to the circulation path 9 and returns to the hot water storage tank 1 from the hot water inlet 8 through the heat exchange path 11. .

  Next, the refrigeration cycle 3 is configured by sequentially connecting a compressor 13, a water heat exchanger 14 that constitutes the heat exchange path 11, a decompression mechanism 15, and an air heat exchanger 16. That is, the discharge port of the compressor 13 and the water heat exchanger 14 are connected by the refrigerant passage 17, the water heat exchanger 14 and the decompression mechanism 15 are connected by the refrigerant passage 18, and the heat exchange with the decompression mechanism 15 is performed. The heat exchanger 16 and the compressor 13 are connected by a refrigerant passage 21 in which an accumulator 20 is interposed. And as a refrigerant | coolant, natural refrigerant | coolants, such as a carbon dioxide gas which uses a high voltage | pressure side by a supercritical pressure, for example are used. The refrigerant passage 17 is provided with an HPS 23 as a pressure protection switch and a pressure sensor 24. Further, in this case, a motor-operated valve (electric expansion valve) 12 is used as the pressure reducing mechanism 15. The air heat exchanger 16 is provided with a fan 22 that adjusts the capacity of the air heat exchanger 16.

  The refrigeration cycle 3 includes a liquid gas heat exchanger 25 that cools the high-pressure refrigerant that has flowed out of the water heat exchanger 14. In this case, the liquid gas heat exchanger 25 has, for example, a double pipe structure, and the first passage 26 through which the refrigerant flowing out from the water heat exchanger 14 passes and the refrigerant flowing out from the air heat exchanger 16 pass through. And a second passage 27. That is, the first passage 26 constitutes a part of the refrigerant passage 18 that connects the water heat exchanger 14 and the decompression mechanism 15, and the second passage 27 connects the air heat exchanger 16 and the compressor 13. A part of the refrigerant passage 21 is configured. For this reason, heat exchange is performed between the high-temperature and high-pressure refrigerant passing through the first passage 26 and the low-temperature and low-pressure refrigerant passing through the second passage 27.

  Further, in the heat pump type hot water supply apparatus 4, refrigerant rectifying mufflers (silencers) 35 and 36 are disposed on the upstream side and the downstream side of the motor-operated valve 12, respectively. That is, the refrigerant can be rectified by the mufflers 35 and 36, so that the refrigerant flowing into the motor-operated valve 12 is rectified and the refrigerant flowing out of the motor-operated valve 12 is also rectified.

  Next, the operation (boiling operation) of this heat pump hot water supply device will be described. The compressor 13 is driven and the water circulation pump 10 is driven (actuated). Then, stored water (hot water) flows out from the water intake 7 provided at the bottom of the hot water storage tank 1, and this flows through the heat exchange path 11 of the circulation path 9. Further, the refrigerant discharged from the compressor 13 returns to the compressor 13 via the water heat exchanger 14, the electric valve 12 as the pressure reducing mechanism 15, and the air heat exchanger 16 in order. Therefore, the water flowing through the heat exchange path 11 of the circulation path 9 is heated (boiling) by the water heat exchanger 14 that is a gas cooler, and returned to the upper part of the hot water storage tank 1 from the hot water inlet 8. By continuously performing such an operation, hot hot water is stored in the hot water storage tank 1. In the current power rate system, the unit price of the nighttime power rate is set lower than in the daytime. Therefore, it is preferable to perform this operation in a low-night time zone to reduce costs.

  The heat pump hot water supply apparatus is a liquid gas heat exchanger 25 that performs heat exchange between the high-pressure refrigerant that flows out of the water heat exchanger 14 and flows into the decompression mechanism 15 and the low-pressure refrigerant that flows out of the air heat exchanger 16. Therefore, the refrigerant from the water heat exchanger (gas cooler) 14 can be supercooled and the refrigerant entering the compressor 13 can be heated. For this reason, wet compression of the compressor 13 can be prevented, and stable operation is possible.

  In addition, the heat pump type hot water supply device includes a temperature sensor (incoming thermistor) 30 that detects a temperature upstream of the heat exchange path 11 of the circulation path 9 and a temperature downstream of the heat exchange path 11 of the circulation path 9. A temperature sensor (hot water thermistor) 31 to detect, a temperature sensor (air heat exchanger thermistor) 32 to detect the temperature of the air heat exchanger 16, a temperature sensor (discharge pipe thermistor) 33 to detect the discharge temperature of the compressor 13, A temperature sensor (outside air temperature thermistor) 34 for detecting the outside air temperature is provided. Data (detected temperature) from these sensors is input to a control unit (not shown) of the heat pump type hot water supply apparatus (for example, composed of a microcomputer or the like), and various controls are performed based on these data. Done.

  That is, during operation of the heat pump type hot water supply device, for example, the temperature of the discharge pipe is detected by the discharge pipe thermistor 33, and the opening degree of the motor-operated valve 12 is adjusted (controlled) so that the discharge pipe temperature becomes the target discharge pipe temperature. )can do. Further, if the temperature of the incoming water thermistor 30 is equal to or higher than a predetermined temperature (for example, 60 ° C.), the operation is stopped because the hot water in the hot water storage tank 1 is boiling, or based on the temperature of the outside air temperature thermistor 34, The operating frequency of the compressor 13 can be controlled to adjust the hot water heating capacity (boiling capacity) or the like.

  By the way, when frost adheres to the air heat exchanger 16, a defrosting operation for removing the frost is performed. Here, the defrosting operation is an operation that heats the frost of the air heat exchanger 16 with the motor-operated valve 12 in an open state (fully open state), for example. At this time, from the start of the defrosting operation in which frost adheres to the air heat exchanger 16 to the middle of the defrosting operation, a cycle as shown in FIG. 2A can be formed to remove the frost. it can. However, in the final stage of the defrosting operation in which the frost is almost melted, the frost is almost melted, so as shown in FIG. The temperature rises. That is, the outlet temperature of the liquid gas heat exchanger 25 (the inlet temperature of the motor-operated valve 12) is increased, and therefore the refrigerant density at the inlet of the motor-operated valve 12 is reduced, the refrigerant flow rate is increased, and the refrigerant passing sound is generated. growing.

  Therefore, at the end of the defrosting operation, for example, if the temperature of the air heat exchanger 16 becomes equal to or higher than a predetermined temperature (for example, 3 ° C.) during the defrosting operation, the frequency of the compressor 13 and the opening of the motor operated valve 12 are decreased. . That is, if the temperature of the air heat exchanger 16 becomes equal to or higher than a predetermined temperature (for example, 3 ° C.) during the defrosting operation, the frost of the air heat exchanger 16 is almost melted. For example, if the frequency of the compressor 13 is about 70 Hz and the opening degree of the motor-operated valve 12 is about 480 pulses, the frequency of the compressor 13 is about 60-64 Hz and the motor-operated valve 12 is up to the middle of the frost operation. Is set to about 380 pulses to 400 pulses. In this way, even if the frequency of the compressor 13 and the opening degree of the motor-operated valve 12 are reduced, the defrosting operation is not affected because it is the final stage of the defrosting operation in a state where the frost is almost melted.

  Thus, the flow rate of the refrigerant can be reduced by reducing the frequency of the compressor 13 and the opening degree of the motor-operated valve 12. As a result, it is possible to prevent an increase in refrigerant circulation sound that occurs immediately before the end of frost removal in the defrosting operation, and to reliably reduce noise during the defrosting operation. The start of the defrosting operation can be determined based on data such as the temperature of the air heat exchanger 16, the outside air temperature, and the time from the start of operation (operation time), for example.

  The air heat exchanger 16 is blown from a fan 22 for capacity adjustment. However, when frost adheres to the air heat exchanger 16, the air resistance against blowing is increased due to the frost, so that a large amount of noise is generated at the blowing amount during normal operation. For this reason, in this heat pump type hot water supply device, the noise due to fan blowing is reduced by reducing the rotational speed of the fan immediately before the defrosting operation is started in the frosting state. By the way, immediately before the start of the defrosting operation (when the rotational speed of the fan is decreased), for example, after the previous defrosting operation is completed, the boiling operation time has elapsed for a predetermined time (for example, 15 minutes) or more. In addition, it is assumed that the temperature of the air heat exchanger 16 is lower than a temperature lower than the outside air temperature by a predetermined temperature (for example, 8 ° C.).

  In this case, in normal control, as shown in FIG. 3B, if the fan rotation speed is 660 (rpm) in the boiling operation not performing the defrosting operation, the defrosting operation is started. However, the rotational speed remains the same. For this reason, if the operating sound is, for example, 38 dBA, the air resistance against the air blowing increases due to frost, so this operating sound gradually increases, and becomes about 43 dBA, for example, when the defrosting operation starts. Therefore, in this heat pump type hot water supply apparatus, if the fan rotation speed is 660 (rpm) in the boiling operation without performing the defrosting operation, as shown in FIG. 3 (a) immediately before entering the defrosting operation. The fan rotation speed is reduced to, for example, 560 (rpm), and the defrosting operation is started. For this reason, a driving sound can be maintained at about 38 dBA, for example. In this case, the upper limit of the fan speed is set. That is, the upper limit value of the rotational speed to be reduced is set to, for example, about 80% of the upper limit value of the frequency during normal operation (boiling operation).

  By the way, if a refrigerant that is not carbon dioxide (a refrigerant that is not a supercritical refrigerant), for example, an HCFC or HFC refrigerant, is used as the refrigerant, the Mollier diagram becomes a graph as shown in FIG. On the other hand, if a supercritical refrigerant is used, the Mollier diagram becomes a graph as shown in FIG. For this reason, when the refrigerant that is not the supercritical refrigerant is used and when the supercritical refrigerant is used, the refrigerant circulation amount is almost the same (for example, 70 kg / h in the 4500 W class) in the same capacity class. However, if a carbon dioxide (CO2) refrigerant is used, the differential pressure across the motor-operated valve 12 increases, and the motor valve 12 having the same diameter as that used for a normal refrigerant increases the amount of refrigerant circulation and cannot be adjusted. That is, when using carbon dioxide refrigerant, it is necessary to make the diameter of the motor-operated valve 12 smaller than when using a normal refrigerant. However, if the diameter of the motor-operated valve 12 is reduced, noise (refrigerant sound) generated when the refrigerant passes through the motor-operated valve 12 increases.

  Therefore, in the heat pump type hot water supply apparatus, refrigerant rectifying mufflers (silencers) 35 and 36 are arranged on the upstream side and the downstream side of the motor-operated valve 12, respectively, and the refrigerant is rectified by the mufflers 35 and 36. I am doing so. For this reason, the refrigerant flowing into the motor-operated valve 12 is rectified, and the refrigerant flowing out of the motor-operated valve 12 is also rectified. For this reason, the fall of the refrigerant | coolant passage sound in the motor operated valve 12 can be achieved. As a result, the refrigerant sound generated in the heat pump unit 4 (the sound generated when the refrigerant flows) can be reduced as a whole, and the heat pump hot water supply apparatus is low in noise and optimal for performing midnight operation. In other words, since the current power rate system is set to have a lower unit price for power consumption at night (midnight) than in the daytime, it is possible to reduce the cost by operating in the low-night time zone.

  Moreover, in the heat pump type hot water supply apparatus, the flow rate of the refrigerant is reduced by reducing the frequency of the compressor 13 and the opening degree of the motor-operated valve 12 immediately before the end of frost removal in the defrosting operation. Thereby, the increase in the refrigerant | coolant sound from immediately before completion | finish of frost removal in a defrost operation can be prevented, and the noise at the time of a defrost operation can be reduced reliably. Moreover, the control for reducing the noise is simple because the frequency of the compressor 13 and the opening of the motor-operated valve 12 may be reduced. For this reason, cost reduction can be achieved and the reliability of noise reduction is improved. In particular, as in this embodiment, immediately before the end of frost removal in the defrosting operation, noise reduction by reducing the frequency of the compressor 13 and the opening degree of the motorized valve 12, and the upstream side of the motorized valve 12; If the noise reduction by disposing the refrigerant rectifying mufflers 35 and 36 on the downstream side is combined, further reduction of the refrigerant noise can be achieved, and an extremely quiet defrosting operation can be performed.

  Further, immediately before the start of the defrosting operation, the rotational speed of the fan 22 (fan that blows air to the air heat exchanger 16) is reduced as compared with the normal operation in the non-frosting state, so that the noise caused by fan blowing can be reduced. Can be achieved. That is, in the frosting state of the air heat exchanger 16, air resistance against blowing is increased due to frost, so that a large amount of noise is generated at a blowing amount as in normal operation. For this reason, as shown to Fig.3 (a), by reducing the rotation speed of the fan 22 before a defrost operation (defrost entry), the reduction of the noise by the fan ventilation of this reduced part B is aimed at. be able to.

  In addition, since a supercritical refrigerant used supercritically is used as the refrigerant, the heat pump unit is friendly to the global environment. In particular, since the high pressure side operates at a supercritical pressure, the differential pressure before and after the motor-operated valve increases, so that the motor-operated valve 12 having a small diameter is used, and the passing sound when the refrigerant passes through the motor-operated valve 12. As described above, the refrigerant rectifying mufflers 35 and 36 are arranged on the upstream side and the downstream side of the motor-operated valve 12, so that noise reduction can be reliably achieved.

  Although specific embodiments of the present invention have been described above, the present invention is not limited to the above embodiments, and various modifications can be made within the scope of the present invention. For example, in the above embodiment, the hot water storage tank 1 is provided, but in normal boiling operation, unheated water flows into the heat exchange path 11 constituted by the water heat exchanger 14, and this Since the high temperature water is heated when flowing through the heat exchange path 11 and flows out of the heat exchange path 11, the hot water storage tank 1 may not be provided. Further, as the refrigerant rectifying mufflers 35 and 36 disposed on the upstream side and the downstream side of the motor-operated valve 12, existing mufflers that function as rectifiers can be used. And in the said embodiment, while providing the mufflers 35 and 36, the opening degree of the motor operated valve 12 etc. are reduced in the last stage of a defrost operation, Furthermore, the rotation speed of the fan 22 is reduced just before entering a defrost operation. However, when the mufflers 35 and 36 are provided, the rotational speed of the fan 22 is decreased immediately before entering the control or the defrosting operation in which the opening degree of the motor operated valve 12 is decreased at the end of the defrosting operation. You may not perform control. That is, noise reduction by reducing the opening degree of the motor-operated valve 12 at the end of the defrosting operation, noise reduction by reducing the rotational speed of the fan 22 immediately before entering the defrosting operation, and noise reduction by the mufflers 35 and 36 It is sufficient that at least one of the silencing can be achieved. As the refrigerant to be used, the refrigerant may be a supercritical refrigerant such as ethylene, ethane, or nitric oxide in addition to carbon dioxide gas. Furthermore, it is not a supercritical refrigerant but dichlorodifluoro. A refrigerant such as methane (R-12) or chlorodifluoromethane (R-22) may be used.

It is a simplified diagram showing an embodiment of a heat pump type hot water supply apparatus of the present invention. The Mollier diagram at the time of a defrost operation is shown, (a) is a graph from a defrost operation start to the middle stage of a defrost operation, (b) is a graph figure of a defrost operation end stage. The relationship between a fan rotation speed and a driving | running | working sound is shown, (a) is a graph figure at the time of reducing a fan rotation speed immediately before a defrost operation, (b) is a graph figure when not changing a fan rotation speed. It is. The Mollier diagram at the time of boiling operation is shown, (a) is a graph when carbon dioxide is used as the refrigerant, and (b) is a graph when HCFC or HFC is used as the refrigerant. It is a simplification figure of the conventional heat pump type hot-water supply apparatus.

Explanation of symbols

  4 .... Heat pump unit, 11 .... Heat exchange path, 12 .... Electric valve, 13 .... Compressor, 14 .... Water heat exchanger, 15 .... Pressure reduction mechanism, 16 .... Air heat exchanger, 22 .... Fan, 35, 36 ・ ・ Muffler for refrigerant rectification

Claims (3)

A heat pump unit (4) in which a compressor (13), a water heat exchanger (14), a pressure reducing mechanism (15), and an air heat exchanger (16) are sequentially connected is provided, and the water heat exchanger (14) A heat pump type hot water supply apparatus capable of a boiling operation for supplying unheated water to a configured heat exchange path (11) and heating the unheated water, wherein the pressure reducing mechanism (15) is a motor operated valve (12). together constitute at, to enable the defrosting operation for supplying the refrigerant from the electric valve (12) in the open state water heat exchanger (15) air heat exchanger (16), frost in the defrosting operation Immediately before the end of the removal, the heat pump hot water supply apparatus reduces the flow rate of the refrigerant by reducing the frequency of the compressor (13) and the opening of the motor operated valve (12). A heat pump unit (4) in which a compressor (13), a water heat exchanger (14), a pressure reducing mechanism (15), and an air heat exchanger (16) are sequentially connected is provided, and the water heat exchanger (14) A heat pump type hot water supply apparatus capable of a boiling operation for supplying unheated water to a configured heat exchange path (11) and heating the unheated water, wherein the pressure reducing mechanism (15) is a motor operated valve (12). And a fan that blows air to the air heat exchanger (16) immediately before the defrosting operation is started by frosting and the motorized valve (12) is opened. The heat pump type hot water supply apparatus characterized in that the rotational speed of 22) is reduced as compared with the normal operation in a non-frosting state. The heat pump hot water supply apparatus according to claim 1 or 2 , wherein the high pressure side of the refrigeration cycle (3) of the heat pump unit (4) is operated at a supercritical pressure.