JP4254532B2 - Heat pump type water heater - Google Patents
Heat pump type water heater Download PDFInfo
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- JP4254532B2 JP4254532B2 JP2003432417A JP2003432417A JP4254532B2 JP 4254532 B2 JP4254532 B2 JP 4254532B2 JP 2003432417 A JP2003432417 A JP 2003432417A JP 2003432417 A JP2003432417 A JP 2003432417A JP 4254532 B2 JP4254532 B2 JP 4254532B2
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- Prior art keywords
- heat exchanger
- refrigerant
- heat pump
- hot water
- supply apparatus
- Prior art date
- Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
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- XLYOFNOQVPJJNP-UHFFFAOYSA-N water Substances O XLYOFNOQVPJJNP-UHFFFAOYSA-N 0.000 title claims description 125
- 239000003507 refrigerant Substances 0.000 claims description 96
- 238000010257 thawing Methods 0.000 claims description 46
- 238000009835 boiling Methods 0.000 claims description 16
- 238000005057 refrigeration Methods 0.000 claims description 9
- 238000010438 heat treatment Methods 0.000 claims description 5
- CURLTUGMZLYLDI-UHFFFAOYSA-N Carbon dioxide Chemical compound O=C=O CURLTUGMZLYLDI-UHFFFAOYSA-N 0.000 description 24
- 229910002092 carbon dioxide Inorganic materials 0.000 description 12
- 239000001569 carbon dioxide Substances 0.000 description 12
- 238000007664 blowing Methods 0.000 description 11
- 230000006837 decompression Effects 0.000 description 8
- 238000010586 diagram Methods 0.000 description 8
- 238000011144 upstream manufacturing Methods 0.000 description 6
- 239000002826 coolant Substances 0.000 description 5
- 230000003247 decreasing effect Effects 0.000 description 5
- 239000007788 liquid Substances 0.000 description 4
- VNWKTOKETHGBQD-UHFFFAOYSA-N methane Chemical compound C VNWKTOKETHGBQD-UHFFFAOYSA-N 0.000 description 3
- VOPWNXZWBYDODV-UHFFFAOYSA-N Chlorodifluoromethane Chemical compound FC(F)Cl VOPWNXZWBYDODV-UHFFFAOYSA-N 0.000 description 2
- MWUXSHHQAYIFBG-UHFFFAOYSA-N Nitric oxide Chemical compound O=[N] MWUXSHHQAYIFBG-UHFFFAOYSA-N 0.000 description 2
- 230000000694 effects Effects 0.000 description 2
- 238000009423 ventilation Methods 0.000 description 2
- OTMSDBZUPAUEDD-UHFFFAOYSA-N Ethane Chemical compound CC OTMSDBZUPAUEDD-UHFFFAOYSA-N 0.000 description 1
- VGGSQFUCUMXWEO-UHFFFAOYSA-N Ethene Chemical compound C=C VGGSQFUCUMXWEO-UHFFFAOYSA-N 0.000 description 1
- 239000005977 Ethylene Substances 0.000 description 1
- 230000006835 compression Effects 0.000 description 1
- 238000007906 compression Methods 0.000 description 1
- 230000030279 gene silencing Effects 0.000 description 1
- 238000012986 modification Methods 0.000 description 1
- 230000004048 modification Effects 0.000 description 1
- 238000013021 overheating Methods 0.000 description 1
- 230000002093 peripheral effect Effects 0.000 description 1
- 239000008399 tap water Substances 0.000 description 1
- 235000020679 tap water Nutrition 0.000 description 1
Classifications
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
- F25B2309/00—Gas cycle refrigeration machines
- F25B2309/06—Compression machines, plants or systems characterised by the refrigerant being carbon dioxide
- F25B2309/061—Compression machines, plants or systems characterised by the refrigerant being carbon dioxide with cycle highest pressure above the supercritical pressure
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
- F25B9/00—Compression machines, plants or systems, in which the refrigerant is air or other gas of low boiling point
- F25B9/002—Compression machines, plants or systems, in which the refrigerant is air or other gas of low boiling point characterised by the refrigerant
- F25B9/008—Compression machines, plants or systems, in which the refrigerant is air or other gas of low boiling point characterised by the refrigerant the refrigerant being carbon dioxide
Landscapes
- Other Air-Conditioning Systems (AREA)
- Heat-Pump Type And Storage Water Heaters (AREA)
Description
この発明は、ヒートポンプ式給湯装置に関するものである。 The present invention relates to a heat pump hot water supply apparatus.
ヒートポンプ式給湯装置には、圧縮機と水熱交換器と減圧機構と空気熱交換器とを順次接続したヒートポンプユニットを備え、上記水熱交換器にて構成される熱交換路に未加熱水を供給してこの未加熱水を加熱する沸上運転が可能なものがある（例えば、特許文献１参照）。すなわち、図５に示すように、貯湯タンク５０を有するタンクユニット５１と、冷凍サイクル５２を有するヒートポンプユニット５３とを備える。そして、冷凍サイクル５２は、圧縮機５４と水熱交換器５５と減圧機構（電動弁）５６と空気熱交換器５７とを順次接続して構成される。また、タンクユニット５１は、上記貯湯タンク５０と、循環用ポンプ５８と熱交換路５９とが介設された循環路６０とを備える。この場合、熱交換路５９は上記水熱交換器５５にて構成することができる。 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.
そして、上記ヒートポンプ式給湯装置では、冷凍サイクル５２の圧縮機５４を駆動すると共に、循環路６０の循環用ポンプ５８を駆動すると、貯湯タンク５０の底部に設けられた取水口から貯湯タンク５０の未加熱水が循環路６０に流出し、これが熱交換路５９を流通する。この際、未加熱水が水熱交換器５５にて加熱され（沸き上げられ）、貯湯タンク５０の上部に設けられら湯入口からこの貯湯タンク５０に返流する。これによって、貯湯タンク５０に高温の湯を貯めるものである。
ところが、近年、冷凍サイクル５２の冷媒に、自然環境等を考慮して炭酸ガス等の自然冷媒を使用する場合がある。このため、ＨＣＦＣ、ＨＦＣ等の冷媒を使用した際のモリエル線図は図４（ｂ）のようになるに対し、炭酸ガス（ＣＯ２）を使用した際のモリエル線図は図４（ａ）のようになる。この際、同一能力のクラスにおいては、冷媒循環量はほぼ同一である（例えば、４５００Ｗクラスで７０ｋｇ／ｈ）。しかしながら、炭酸ガスの冷媒を使用すれば、電動弁前後の差圧が大きくなるため通常の冷媒に使用したものと同一口径の電動弁では冷媒循環量が多くなるため調節できない。すなわち、炭酸ガスの冷媒を使用する場合、電動弁の口径を通常の冷媒を使用するときよりも小さくする必要がある。このように、電動弁の口径を小さくすれば、この電動弁を冷媒が通過する際に発生する騒音（冷媒音）が大きくなっていた。 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.
また、上記ヒートポンプ式給湯装置においては、空気熱交換器に付着した霜を除去するために、電動弁を開状態（全開状態）とする除霜運転を行う場合がある。このよう運転では、電動弁の入口の冷媒密度の低下による流速増加で、通常の沸上運転時よりも大きな冷媒音が発生していた。すなわち、除霜運転開始から運転中盤では、空気熱交換器の霜に熱を与えることによって、霜が除去されていくが、除霜運転終盤においては、霜がほとんど融けているので、次第に過熱運転状態となる。このため、電動弁の入口温度が上昇する。電動弁の入口温度が高くなれば、冷媒密度の低下することになって、流速があがり冷媒通過音が増大する。 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.
さらに、空気熱交換器には能力調整のためにファンが付設されている。しかしながら、空気熱交換器に霜が付くと、空気熱交換器を通過する際の送風の空気抵抗が大きくなり、大きな騒音が発生していた。 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.
この発明は、上記従来の欠点を解決するためになされたものであって、その目的は、低騒音化を達成できて、深夜等の運転に最適となるヒートポンプ式給湯装置を提供することにある。 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. .
請求項１のヒートポンプ式給湯装置は、圧縮機１３と水熱交換器１４と減圧機構１５と空気熱交換器１６とを順次接続したヒートポンプユニット４を備え、上記水熱交換器１４にて構成される熱交換路１１に未加熱水を供給してこの未加熱水を加熱する沸上運転が可能なヒートポンプ式給湯装置であって、上記減圧機構１５を電動弁１２にて構成すると共に、この電動弁１２を開状態として水熱交換器１５から空気熱交換器１６へと冷媒を供給する除霜運転を可能とし、除霜運転における霜除去終了の直前に、上記圧縮機１３の周波数及び上記電動弁１２の開度を低下させることによって冷媒の流速を低下させることを特徴としている。
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.
上記請求項１のヒートポンプ式給湯装置では、除霜運転における霜除去終了の直前に、圧縮機１３の周波数及び電動弁１２の開度を低下させることによって、冷媒の流速を低下させることができる。
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.
請求項２のヒートポンプ式給湯装置は、圧縮機１３と水熱交換器１４と減圧機構１５と空気熱交換器１６とを順次接続したヒートポンプユニット４を備え、上記水熱交換器１６にて構成される熱交換路１１に未加熱水を供給してこの未加熱水を加熱する沸上運転が可能なヒートポンプ式給湯装置であって、上記減圧機構１６を電動弁１２にて構成すると共に、この電動弁１２を開状態とした除霜運転を可能とし、着霜して除霜運転が開始される直前において、空気熱交換器１６に送風するファン２２の回転数を非着霜状態の通常運転時よりも低下させることを特徴としている。
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.
上記請求項２のヒートポンプ式給湯装置では、除霜運転が開始される直前において、非着霜状態の通常運転時よりもファン２２（空気熱交換器１６に送風するファン）の回転数を低下させるので、ファン送風による騒音の低減を達成できる。すなわち、空気熱交換器１６の着霜状態においては、霜のために送風に対する空気抵抗が大きくなるので、通常運転時のような送風量では、大きな騒音が生じていた。このため、除霜運転前においてファン２２の回転数を低下させることによって、ファン送風による騒音の低減を図ることができる。
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.
請求項３のヒートポンプ式給湯装置は、上記ヒートポンプユニット４の冷凍サイクルの高圧側が超臨界圧力で運転することを特徴としている。 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.
請求項３のヒートポンプ式給湯装置では、高圧側が超臨界圧力で運転するものであるので、冷媒に超臨界で使用する超臨界冷媒を用いることになり、地球環境に優しいヒートポンプユニット４となる。また、高圧側が超臨界圧力で運転するので、電動弁１２前後の差圧が大きくなるため、電動弁１２を小さな口径のものを使用することになり、冷媒が電動弁１２を通過する際の通過音が大きく、上記請求項１から請求項３の作用を特に有効に発揮する。
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.
請求項１のヒートポンプ式給湯装置によれば、除霜運転における霜除去終了の直前に、圧縮機の周波数及び電動弁の開度を低下させることによって、冷媒の流速を低下させる。これにより、除霜運転における霜除去終了の直前からの冷媒音の増加を防止することができ、除霜運転時の騒音を確実に少なくすることができる。しかも、騒音を少なくするための制御としては、圧縮機の周波数及び電動弁の開度を低下させればよいので、簡単である。このため、コスト低減を達成できると共に、低騒音化の信頼性が向上する。
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 .
請求項２のヒートポンプ式給湯装置によれば、除霜運転前においてファン２２の回転数を低下させることによって、ファン送風による騒音の低減を図ることができる。
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.
請求項３のヒートポンプ式給湯装置によれば、冷媒に超臨界で使用する超臨界冷媒を用いることになり、地球環境に優しいヒートポンプユニットとなる。また、高圧側が超臨界圧力で運転するので、電動弁前後の差圧が大きくなるため、電動弁を小さな口径のものを使用することになり、冷媒が電動弁を通過する際の通過音が大きく、上記請求項１又は請求項２の作用効果を特に有効に発揮することができる。
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.
次に、この発明のヒートポンプ式給湯装置の具体的な実施の形態について、図面を参照しつつ詳細に説明する。図１はヒートポンプ式給湯装置の簡略図である。このヒートポンプ式給湯装置は、貯湯タンク１を有するタンクユニット２と、冷凍サイクル３を有するヒートポンプユニット４とを備える。そして、タンクユニット２の貯湯タンク１には、その底壁に給水口５が設けられると共に、その上壁に出湯口６が設けられている。この給水口５から貯湯タンク１に水道水が供給され、出湯口６から高温の温湯が出湯される。また、貯湯タンク１には、その底壁に取水口７が開設されると共に、側壁（周壁）の上部に湯入口８が開設され、取水口７と湯入口８とが循環路９にて連結されている。そして、この循環路９に水循環用ポンプ１０と熱交換路１１とが介設されている。すなわち、水循環用ポンプ１０が駆動すると、貯湯タンク１内の未加熱水が取水口７から循環路９に流出して、熱交換路１１を介して湯入口８から貯湯タンク１内に返流する。 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. .
次に、冷凍サイクル３は、圧縮機１３と、上記熱交換路１１を構成する水熱交換器１４と、減圧機構１５と、空気熱交換器１６とを順に接続して構成される。すなわち、圧縮機１３の吐出口と水熱交換器１４とを冷媒通路１７にて接続し、水熱交換器１４と減圧機構１５とを冷媒通路１８にて接続し、減圧機構１５と空気熱交換器１６とを冷媒通路１９にて接続し、空気熱交換器１６と圧縮機１３とをアキュームレータ２０が介設された冷媒通路２１にて接続している。そして、冷媒としては、例えば、高圧側を超臨界圧力で使用する炭酸ガス等の自然冷媒を用いる。また、上記冷媒通路１７には、圧力保護スイッチとしてのＨＰＳ２３と、圧力センサ２４とが設けられている。さらに、減圧機構１５としては、この場合、電動弁（電動膨張弁）１２を使用する。また、空気熱交換器１６にはこの空気熱交換器１６の能力を調整するファン２２が付設されている。 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.
また、冷凍サイクル３は、水熱交換器１４から流出した高圧冷媒を冷却する液ガス熱交換器２５を備える。この場合、液ガス熱交換器２５は、例えば、二重管構造であって、水熱交換器１４から流出した冷媒が通過する第１通路２６と、空気熱交換器１６から流出した冷媒が通過する第２通路２７とを備える。すなわち、第１通路２６が、水熱交換器１４と減圧機構１５とを連結する冷媒通路１８の一部を構成し、第２通路２７が、空気熱交換器１６と圧縮機１３とを連結する冷媒通路２１の一部を構成する。このため、第１通路２６を通過する高温高圧の冷媒と、第２通路２７を通過する低温低圧の冷媒との間で熱交換が行われる。 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.
さらに、このヒートポンプ式給湯装置４には、電動弁１２の上流側と下流側とにそれぞれ冷媒整流用マフラー（消音器）３５、３６が配置される。すなわち、マフラー３５、３６にて冷媒を整流することができ、このため、電動弁１２に流入する冷媒が整流されると共に、電動弁１２から流出する冷媒も整流される。 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.
次に、このヒートポンプ式給湯装置の運転動作（沸上運転）を説明する。圧縮機１３を駆動すると共に、水循環用ポンプ１０を駆動（作動）する。すると、貯湯タンク１の底部に設けた取水口７から貯溜水（温湯）が流出し、これが循環路９の熱交換路１１を流通する。また、圧縮機１３からの吐出冷媒が、水熱交換器１４、減圧機構１５としての電動弁１２、空気熱交換器１６とを順次経由して上記圧縮機１３へと返流する。そのため、循環路９の熱交換路１１を流通する水がガス冷却器である水熱交換器１４によって加熱され（沸き上げられ）、湯入口８から貯湯タンク１の上部に返流される。そしてこのような動作を継続して行うことによって、貯湯タンク１に高温の温湯が貯湯されることになる。なお、現状の電力料金制度は夜間の電力料金単価が昼間に比べて低く設定されているので、この運転は、低額である深夜時間帯に行い、コストの低減を図るようにするのが好ましい。 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.
そして、このヒートポンプ式給湯装置は、水熱交換器１４から流出して減圧機構１５に流入する高圧冷媒と、空気熱交換器１６から流出した低圧冷媒との熱交換を行う液ガス熱交換器２５を設けたので、水熱交換器（ガス冷却器）１４からの冷媒に過冷却を付与し、また、圧縮機１３に入る冷媒を加熱することができる。このため、圧縮機１３の湿り圧縮を防止することができ、安定した運転が可能となる。 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.
また、このヒートポンプ式給湯装置は、循環路９の熱交換路１１よりも上流側の温度を検出する温度センサ（入水サーミスタ）３０と、循環路９の熱交換路１１よりも下流側の温度を検出する温度センサ（出湯サーミスタ）３１と、空気熱交換器１６の温度を検出する温度センサ（空気熱交サーミスタ）３２、圧縮機１３の吐出温度を検出する温度センサ（吐出管サーミスタ）３３と、外気温度を検出する温度センサ（外気温度サーミスタ）３４等が設けられている。そして、これらのセンサからのデータ（検出された温度）がこのヒートポンプ式給湯装置の図示省略の制御部（例えば、マイクロコンピュータ等からなる）に入力され、これらのデータに基づいて、各種の制御が行われる。 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.
すなわち、ヒートポンプ式給湯装置の運転時には、例えば、吐出管サーミスタ３３にて吐出管の温度が検出され、この吐出管温度を目標吐出管温度となるように、電動弁１２の開度を調整（制御）することができる。また、入水サーミスタ３０の温度が所定温度（例えば、６０℃）以上であれば、貯湯タンク１内の湯が沸き上がっているとして運転を停止させたり、また、外気温度サーミスタ３４の温度に基づいて、圧縮機１３の運転周波数を制御して、湯加熱能力（沸上能力）等を調整したりすることができる。 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.
ところで、空気熱交換器１６に霜が付着した場合、霜を除去するための除霜運転を行うことになる。ここで、除霜運転とは、例えば上記電動弁１２を開状態（全開状態）として、空気熱交換器１６の霜に熱を与える運転である。この際、空気熱交換器１６に霜が付着している除霜運転開始時から除霜運転中盤までは、図２（ａ）のようなサイクルを形成して、霜を除去していくことができる。しかしながら、霜がほとんど融けている状態となる除霜運転終盤においては、霜がほとんど融けているので、図２（ｂ）のように、次第に過熱運転となり、液ガス熱交換器２５の低圧部の温度が上昇する。すなわち、液ガス熱交換器２５の出口温度（電動弁１２の入口温度）が高くなり、このため、電動弁１２の入口の冷媒密度が低下して冷媒の流速が増加して、冷媒通過音が大きくなる。 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.
そこで、除霜運転終盤においては、例えば除霜運転中に空気熱交換器１６の温度が所定温度（例えば３℃）以上となれば、圧縮機１３の周波数及び電動弁１２の開度を低下させる。すなわち、除霜運転中に空気熱交換器１６の温度が所定温度（例えば３℃）以上となれば、空気熱交換器１６の霜がほとんど融けている状態となるので、除霜運転開始から除霜運転中盤まで、例えば、圧縮機１３の周波数を７０Ｈｚ程度であると共に、電動弁１２の開度を４８０パルス程度としていれば、圧縮機１３の周波数を６０Ｈｚから６４Ｈｚ程度とすると共に、電動弁１２の開度を３８０パルスから４００パルス程度とする。なお、このように、圧縮機１３の周波数及び電動弁１２の開度を低下させても、霜がほとんど融けている状態の除霜運転終盤であるので、除霜作用に影響がない。 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.
このように、圧縮機１３の周波数及び電動弁１２の開度を低下させることによって、冷媒の流速を低下させることができる。これにより、除霜運転における霜除去終了の直前において発生する冷媒流通音の増加を防止することができ、除霜運転時の騒音を確実に少なくすることができる。なお、除霜運転の開始は、例えば、空気熱交換器１６の温度、外気温度、及び運転開始からの時間（運転時間）等のデータに基づいて決定することができる。 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.
また、上記空気熱交換器１６には、能力調整のためにファン２２から送風される。ところが、空気熱交換器１６に霜が付着した場合、霜のために送風に対する空気抵抗が大きくなるので、通常運転時のような送風量では大きな騒音が生じていた。このため、このヒートポンプ式給湯装置では、着霜状態となって除霜運転が開始される直前において、ファンの回転数を低下させることによって、ファン送風による騒音の低減を図っている。ところで、除霜運転が開始される直前（ファンの回転数を低下させるとき）とは、例えば、前回の除霜運転が終了した後、沸上運転時間が所定時間（例えば、１５分）以上経過し、かつ、空気熱交換器１６の温度が、外気温度よりも所定温度（例えば、８℃）だけ低い温度未満のときとする。 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.).
この場合、通常の制御において、図３（ｂ）に示すように、除霜運転を行っていない沸上運転でファン回転数が例えば６６０（ｒｐｍ）であれば、除霜運転に突入する際にも、回転数はこのままである。このため、運転音として例えば３８ｄＢＡであれば、霜のために送風に対する空気抵抗が大きくなるので、次第にこの運転音が大きくなり、除霜運転突入時には、例えば４３ｄＢＡ程度になる。そこで、このヒートポンプ式給湯装置では、除霜運転を行っていない沸上運転でファン回転数が例えば６６０（ｒｐｍ）であれば、除霜運転に突入する直前に図３（ａ）に示すように、ファン回転数を例えば５６０（ｒｐｍ）に低下させて、除霜運転に突入するようにしている。このため、運転音を例えば３８ｄＢＡ程度に維持することができる。この場合、ファン回転数の上限を設定することになる。すなわち、低下させる回転数の上限値を通常の運転時（沸上運転時）の周波数の上限値の例えば８０％程度に設定する。 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).
ところで、冷媒に炭酸ガスでない冷媒（超臨界冷媒でない冷媒）、例えば、ＨＣＦＣ、ＨＦＣ冷媒を使用すれば、モリエル線図は図４（ｂ）のようなグラフ図となる。これに対して、超臨界冷媒を使用すれば、モリエル線図は図４（ｂ）のようなグラフ図となる。このため、超臨界冷媒でない冷媒を使用する場合と、超臨界冷媒を使用する場合では、同一能力クラスでは、冷媒循環量がほぼ同じ（例えば、４５００Ｗクラスで７０ｋｇ／ｈ）となる。しかしながら、炭酸ガス（ＣＯ２）の冷媒を使用すれば、電動弁１２前後の差圧が大きくなるため通常の冷媒に使用したものと同一口径の電動弁１２では冷媒循環量が多くなるため調節できない。すなわち、炭酸ガスの冷媒を使用する場合、電動弁１２の口径を通常の冷媒を使用するときよりも小さくする必要がある。しかしながら、電動弁１２の口径を小さくすれば、この電動弁１２を冷媒が通過する際に発生する騒音（冷媒音）が大きくなっていた。 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.
そこで、このヒートポンプ式給湯装置のものでは、電動弁１２の上流側と下流側とにそれぞれ冷媒整流用マフラー（消音器）３５、３６を配置して、このマフラー３５、３６にて冷媒を整流するようにしている。このため、電動弁１２に流入する冷媒が整流されると共に、電動弁１２から流出する冷媒も整流される。このため、電動弁１２での冷媒通過音の低下を達成することができる。これにより、ヒートポンプユニット４において発生する冷媒音（冷媒が流れる際に発生する音）を全体として低減することができ、騒音が少なく深夜運転を行うのに最適なヒートポンプ式給湯装置となる。すなわち、現状の電力料金制度は夜間（深夜）の電力料金単価が昼間に比べて低く設定されているので、運転を、低額である深夜時間帯に行い、コストの低減を図ることができる。 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.
また、ヒートポンプ式給湯装置では、除霜運転における霜除去終了の直前に、圧縮機１３の周波数及び電動弁１２の開度を低下させることによって、冷媒の流速を低下させる。これにより、除霜運転における霜除去終了の直前からの冷媒音の増加を防止することができ、除霜運転時の騒音を確実に少なくすることができる。しかも、騒音を少なくするための制御としては、圧縮機１３の周波数及び電動弁１２の開度を低下させればよいので、簡単である。このため、コスト低減を達成できると共に、低騒音化の信頼性が向上する。特に、この実施の形態のように、除霜運転における霜除去終了の直前に、圧縮機１３の周波数及び電動弁１２の開度を低下させることによる低騒音化と、電動弁１２の上流側と下流側とに冷媒整流用マフラー３５、３６を配置することによる低騒音化とを組み合わせるようにすれば、冷媒音の一層の低下を達成でき、極めて静かな除霜運転を行うことができる。 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.
さらに、除霜運転が開始される直前において、非着霜状態の通常運転時よりもファン２２（空気熱交換器１６に送風するファン）の回転数を低下させるので、ファン送風による騒音の低減を達成できる。すなわち、空気熱交換器１６の着霜状態においては、霜のために送風に対する空気抵抗が大きくなるので、通常運転時のような送風量では、大きな騒音が生じていた。このため、図３（ａ）に示すように、除霜運転（除霜突入）前においてファン２２の回転数を低下させることによって、この低下させている部分Ｂのファン送風による騒音の低減を図ることができる。 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.
また、冷媒に超臨界で使用する超臨界冷媒を用いるので、地球環境に優しいヒートポンプユニットとなる。特に、高圧側が超臨界圧力で運転するので、電動弁前後の差圧が大きくなるため、電動弁１２を小さな口径のものを使用することになり、冷媒が電動弁１２を通過する際の通過音が大きく、上記実施の形態のように、電動弁１２の上流側及び下流側に冷媒整流用マフラー３５、３６を配置することにより、低騒音化を確実に達成することができる。 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.
以上にこの発明の具体的な実施の形態について説明したが、この発明は上記形態に限定されるものではなく、この発明の範囲内で種々変更して実施することができる。例えば、上記実施の形態では、貯湯タンク１を有するものであったが、正常の沸上運転において、水熱交換器１４にて構成される熱交換路１１に未加熱水が流入して、この熱交換路１１を流れる際に加熱されて、高温水がこの熱交換路１１から流出するものであればよいので、貯湯タンク１を有さないものであってもよい。また、電動弁１２の上流側及び下流側に配置する冷媒整流用マフラー３５、３６としては、整流器として機能する既存のマフラーを使用することができる。そして、上記実施の形態では、マフラー３５、３６を備えると共に、除霜運転の終盤において電動弁１２の開度等を低下させ、さらには、除霜運転に入る直前にファン２２の回転数を低下させるようにしているが、マフラー３５、３６を備えている場合、除霜運転の終盤において電動弁１２の開度等を低下させる制御や除霜運転に入る直前にファン２２の回転数を低下させる制御を行わないものであってもよい。すなわち、除霜運転の終盤において電動弁１２の開度等を低下させることによる消音化、除霜運転に入る直前にファン２２の回転数を低下させることによる消音化、及びマフラー３５、３６による消音化のうち、すくなくともいずれかの消音化が達成できればよい。なお、使用する冷媒として、冷媒としては、炭酸ガス以外に、エチレンやエタン、酸化窒素等の超臨界で使用する冷媒であってもよく、さらには、超臨界で使用する冷媒ではなく、ジクロロジフルオロメタン（Ｒ−１２）やクロロジフルオロメタン（Ｒ−２２）のような冷媒を使用してもよい。 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.
４・・ヒートポンプユニット、１１・・熱交換路、１２・・電動弁、１３・・圧縮機、１４・・水熱交換器、１５・・減圧機構、１６・・空気熱交換器、２２・・ファン、３５、３６・・冷媒整流用マフラー 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)
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.
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| JP2007040555A (en) * | 2005-08-01 | 2007-02-15 | Matsushita Electric Ind Co Ltd | Heat pump type water heater |
| JP2007271211A (en) * | 2006-03-31 | 2007-10-18 | Daikin Ind Ltd | Refrigerating device |
| JP4270274B2 (en) * | 2006-03-31 | 2009-05-27 | ダイキン工業株式会社 | Outdoor unit |
| JP4765727B2 (en) * | 2006-03-31 | 2011-09-07 | ダイキン工業株式会社 | Refrigeration equipment |
| JP2009058222A (en) * | 2006-03-31 | 2009-03-19 | Daikin Ind Ltd | Outdoor unit |
| JP4904970B2 (en) * | 2006-08-01 | 2012-03-28 | ダイキン工業株式会社 | Refrigeration equipment |
| JP5082865B2 (en) * | 2008-01-11 | 2012-11-28 | 株式会社デンソー | Heat pump device, hot water supply device including the same, and control device therefor |
| CN102449408B (en) * | 2009-05-29 | 2014-07-30 | 大金工业株式会社 | Air-conditioning device |
| EP3764022B1 (en) | 2018-03-08 | 2023-10-25 | Mitsubishi Electric Corporation | Hot water supply device |
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