JP2009257717A

JP2009257717A - Heat pump water heater

Info

Publication number: JP2009257717A
Application number: JP2008110292A
Authority: JP
Inventors: Yutaka Enokitsu; 豊榎津; Yoshihiko Kenmori; 仁彦権守; Masami Murayama; 昌巳村山
Original assignee: Hitachi Appliances Inc
Current assignee: Hitachi Appliances Inc
Priority date: 2008-04-21
Filing date: 2008-04-21
Publication date: 2009-11-05
Anticipated expiration: 2028-04-21
Also published as: CN102016439A; WO2009130804A1; KR101222300B1; CN102016439B; JP5081050B2; KR20100128332A

Abstract

<P>PROBLEM TO BE SOLVED: To provide a heat pump water heater carrying out comprehensively optimum operation control by securing heating capacity, improving heating efficiency, and carrying out energy saving within a period including winter defrosting. <P>SOLUTION: The heat pump water heater includes a heat pump coolant circuit 30 having a compressor, a water-coolant heat exchanger, an expansion valve, and an air-coolant heat exchanger, a hot water supply circuit 40 having a hot water storage tank, an internal circulating pump, a hot water supply mixing valve, a bathtub heat exchanger, a bathtub circulating pump, and a hot water-water mixing valve, and forming direct hot water supply from tank stored hot water and hot water supply, bathtub hot water filling, and bathtub reheating from the tank, and an operation control part 50 carrying out hot water storage operation, direct hot water supply operation, tank hot water supply operation, bathtub hot water filling operation, and bathtub reheating operation by operation settings of a tapping location remote control 51 and a bath remote control 52. The operation control part carries out optimum operation control of determining any of three types of operation means of heating efficiency priority operation, heating capacity priority operation, and intermediate defrosting operation using an ambient temperature, an air-coolant heat exchanger temperature, and a hot water supply/hot water storage mode as criteria. <P>COPYRIGHT: (C)2010,JPO&INPIT

Description

本発明は、ヒートポンプ給湯機に係わり、特に、着霜期を含む期間におけるヒートポンプの最適運転制御に関するものである。 The present invention relates to a heat pump water heater, and more particularly to optimum operation control of a heat pump in a period including a frost period.

従来のヒートポンプ給湯機は電気温水器と同様に大容量の貯湯タンクを設け、夜間割引料金の安価な電力を使ってヒートポンプ運転を行ない、夜中のうちに湯を沸かして貯湯タンクに貯湯しておき、貯湯した湯を昼間に使う貯湯式のものが一般的であった。 A conventional heat pump water heater has a large-capacity hot water storage tank similar to an electric water heater, operates a heat pump using cheap electricity with a discounted night rate, boils hot water during the night, and stores it in the hot water storage tank. The hot water storage type that uses the hot water stored in the daytime was common.

これに対し、近年、主に給湯使用する昼間にもヒートポンプ運転を行なって加熱した温水を直接給湯することにより、貯湯タンクの大幅な小形化を図った瞬間式ヒートポンプ給湯機が開発されている。この瞬間式ヒートポンプ給湯機の従来例として、例えば、特許文献１に開示されたものがある。 On the other hand, in recent years, instantaneous heat pump water heaters have been developed in which a hot water tank is directly miniaturized by directly supplying hot water heated by operating a heat pump even during the daytime when hot water is used. As a conventional example of this instantaneous heat pump water heater, there is one disclosed in Patent Document 1, for example.

この特許文献１によれば、予め貯湯運転を行なって６０〜１００Ｌの小形貯湯タンクに高温水を貯湯しておき、湯水使用時には、ヒートポンプの加熱温度が適温に到達しない運転当初はヒートポンプの加熱水に貯湯タンクからの高温水を混ぜて適温として給湯し、ヒートポンプ運転による加熱温度が適温に達すると、貯湯タンクからの給湯を止め、ヒートポンプ運転で加熱した適温水を直接給湯して使用するものである。 According to Patent Document 1, hot water storage operation is performed in advance, hot water is stored in a small hot water storage tank of 60 to 100 L, and when the hot water is used, the heating temperature of the heat pump does not reach an appropriate temperature at the beginning of operation. Hot water from the hot water storage tank is mixed to supply hot water at an appropriate temperature, and when the heating temperature by the heat pump operation reaches an appropriate temperature, the hot water from the hot water storage tank is stopped and the hot water heated by the heat pump operation is directly supplied and used. is there.

また、瞬間式ヒートポンプ給湯機の運転制御は、タンク貯湯または台所・洗面所給湯に対応して、圧縮機の回転数を変えて加熱能力を調整し、空気冷媒熱交換器（蒸発器）の除霜は、空気冷媒熱交換器の温度によって着霜量を検知し、多量に着霜してヒートポンプの加熱性能が低下してから除霜用バイパス弁を開放して除霜を行なうもので、いずれも比較的簡易な構成のものであった。
特開２００３−２７９１３３号公報 In addition, the operation control of the instantaneous heat pump water heater is controlled by changing the number of rotations of the compressor and adjusting the heating capacity corresponding to tank hot water or kitchen / lavatory hot water supply, and removing the air refrigerant heat exchanger (evaporator). Frost detects the amount of frost formation based on the temperature of the air refrigerant heat exchanger, defrosts by defrosting a large amount of frost and opening the defrosting bypass valve after the heating performance of the heat pump decreases. Also, the configuration was relatively simple.
JP 2003-279133 A

上記の特許文献１に開示されているように、従来のヒートポンプ給湯機においては、ほぼ給湯用途に対応して圧縮機の回転数を変えて加熱能力を調整していた。しかし、近年ヒートポンプ給湯機が普及するに従い、使用用途が多岐に亘り、給湯温度も複雑化されてきた。例えば、風呂湯張り温度は、従来入浴直前に給湯するため給湯温度は約４２℃一定であったが、湯張り時間を事前に予約設定しておく機能が付き、やや高目の４５℃給湯の必要性が出てくると共に、季節によって３８℃〜４８℃位まで給湯温度を選択できるように機能追加されてきた。 As disclosed in the above-mentioned Patent Document 1, in the conventional heat pump water heater, the heating capacity is adjusted by changing the number of rotations of the compressor substantially corresponding to the hot water supply application. However, in recent years, as heat pump water heaters have become widespread, use applications have been diversified and hot water supply temperatures have been complicated. For example, the bath hot water temperature is constant at about 42 ° C because hot water is supplied just before bathing, but it has a function to reserve the hot water time in advance. As the need emerges, functions have been added so that the hot water supply temperature can be selected from 38 ° C. to 48 ° C. depending on the season.

また、タンク貯湯温度についても多様化が進み、給湯使用量の季節変化に対応して、夏期、春・秋の中間期は約６５℃で貯湯し、冬期は７０〜７５℃、冬期低温時は８５〜９０℃で貯湯するなどの工夫がなされている。 In addition, tank hot water storage temperature has been diversified, and in response to seasonal changes in hot water usage, hot water is stored at about 65 ° C in the summer, spring and autumn, 70-75 ° C in winter, and at low temperatures in winter The idea of storing hot water at 85-90 degreeC is made | formed.

ところで、これらの多様化した給湯使用状況に対し、ヒートポンプの運転制御は給湯量確保を重点にそれぞれの給湯温度に対応して加熱能力優先で制御されており、省エネの観点からは必ずしも最適運転制御とはなっていなかった。例えば、風呂湯張り運転を時間予約する場合は湯張り時間が長くなっても加熱効率優先で良いが、シャワーのように大きな給湯量を必要とする場合は効率よりも加熱能力を優先しなければならない。また、冬期においては、連続運転を優先すると長時間給湯時に着霜による加熱能力低下が課題となり、空気冷媒熱交換器温度を検知して除霜運転を入れるようにすると、台所給湯中や洗面中に除霜を開始して給湯が止まってしまうという課題があり、これらの多様化した使用条件に対し、加熱能力、省エネ、除霜制御等を総合的に考慮した最適運転制御手段の必要性が従来求められていた。 By the way, for these diversified hot water usage situations, heat pump operation control is controlled with priority given to each hot water supply temperature with emphasis on securing hot water supply, and optimal operation control is not always necessary from the viewpoint of energy saving. It was not. For example, when reserving a bathing hot water operation, heating efficiency may be prioritized even if the hot water filling time is long, but when a large amount of hot water supply is required, such as a shower, heating capacity must be prioritized over efficiency. Don't be. In winter, when continuous operation is prioritized, heating capacity declines due to frost formation during hot water supply for long periods of time. However, there is a need for an optimal operation control means that comprehensively considers heating capacity, energy saving, defrost control, etc. for these diversified use conditions. It has been sought in the past.

本発明の目的は、これらの課題を解決するために、冬期除霜時を含めた期間において、加熱能力の確保、加熱効率の向上、省エネを図り総合的に最適な運転制御を行うヒートポンプ給湯機を提供することにある。 In order to solve these problems, the object of the present invention is to provide a heat pump water heater that performs comprehensively optimal operation control in order to ensure heating capacity, improve heating efficiency, and save energy during a period including defrosting in winter. Is to provide.

前記課題を解決するために、本発明は主として次のような構成を採用する。
冷媒を圧縮する圧縮機、水と冷媒との熱交換を行なう水冷媒熱交換器、膨張弁、空気と冷媒との熱交換を行なう空気冷媒熱交換器、冷媒配管、を有するヒートポンプ冷媒回路と、前記水冷媒熱交換器で加熱した温水を貯めて置く貯湯タンク、機内循環ポンプ、給湯混合弁、前記水冷媒熱交換器で加熱した温水との熱交換を行う風呂用熱交換器、風呂循環用ポンプ、湯水混合弁、水配管、を有して、前記貯湯タンクに高温水を貯める貯湯回路、前記水冷媒熱交換器で加熱した温水を出湯箇所に直接給湯する直接給湯回路、前記貯湯タンクからの温水を出湯箇所に給湯するタンク給湯回路、前記水冷媒熱交換器で加熱した温水を前記風呂循環用ポンプで風呂に給湯する風呂湯張り回路、前記風呂用熱交換器からの温水を前記風呂循環用ポンプで風呂に給湯する風呂追焚回路、を形成する給湯回路と、出湯箇所リモコンと風呂リモコンの操作設定で、各構成要素を制御して貯湯運転、直接給湯運転、タンク給湯運転、風呂湯張り運転、風呂追焚運転を行う運転制御部と、を備えたヒートポンプ給湯機であって、前記運転制御部は、ヒートポンプ給湯機の周囲温度と、前記空気冷媒熱交換器の温度と、及びタンクへの貯湯、出湯箇所への給湯、風呂湯張り、所定時間以上の運転での給湯、を含む給湯・貯湯モードと、を判定基準として、加熱効率優先運転、加熱能力優先運転、中間除霜運転、の３種類の運転手段のいずれかを判定する最適運転制御を行う構成である。 In order to solve the above problems, the present invention mainly adopts the following configuration.
A heat pump refrigerant circuit having a compressor for compressing refrigerant, a water refrigerant heat exchanger for exchanging heat between water and refrigerant, an expansion valve, an air refrigerant heat exchanger for exchanging heat between air and refrigerant, and a refrigerant pipe; Hot water storage tank for storing hot water heated by the water refrigerant heat exchanger, in-machine circulation pump, hot water mixing valve, bath heat exchanger for exchanging heat with hot water heated by the water refrigerant heat exchanger, for bath circulation A hot water storage circuit for storing hot water in the hot water storage tank, a direct hot water supply circuit for directly supplying hot water heated by the water refrigerant heat exchanger to a hot water outlet, A hot water supply circuit for supplying hot water to a hot water outlet, a hot water heating circuit for supplying hot water heated by the water-refrigerant heat exchanger to the bath with the pump for circulating the bath, and hot water from the heat exchanger for bath to the bath Wind with circulation pump Hot water supply circuit to form a hot water supply circuit, and hot water storage operation, direct hot water supply operation, tank hot water operation, bath hot water operation, bath An operation control unit that performs a memorial operation, wherein the operation control unit includes an ambient temperature of the heat pump water heater, a temperature of the air refrigerant heat exchanger, and hot water storage in a tank, Three types of heating efficiency priority operation, heating capacity priority operation, and intermediate defrosting operation are used as criteria for determining hot water and hot water storage modes, including hot water supply to hot water outlets, bath hot water filling, and hot water supply for operation over a predetermined time. It is the structure which performs the optimal driving | operation control which determines either of the driving | operation means.

また、前記ヒートポンプ給湯機において、前記運転制御部は、前記加熱効率優先運転と判定した場合は加熱効率が最大となるような圧縮機回転数で運転し、前記加熱能力優先運転と判定した場合は加熱能力が最大となるような圧縮機回転数で運転し、前記中間除霜運転と判定した場合は加熱能力が最大となるような圧縮機回転数で運転し且つ推定されるヒートポンプ運転時間の約１／２の時間経過後に除霜運転を行なう構成である。さらに、前記運転制御部は、前記判定基準として、前記周囲温度を約＋７℃以上または約−7℃以下と、約−7℃〜＋７℃の少なくとも２つ以上に区分する構成である。 Further, in the heat pump water heater, when the operation control unit determines that the heating efficiency priority operation is performed, the operation is performed at a compressor rotation speed that maximizes the heating efficiency, and when the heating capacity priority operation is determined. Operate at a compressor speed that maximizes the heating capacity, and if it is determined as the intermediate defrosting operation, operate at a compressor speed that maximizes the heating capacity, and approximately the estimated heat pump operating time It is the structure which performs a defrost driving | operation after 1/2 time progress. Furthermore, the operation control unit is configured to divide the ambient temperature into at least two of about + 7 ° C. or more and about −7 ° C. or less and about −7 ° C. to + 7 ° C. as the determination criterion.

また、前記ヒートポンプ給湯機において、前記運転制御部は、前記判定基準として、前記空気冷媒熱交換器温度を約０℃以上と約０℃未満の２つに区分する構成である。さらに、前記運転制御部は、前記判定基準として、給湯モード毎にヒートポンプ運転時間を学習し、推定運転時間が約６０分以上の給湯モードの場合、最適運転制御として中間除霜運転と判定する構成である。さらに、前記運転制御部は、ヒートポンプ運転による加熱運転終了後に前記空気冷媒熱交換器の着霜判定を行ない、着霜していると判定した場合は除霜運転を行なってからヒートポンプ運転を停止し、着霜していないと判定した場合は除霜運転を行なわずにヒートポンプ運転を停止する構成である。 Further, in the heat pump water heater, the operation control unit is configured to divide the air refrigerant heat exchanger temperature into two of about 0 ° C. or more and less than about 0 ° C. as the determination criterion. Further, the operation control unit learns the heat pump operation time for each hot water supply mode as the determination criterion, and determines the intermediate defrost operation as the optimum operation control in the hot water supply mode with an estimated operation time of about 60 minutes or more. It is. Further, the operation control unit performs the frost determination of the air refrigerant heat exchanger after the heating operation by the heat pump operation is completed, and when it is determined that the frost is formed, performs the defrost operation and then stops the heat pump operation. When it is determined that frost is not formed, the heat pump operation is stopped without performing the defrosting operation.

本発明によれば、ヒートポンプ給湯機の使用条件を十分に加味した最適運転を判定することが可能となり、冬期除霜時を含めて加熱能力の確保、加熱効率の向上及び省エネを図り総合的に最適な運転手段を選定することができる。 According to the present invention, it is possible to determine the optimum operation sufficiently considering the use conditions of the heat pump water heater, and comprehensively aiming to ensure heating capacity, improve heating efficiency and save energy, including during winter defrosting. Optimal driving means can be selected.

また、最適運転手段の判定基準と、加熱効率優先運転、加熱能力優先運転、中間除霜運転の３種類の運転手段とを、より具体的に詳細規定することにより、一層最適な運転手段の選定を図ると共に製品化を容易にすることができる。 In addition, by selecting the optimum operation means judgment criteria and the three types of operation means of heating efficiency priority operation, heating capacity priority operation, and intermediate defrost operation more specifically, the selection of the most optimal operation means And at the same time making the product easier.

また、運転終了時の着霜を検知し、着霜がある場合のみ除霜運転を行なってから運転停止するので、次回の運転開始時に着霜のない状態で運転開始でき、運転開始時の加熱立ち上がり特性の向上を図ることができるとともに、低外気温度または降雪などの条件下において、運転終了時の着霜が停止期間内に増長することを防止することができる。 In addition, frost formation at the end of operation is detected, and only when there is frost, the defrost operation is performed and then the operation is stopped.Therefore, at the start of the next operation, the operation can be started without frost formation, and heating at the start of operation can be performed. The rise characteristics can be improved, and frost formation at the end of operation can be prevented from increasing during the stop period under conditions such as low outside air temperature or snowfall.

本発明の実施形態に係るヒートポンプ給湯機について、図１〜図７を参照しながら以下詳細に説明する。図１は、本発明の実施形態に係るヒートポンプ給湯機の構成要素と接続経路を示す全体構成図である。図１において、本実施形態に係るヒートポンプ給湯機は、全体として、ヒートポンプ冷媒回路３０と、給湯回路４０と、運転制御手段５０と、から構成されている。 A heat pump water heater according to an embodiment of the present invention will be described in detail below with reference to FIGS. FIG. 1 is an overall configuration diagram showing components and connection paths of a heat pump water heater according to an embodiment of the present invention. In FIG. 1, the heat pump water heater according to this embodiment includes a heat pump refrigerant circuit 30, a hot water supply circuit 40, and an operation control means 50 as a whole.

ヒートポンプ冷媒回路３０は、第一冷媒回路３０ａ及び第二冷媒回路３０ｂの２サイクル方式で構成され、圧縮機１ａ，１ｂ、水冷媒熱交換器２に配置される冷媒側伝熱管２ａ，２ｂ、膨張弁３ａ，３ｂ、空気冷媒熱交換器４ａ，４ｂを、それぞれ冷媒配管を介して順次接続して構成されており、その中に冷媒が封入されている。 The heat pump refrigerant circuit 30 is configured by a two-cycle system of a first refrigerant circuit 30a and a second refrigerant circuit 30b, and includes refrigerant-side heat transfer tubes 2a and 2b disposed in the compressors 1a and 1b and the water-refrigerant heat exchanger 2, and expansion. The valves 3a and 3b and the air refrigerant heat exchangers 4a and 4b are sequentially connected via refrigerant pipes, respectively, in which refrigerant is enclosed.

圧縮機１ａ，１ｂは容量制御が可能で、多量の給湯を行なう場合には大きな容量で運転される。ここで、圧縮機１ａ，１ｂはＰＷＭ制御、電圧制御（例えばＰＡＭ制御）及びこれらの組合せ制御により、低速（例えば７００回転／分）から高速（例えば７０００回転／分）まで回転数制御ができるようになっている。水冷媒熱交換器２は冷媒側伝熱管２ａ，２ｂ及び給水側伝熱管２ｃ，２ｄを備えており、冷媒側伝熱管２ａ，２ｂと給水側伝熱管２ｃ，２ｄとの間で熱交換を行なうように構成されている。 The compressors 1a and 1b are capable of capacity control, and are operated with a large capacity when supplying a large amount of hot water. Here, the compressors 1a and 1b can control the rotational speed from a low speed (for example, 700 rotations / minute) to a high speed (for example, 7000 rotations / minute) by PWM control, voltage control (for example, PAM control) and combination control thereof. It has become. The water refrigerant heat exchanger 2 includes refrigerant side heat transfer tubes 2a and 2b and water supply side heat transfer tubes 2c and 2d, and performs heat exchange between the refrigerant side heat transfer tubes 2a and 2b and the water supply side heat transfer tubes 2c and 2d. It is configured as follows.

膨張弁３ａ，３ｂとしては、一般に開度調整時の応答性が速い電動膨張弁が使用され、水冷媒熱交換器２を経て送られてくる中温高圧冷媒を減圧し、蒸発し易い低圧冷媒として空気冷媒熱交換器４ａ，４ｂへ送る。また、膨張弁３ａ，３ｂは冷媒通路の開度を変えてヒートポンプ冷媒回路内の冷媒循環量を調節する働きや、開度を大きくして中温冷媒を空気冷媒熱交換器４ａ，４ｂに多量に送って霜を溶かす除霜装置の役目も行なう。 As the expansion valves 3a and 3b, an electric expansion valve having a quick response at the time of opening adjustment is generally used, and the medium temperature and high pressure refrigerant sent through the water refrigerant heat exchanger 2 is depressurized and is easily evaporated. It sends to air refrigerant heat exchanger 4a, 4b. Further, the expansion valves 3a and 3b function to adjust the refrigerant circulation amount in the heat pump refrigerant circuit by changing the opening of the refrigerant passage, and increase the opening to increase the amount of medium temperature refrigerant to the air refrigerant heat exchangers 4a and 4b. It also serves as a defrosting device that sends frost to melt.

空気冷媒熱交換器４ａ，４ｂは、送風ファン５ａ，５ｂの回転により外気を取り入れ、空気と冷媒との熱交換を行ない、外気から熱を吸収する役目を行なう。給湯回路４０は、（１）貯湯、（２）直接給湯、（３）タンク給湯、（４）風呂湯張り、（５）風呂追焚きを行なうための水循環回路を備えて構成されている。 The air refrigerant heat exchangers 4a and 4b take in outside air by rotation of the blower fans 5a and 5b, perform heat exchange between the air and the refrigerant, and absorb heat from the outside air. The hot water supply circuit 40 includes a water circulation circuit for performing (1) hot water storage, (2) direct hot water supply, (3) tank hot water supply, (4) bath hot water filling, and (5) bath reheating.

貯湯回路（１）は、タンク沸上げ運転によって貯湯タンク１６に高温水を貯めるための水回路で、貯湯タンク１６、機内循環ポンプ１７、水熱交流量センサ１０、給水側伝熱管２ｃ，２ｄ、給湯混合弁１１、貯湯タンク１６が水配管を介して順次接続され構成されている。 The hot water storage circuit (1) is a water circuit for storing hot water in the hot water storage tank 16 by the tank boiling operation. The hot water storage tank 16, the in-machine circulation pump 17, the hydrothermal AC sensor 10, the water supply side heat transfer pipes 2c, 2d, A hot water mixing valve 11 and a hot water storage tank 16 are sequentially connected via a water pipe.

直接給湯回路（２）は、給水金具６、減圧弁７、給水水量センサ８、給水側逆止弁９、水熱交流量センサ１０、給水側伝熱管２ｃ，２ｄ、給湯混合弁１１、湯水混合弁１２、流量調整弁１３、台所出湯金具１４が水配管を介して順次接続され構成されている。なお、給水金具６は水道などの給水源に接続され、台所出湯金具１４は台所蛇口１５などに接続されている。 The direct hot water supply circuit (2) includes a water supply fitting 6, a pressure reducing valve 7, a water supply water amount sensor 8, a water supply side check valve 9, a hydrothermal AC amount sensor 10, water supply side heat transfer tubes 2c and 2d, a hot water supply mixing valve 11, and hot water mixing. A valve 12, a flow rate adjustment valve 13, and a kitchen tapping metal fitting 14 are sequentially connected via a water pipe. The water supply fitting 6 is connected to a water supply source such as a water supply, and the kitchen tap metal fitting 14 is connected to a kitchen faucet 15 or the like.

タンク給湯回路（３）は、給水金具６、減圧弁７、給水水量センサ８、給水側逆止弁９、貯湯タンク１６、給湯混合弁１１、湯水混合弁１２、流量調整弁１３、台所出湯金具１４が水配管を介して順次接続され構成されている。 The tank hot water supply circuit (3) includes a water supply fitting 6, a pressure reducing valve 7, a water supply amount sensor 8, a water supply side check valve 9, a hot water storage tank 16, a hot water supply mixing valve 11, a hot water mixing valve 12, a flow rate adjusting valve 13, and a kitchen tapping metal fitting. 14 are sequentially connected via a water pipe.

風呂湯張り回路（４）は、給水金具６、減圧弁７、給水水量センサ８、給水側逆止弁９、水熱交流量センサ１０、給水側伝熱管２ｃ，２ｄ、給湯混合弁１１、湯水混合弁１２、流量調整弁１３、風呂注湯弁１８、フロースイッチ１９、風呂循環ポンプ２０、水位センサ２１、風呂入出湯金具２２、風呂循環アダプター２３、浴槽２４が水配管を介して順次接続され構成されている。また、風呂入出湯金具２２からは浴槽２４と共に風呂蛇口２５やシャワー（図示せず）にも給湯できるよう接続されている。なお、風呂湯張り時には、風呂湯張り回路による直接給湯と共に、貯湯タンク１６内の湯量が最低必要量以下にならない範囲において貯湯タンク１６から浴槽２４へのタンク給湯も行なう。 The bath hot water filling circuit (4) includes a water supply fitting 6, a pressure reducing valve 7, a water supply amount sensor 8, a water supply side check valve 9, a hydrothermal AC amount sensor 10, water supply side heat transfer tubes 2c and 2d, a hot water supply mixing valve 11, and hot water. A mixing valve 12, a flow rate adjusting valve 13, a bath pouring valve 18, a flow switch 19, a bath circulation pump 20, a water level sensor 21, a bath inlet / outlet fitting 22, a bath circulation adapter 23, and a bathtub 24 are sequentially connected via a water pipe. It is configured. Moreover, it connects so that it can supply hot water to the bath faucet 25 and the shower (not shown) from the bath entry / exit metal fitting 22 with the bathtub 24. During bath hot water filling, hot water supply from the hot water storage tank 16 to the bathtub 24 is also performed within the range where the hot water amount in the hot water storage tank 16 does not fall below the minimum required amount, as well as direct hot water supply by the bath hot water filling circuit.

風呂追焚回路（５）は、浴槽２４、風呂循環アダプター２３、風呂入出湯金具２２、水位センサ２１、風呂循環ポンプ２０、フロースイッチ１９、風呂用熱交換器２７の風呂水伝熱管２７ｂ、風呂出湯金具２６、風呂循環アダプター２３、浴槽２４が水配管を介して順次接続され構成されている。なお、風呂追焚き時には、風呂追焚回路（５）による浴槽水の水循環と共に、ヒートポンプ運転及び機内循環ポンプ１７を運転し、かつ温水開閉弁２８を開放して水冷媒熱交換器２で加熱された温水を風呂用熱交換器２７に設けられた温水伝熱管２７ａに循環させ、温水伝熱管２７ａと風呂水伝熱管２７ｂとの間で熱交換し、風呂追焚きを行なうものである。 The bath memory circuit (5) includes a bathtub 24, a bath circulation adapter 23, a bath inlet / outlet fitting 22, a water level sensor 21, a bath circulation pump 20, a flow switch 19, a bath water heat transfer tube 27b of a bath heat exchanger 27, a bath A hot metal fitting 26, a bath circulation adapter 23, and a bathtub 24 are sequentially connected via a water pipe. At the time of bathing, the bath water is circulated by the bath chasing circuit (5), the heat pump operation and the in-machine circulation pump 17 are operated, the hot water on-off valve 28 is opened, and the water / refrigerant heat exchanger 2 is heated. The hot water is circulated through a hot water heat transfer tube 27a provided in the heat exchanger 27 for bath, heat is exchanged between the hot water heat transfer tube 27a and the bath water heat transfer tube 27b, and the bath is reheated.

次に、運転制御手段５０は、台所リモコン５１（台所に限らず洗面所などの出湯箇所リモコン）及び風呂リモコン５２の操作設定により、ヒートポンプ冷媒回路３０の運転・停止並びに圧縮機１ａ，１ｂの回転数制御を行なうと共に、膨張弁３ａ，３ｂの冷媒開度調整、機内循環ポンプ１７、風呂循環ポンプ２０の運転・停止及び給湯混合弁１１、湯水混合弁１２、流量調整弁１３、風呂注湯弁１８、温水開閉弁２８を制御することにより、貯湯運転、直接給湯運転、タンク給湯運転、風呂湯張り運転、風呂追焚運転を行なうものである。 Next, the operation control means 50 operates / stops the heat pump refrigerant circuit 30 and rotates the compressors 1a and 1b according to the operation settings of the kitchen remote controller 51 (not only in the kitchen but also at the hot water outlet such as a washroom) and the bath remote controller 52. In addition to performing numerical control, the refrigerant opening adjustment of the expansion valves 3a and 3b, the operation / stop of the in-machine circulation pump 17, the bath circulation pump 20, the hot water mixing valve 11, the hot water mixing valve 12, the flow rate adjusting valve 13, the bath pouring valve 18. By controlling the hot water on / off valve 28, a hot water storage operation, a direct hot water supply operation, a tank hot water operation, a bath hot water operation, and a bath chasing operation are performed.

また、運転制御手段５０は、圧縮機１ａ，１ｂの回転数を制御し、運転開始時は徐々に回転数を増して行き、加熱立上げ時間を早めるため所定の高速回転数で運転するが、台所・洗面給湯（約４２℃）のような通常負荷の場合、運転安定後は中速運転に戻すと共に、熱負荷の大きい貯湯運転（約６５〜９０℃）時は比較的高速運転とするよう制御する。 Further, the operation control means 50 controls the rotation speed of the compressors 1a and 1b, and gradually increases the rotation speed at the start of operation and operates at a predetermined high speed rotation speed in order to shorten the heating start-up time. In the case of normal load such as kitchen / wash water supply (about 42 ° C), return to medium speed operation after stable operation and relatively high speed operation during hot water storage operation (about 65-90 ° C) with large heat load. Control.

さらに、ヒートポンプ給湯機には、貯湯タンク１６の貯湯温度や貯湯量を検知するためのタンクサーミスタ１６ａ〜１６ｅ、周囲温度を検知する周囲温度サーミスタ（図示せず）、空気冷媒熱交換器の温度を検知する空気熱交サーミスタ及び各部の温度を検知するサーミスタ（図示せず）や圧縮機１ａ，１ｂの吐出圧力を検知する圧力センサ（図示せず）、浴槽２４内の水位を検知する水位センサ２１等が設けられ、各検出信号は運転制御手段５０に入力されるように構成されている。運転制御手段５０はこれらの信号に基づいて各機器を制御するものである。 Further, the heat pump water heater includes tank thermistors 16a to 16e for detecting the hot water storage temperature and the amount of hot water stored in the hot water storage tank 16, an ambient temperature thermistor (not shown) for detecting the ambient temperature, and the temperature of the air refrigerant heat exchanger. An air heat exchange thermistor to detect, a thermistor (not shown) that detects the temperature of each part, a pressure sensor (not shown) that detects the discharge pressure of the compressors 1a and 1b, and a water level sensor 21 that detects the water level in the bathtub 24. Etc., and each detection signal is input to the operation control means 50. The operation control means 50 controls each device based on these signals.

なお、給湯混合弁１１は、給湯運転開始当初においては水冷媒熱交換器２側と湯水混合弁１２側間、及び貯湯タンク１６側と湯水混合弁１２側間が共に開となって、水冷媒熱交換器２及び貯湯タンク１６の両方から給湯し、ヒートポンプによる水冷媒熱交換器２での加熱温度が給湯温度（約４２℃）に達すると、貯湯タンク１６側と湯水混合弁１２側間を閉じて、水冷媒熱交換器２からのみ給湯する。 The hot water supply mixing valve 11 is opened at the beginning of the hot water supply operation so that the water refrigerant heat exchanger 2 side and the hot water mixing valve 12 side, and the hot water storage tank 16 side and the hot water mixing valve 12 side are both open. When hot water is supplied from both the heat exchanger 2 and the hot water storage tank 16 and the heating temperature in the water refrigerant heat exchanger 2 by the heat pump reaches the hot water supply temperature (about 42 ° C.), the hot water tank 16 side and the hot water mixing valve 12 side are connected. Close and supply hot water only from the water-refrigerant heat exchanger 2.

また、温水開閉弁２８は、水冷媒熱交換器２と風呂用熱交換器２７の間に設けられ、風呂追焚き時は開いて風呂追い焚き運転を行い、それ以外の時は水回路を閉じて水冷媒熱交換器２から風呂用熱交換器２７への熱の漏洩を防ぐためのものである。また、給水側逆止弁９は、一方向にのみに水を流し、逆流を防止するものである。 The hot water on / off valve 28 is provided between the water-refrigerant heat exchanger 2 and the bath heat exchanger 27. The hot water on / off valve 28 is opened when the bath is replenished to perform the bath retreat operation, and at other times the water circuit is closed. Thus, heat leakage from the water refrigerant heat exchanger 2 to the bath heat exchanger 27 is prevented. Further, the water supply side check valve 9 allows water to flow only in one direction to prevent backflow.

次に、本実施形態に係るヒートポンプ給湯機の運転動作について、図１のヒートポンプ冷媒回路３０及び給湯回路４０を参照しながら、図２の給湯運転フローチャートに基づいて説明する。図２は本発明の実施形態に係るヒートポンプ給湯機における、台所蛇口を開けて湯水を使用した場合の給湯運転の流れを示すフローチャートである。 Next, the operation of the heat pump water heater according to the present embodiment will be described based on the hot water supply operation flowchart of FIG. 2 with reference to the heat pump refrigerant circuit 30 and the hot water supply circuit 40 of FIG. FIG. 2 is a flowchart showing a flow of a hot water supply operation when the kitchen faucet is opened and hot water is used in the heat pump water heater according to the embodiment of the present invention.

台所蛇口１５を開けて湯水使用が始まる（ステップ６１）と、給水水量センサ８の検知で、運転制御手段５０は圧縮機１ａ，１ｂを運転させヒートポンプの冷媒回路３０の運転を開始するとともに、給水金具６、減圧弁７、給水水量センサ８、給水側逆止弁９、水熱交流量センサ１０、給水側伝熱管２ｃ、２ｄ、給湯混合弁１１、湯水混合弁１２、流量調整弁１３、台所出湯金具１４、台所蛇口１５の直接給湯回路により直接給湯運転を開始する（ステップ６２）。同時に、給水金具６、減圧弁７、給水水量センサ８、給水側逆止弁９、貯湯タンク１６、給湯混合弁１１、湯水混合弁１２、流量調整弁１３、台所出湯金具１４、台所蛇口１５のタンク給湯回路によりタンク給湯運転を開始する（ステップ６３）。 When the kitchen faucet 15 is opened and the use of hot water is started (step 61), the operation control means 50 operates the compressors 1a and 1b and starts the operation of the refrigerant circuit 30 of the heat pump by the detection of the water supply amount sensor 8, and the water supply Metal fitting 6, pressure reducing valve 7, feed water amount sensor 8, feed water side check valve 9, hydrothermal AC amount sensor 10, feed water side heat transfer tubes 2 c and 2 d, hot water mixing valve 11, hot water mixing valve 12, flow rate adjusting valve 13, kitchen The direct hot water supply operation is started by the direct hot water supply circuit of the hot metal fitting 14 and the kitchen faucet 15 (step 62). At the same time, the water supply fitting 6, the pressure reducing valve 7, the water supply amount sensor 8, the water supply side check valve 9, the hot water storage tank 16, the hot water supply mixing valve 11, the hot water mixing valve 12, the flow rate adjustment valve 13, the kitchen tapping metal 14, and the kitchen faucet 15. The tank hot water supply operation is started by the tank hot water supply circuit (step 63).

ここで、ヒートポンプ冷媒回路３０は、圧縮機１ａ，１ｂで圧縮された高温高圧冷媒を水冷媒熱交換器２の冷媒側伝熱管２ａ，２ｂへ送り込み、給水側伝熱管２ｃ，２ｄ内を流れる水を加熱して給湯混合弁１１側へ循環させるが、運転直後の立上がり時は水冷媒熱交換器２へ送り込まれてくる冷媒が十分に高温高圧となりきらず温度が低く、かつ水冷媒熱交換器２全体が冷えているため、水を加熱する加熱能力が十分ではないため、貯湯タンク１６からの高温水を供給するタンク給湯（ステップ６３）が必要となる。時間の経過と共に冷媒は高温高圧となり、それに従って、発生する冷媒からの放熱量が増加し、水への加熱能力が増してゆく。 Here, the heat pump refrigerant circuit 30 sends the high-temperature and high-pressure refrigerant compressed by the compressors 1a and 1b to the refrigerant-side heat transfer tubes 2a and 2b of the water-refrigerant heat exchanger 2, and the water flowing in the water-supply-side heat transfer tubes 2c and 2d. Is heated and circulated to the hot water supply mixing valve 11 side, but at the time of start-up immediately after the operation, the refrigerant sent to the water refrigerant heat exchanger 2 is not sufficiently high-temperature and high-pressure and the temperature is low, and the water-refrigerant heat exchanger 2 Since the whole is cold, the heating capacity for heating the water is not sufficient, so a tank hot water supply (step 63) for supplying high-temperature water from the hot water storage tank 16 is required. As the time elapses, the refrigerant becomes high temperature and pressure, and accordingly, the amount of heat released from the generated refrigerant increases, and the ability to heat water increases.

ヒートポンプ運転の加熱能力が適温状態に達するまでには数分かかるため、運転制御手段５０は、運転開始から適温状態に達するまでの間は、圧縮機１ａ，１ｂの回転数を定常時より高速にすると共に、貯湯タンク１６から高温水を供給するタンク給湯運転（ステップ６３）を並行して行い、台所蛇口１５からは適温水を給湯する。また、ヒートポンプ運転による加熱温度判定（ステップ６４）を行い、規定未満であれば直接給湯とタンク給湯の並行運転を継続し、規定以上に達すればタンク給湯を停止（ステップ６５）して、直接給湯の単独運転による給湯を継続する（ステップ６６）。 Since it takes several minutes for the heating capacity of the heat pump operation to reach an appropriate temperature state, the operation control means 50 increases the rotation speed of the compressors 1a and 1b at a higher speed than in the steady state from the start of operation to the arrival of the appropriate temperature state. At the same time, a tank hot water supply operation (step 63) for supplying high-temperature water from the hot water storage tank 16 is performed in parallel, and appropriate hot water is supplied from the kitchen faucet 15. Further, the heating temperature is determined by the heat pump operation (step 64). If the temperature is less than the specified value, the parallel hot water supply and the tank hot water operation are continued. If the specified temperature is exceeded, the tank hot water supply is stopped (step 65). The hot water supply by the single operation is continued (step 66).

なお、運転制御手段５０は、給湯混合弁１１後の混合湯温が適温よりかなり低い場合はタンク給湯量を増やし、適温にほぼ近くなるに従ってタンク給湯量を減らすように給湯混合弁１１を作動させ、流量比率を調整して適温とする。更に、給湯混合弁１１通過後の混合湯温が適温より高い場合には湯水混合弁１２からの給水量を調整することによっても使用端末への給湯温度の調整を行なうことができる。 The operation control means 50 operates the hot water supply mixing valve 11 to increase the tank hot water supply amount when the mixed hot water temperature after the hot water supply mixing valve 11 is considerably lower than the appropriate temperature, and to decrease the tank hot water supply amount as the temperature approaches the appropriate temperature. Adjust the flow rate ratio to make it suitable temperature. Furthermore, when the mixed hot water temperature after passing through the hot water mixing valve 11 is higher than the appropriate temperature, the hot water supply temperature to the use terminal can be adjusted also by adjusting the amount of water supplied from the hot water mixing valve 12.

従って、貯湯タンク１６の役割は、ヒートポンプ運転の加熱能力が、給湯温度に十分な温度に達するまでの立上がり時の補助的なものであり、ヒートポンプ冷媒回路３０の能力、特に圧縮機１ａ，１ｂの出力が大きいほど、立上げ時間を短くでき、貯湯タンク１６の容量を小さくできる。また、台所給湯と同時に風呂湯張りを行なう等のように複数箇所の同時使用に直接給湯のみで対応するには、圧縮機１ａ，１ｂの容量は、従来の貯湯式で一般に用いられている５ｋＷ程度に対し２０ｋＷ程度まで大きくすることが望ましいが、新規圧縮機の開発が必要であるばかりでなく、ヒートポンプ冷媒回路３０の各部品は新規検討が必要となり、極めて困難である。 Therefore, the role of the hot water storage tank 16 is an auxiliary one at the time of start-up until the heating capacity of the heat pump operation reaches a temperature sufficient for the hot water supply temperature, and the capacity of the heat pump refrigerant circuit 30, particularly the compressors 1a and 1b. The larger the output, the shorter the startup time and the smaller the capacity of the hot water storage tank 16. In addition, in order to cope with simultaneous use of a plurality of locations by using only direct hot water supply such as performing hot water bathing at the same time as kitchen hot water supply, the capacity of the compressors 1a and 1b is 5 kW which is generally used in a conventional hot water storage system. Although it is desirable to increase it to about 20 kW, the development of a new compressor is necessary, and each part of the heat pump refrigerant circuit 30 needs to be newly studied, which is extremely difficult.

そこで本発明の実施形態においては、従来圧縮機の２倍程度の圧縮機を２個使用した２サイクルヒートポンプ方式３０ａ，３０ｂとし、従来技術の活用と、実績による信頼性を確保したものであり、圧縮機の容量が十分であれば、１サイクルヒートポンプ方式においても本発明の適用・効果は変わらない。 Therefore, in the embodiment of the present invention, the two-cycle heat pump system 30a, 30b using two compressors about twice as large as the conventional compressor is used, and the reliability of the conventional technology and the results are ensured, If the capacity of the compressor is sufficient, the application and effect of the present invention will not change even in the one-cycle heat pump system.

次に、運転立ち上がり時が過ぎて直接給湯の単独運転になると（ステップ６６）、周囲温度（外気温度）、空気冷媒熱交換器４ａ，４ｂの温度、及び給湯モード（図２では台所給湯）を判定項目とした（ステップ６７）判定基準に基づき最適運転手段の判定を行なう（ステップ６８）。 Next, when the operation start time has passed and direct hot water supply operation is started (step 66), the ambient temperature (outside air temperature), the temperature of the air refrigerant heat exchangers 4a and 4b, and the hot water supply mode (kitchen hot water in FIG. 2) are changed. The optimum driving means is determined on the basis of the determination criterion (step 67) as a determination item (step 68).

最適運転手段の判定（ステップ６８）により、手段Ａと判定された場合は加熱効率優先運転（ステップ６９）、手段Ｂと判定された場合は加熱能力優先運転（ステップ７０）、手段Ｃと判定された場合は中間除霜運転（後述するが、給湯運転の途中で除霜運転を行うこと）として直接給湯運転（ステップ７１）を継続する。 When it is determined as the means A by the determination of the optimum operation means (step 68), the heating efficiency priority operation (step 69) is determined, and when it is determined as the means B, the heating capacity priority operation (step 70) is determined as the means C. If this occurs, the hot water supply operation (step 71) is continued as an intermediate defrost operation (which will be described later, the defrost operation is performed during the hot water supply operation).

その後、湯水使用が終了する（ステップ７２）と、直接給湯を停止する（ステップ７３）とともに、空気冷媒熱交換器４ａ，４ｂの着霜判定を行ない（ステップ７４）、着霜していると判定した場合（例えば周囲温度が０℃以下の場合は着霜と判定する）は除霜運転を行なってから（ステップ７５）、ヒートポンプ運転を停止し（ステップ７６）、着霜していないと判定した場合は除霜運転を行なわずにヒートポンプ運転を停止する（ステップ７６）。 Thereafter, when the use of hot water is finished (step 72), the hot water supply is stopped directly (step 73), and the frost formation of the air refrigerant heat exchangers 4a and 4b is performed (step 74), and it is determined that the frost is formed. (For example, when the ambient temperature is 0 ° C. or less, it is determined that frost is formed.) After performing the defrosting operation (step 75), the heat pump operation is stopped (step 76), and it is determined that frost is not formed. In this case, the heat pump operation is stopped without performing the defrosting operation (step 76).

次に、図３と図４を参照しながら、本実施形態に係るヒートポンプ給湯機の最適運転制御手段の判定基準および最適運転手段Ａ，Ｂ，Ｃの内容について説明する。図３は一般的なヒートポンプ給湯機における加熱能力と加熱効率の関係を示す表である。図４は本実施形態に係るヒートポンプ給湯機における最適運転手段を決定する判定条件と判定基準を示す表である。 Next, with reference to FIG. 3 and FIG. 4, the determination criteria of the optimum operation control means and the contents of the optimum operation means A, B, C of the heat pump water heater according to this embodiment will be described. FIG. 3 is a table showing the relationship between the heating capacity and the heating efficiency in a general heat pump water heater. FIG. 4 is a table showing determination conditions and determination criteria for determining the optimum operation means in the heat pump water heater according to the present embodiment.

図３は、ヒートポンプ運転時の加熱能力と加熱効率の関係を示すもので、線図Ａは台所給湯（約４２℃）の場合、線図Ｂはタンク貯湯（タンクへの給湯であり前述の貯湯回路（１）のこと）（約６５℃）の場合を示し、一定の給湯温度においては、加熱能力を上げるほど加熱効率が低下することを示す。これは、加熱能力を増すためには圧縮機の回転数を上げて高速回転にするため、圧縮機の機械ロスが増えることによるもので、自動車において通常速度に対し高速走行時はガソリンの燃費効率が低下することと同様である。 FIG. 3 shows the relationship between the heating capacity and the heating efficiency during heat pump operation. Diagram A shows the case of kitchen hot water supply (about 42 ° C.), and diagram B shows the tank hot water (hot water supply to the tank. Circuit (1)) (approx. 65 ° C.), and at a constant hot water supply temperature, the heating efficiency decreases as the heating capacity increases. This is because in order to increase the heating capacity, the compressor speed is increased to a higher speed, which increases the mechanical loss of the compressor. Is the same as lowering.

図３の線図Ａは、一定の条件、例えば周囲温度１６℃、給水温度１７℃において、一定の流量（例えば５Ｌ／分）以上で、台所給湯温度（約４２℃）まで加熱するためには最低の加熱能力Ａｍｉｎが必要である。次に、加熱能力Ａｍｉｎから加熱能力を増していくと、次第に加熱効率が低下し加熱能力最大点Ａｍａｘに達する。線図Ｂは線図Ａと同一条件において、タンク貯湯運転（前述の貯湯回路（１）の運転）を行なう場合で、タンク貯湯温度（約６５℃）まで加熱するためには最低の加熱能力Ｂｍｉｎが必要であり、加熱能力Ｂｍｉｎから加熱能力を増していくと、次第に加熱効率が低下し加熱能力最大点Ｂｍａｘに達する。なお、加熱能力最大点Ａｍａｘ、Ｂｍａｘは、ヒートポンプの加熱能力、及び給湯温度、給湯流量等によっても異なる。 The diagram A in FIG. 3 shows how to heat to a kitchen hot water supply temperature (about 42 ° C.) at a constant flow rate (for example, 5 L / min) or more at a certain condition, for example, an ambient temperature of 16 ° C. A minimum heating capacity Amin is required. Next, as the heating capacity is increased from the heating capacity Amin, the heating efficiency gradually decreases and reaches the maximum heating capacity point Amax. Diagram B shows the case where tank hot water storage operation (operation of the aforementioned hot water storage circuit (1)) is performed under the same conditions as diagram A, and the minimum heating capacity Bmin for heating to the tank hot water temperature (about 65 ° C.). When the heating capacity is increased from the heating capacity Bmin, the heating efficiency gradually decreases and reaches the maximum heating capacity point Bmax. The heating capacity maximum points Amax and Bmax vary depending on the heating capacity of the heat pump, the hot water supply temperature, the hot water supply flow rate, and the like.

線図Ａと線図Ｂから解かる様に、同一条件においては給湯温度が高いほど大きな加熱能力を必要とするため、加熱能力を上げた場合と同様に給湯温度が高いと加熱効率は低下する。 As can be seen from the diagrams A and B, under the same conditions, the higher the hot water supply temperature, the larger the heating capacity is required. Therefore, the heating efficiency decreases when the hot water supply temperature is high, as in the case of increasing the heating capacity. .

次に、図４に最適運転手段判定基準の一例を示す。運転条件としては、周囲温度（外気温度）、空気冷媒熱交換器温度、及び給湯モードの３項目を設ける。周囲温度は温度が高い又は絶対湿度が低いためほとんど着霜しない＋７℃以上または−７℃以下と、着霜し易い−７℃〜＋７℃に分け、空気冷媒熱交換器温度は０℃以上と０℃未満に分ける（熱交換器温度が０℃以上であれば霜は付き難い）。一方、給湯モードはタンク貯湯、台所・洗面給湯、風呂湯張り、シャワー、及び各モード共通で６０分以上の給湯モードに区分する。区分けした給湯モード毎に、周囲温度及び空気冷媒熱交換器温度の区分に対応して、最適運転手段を規定しておき、これらの条件を当てはめることで、最適運転手段として、Ａ（加熱効率優先運転）、Ｂ（加熱能力優先運転）、Ｃ（中間除霜運転）を判定する。 Next, FIG. 4 shows an example of the optimum driving means determination criterion. As operating conditions, three items of ambient temperature (outside air temperature), air refrigerant heat exchanger temperature, and hot water supply mode are provided. Ambient temperature is divided into -7 ° C to + 7 ° C, where the temperature is high or the absolute humidity is low and hardly frosts, and -7 ° C to + 7 ° C, and the air refrigerant heat exchanger temperature is 0 ° C or higher. Divide into less than 0 ° C (if the heat exchanger temperature is 0 ° C or higher, frost is unlikely). On the other hand, the hot water supply mode is divided into tank hot water storage, kitchen hot water supply, bath hot water, shower, and hot water supply mode of 60 minutes or more common to each mode. For each divided hot water supply mode, the optimum operation means is defined corresponding to the classification of the ambient temperature and the air refrigerant heat exchanger temperature, and by applying these conditions, A (heating efficiency priority) Operation), B (heating capacity priority operation), and C (intermediate defrosting operation) are determined.

なお、周囲温度について着霜しない温度領域と着霜し易い温度領域の２段階に分けているが、これに限らず、着霜し易い領域−７℃〜＋７℃をさらに２段階に分けて，例えば、最も着霜し易い−２℃〜＋３℃と、この領域を外れた−７℃〜＋７℃範囲内の温度領域とに分けて、トータルで３つの領域に区分けしてよく、−２℃〜＋３℃の場合には、膨張弁の開度をさらに開けて除霜を行うように制御しても良い。 In addition, although it is divided into two stages of a temperature region where frost is not formed and a temperature region where frost is easy to be formed with respect to the ambient temperature, not limited to this, the region where frost is easily formed −7 ° C. to + 7 ° C. For example, it may be divided into a total of three regions by dividing into −7 ° C. to + 3 ° C., which is most likely to form frost, and a temperature region within the range of −7 ° C. to + 7 ° C., which is outside this region. In the case of ˜ + 3 ° C., the defrosting may be performed by further opening the expansion valve.

図４に示す例示において、タンク貯湯運転を１５０Ｌで区分したのは、冬期高温沸き上げ（約８０℃〜９０℃）時に６０分前後の区別を推定したものであり、ヒートポンプの加熱能力等により区分容量は異なってくる。また、湯張り、シャワーを加熱能力優先Ｂとしたのは、入浴までの待ち時間を短くすること、及びシャワー時の給湯量不足を避けるためであるが、予約時間による自動湯張りや、特に強い水勢を必要としないシャワーを推定する場合は運転効率優先Ａと判定しても良い。 In the illustration shown in FIG. 4, the tank hot water storage operation is divided into 150 L because the distinction is estimated around 60 minutes at the time of high temperature boiling in winter (about 80 ° C. to 90 ° C.). The capacity will be different. In addition, the reason why the hot water filling and the shower are set to the heating capacity priority B is to shorten the waiting time until bathing and to avoid the shortage of hot water supply at the time of showering. When estimating a shower that does not require water, the operation efficiency priority A may be determined.

ここで、最適運転手段のＡは主に加熱効率を優先した運転制御を行なうもので、図３におけるＡｍｉｎやＢｍｉｎを目標とした加熱効率最大運転を行なう。最適運転手段のＢは主に加熱能力を優先した運転制御を行なうもので、図３におけるＡｍａｘやＢｍａｘを目標とした加熱能力最大運転を行なう。また、最適運転手段のＣは中間除霜運転（給湯運転の途中での除霜運転）を行なうものであるが、これは、冬期低温時における着霜による加熱効率低下を考慮した着霜期最適運転手段であり、図５〜図７を用いて以下説明する。 Here, the optimum operation means A performs operation control mainly giving priority to the heating efficiency, and performs the maximum heating efficiency operation targeting Amin and Bmin in FIG. The optimum operation means B performs operation control mainly giving priority to the heating capacity, and performs the maximum heating capacity operation targeting Amax and Bmax in FIG. In addition, the optimum operating means C performs an intermediate defrosting operation (defrosting operation in the middle of a hot water supply operation). This is an optimum operation in the frosting period in consideration of a decrease in heating efficiency due to frosting at low temperatures in winter. This will be described below with reference to FIGS.

図５は一般的なヒートポンプ給湯機における冬期連続運転した場合の加熱能力の時間的変化を表す表である。図５の線Ａは冬期低温時（周囲温度約−７℃〜＋７℃）において、連続運転した場合の運転時間と加熱能力の変化を示す。運転時間の経過と共に空気冷媒熱交換器４ａ，４ｂの表面に着霜して約３０分経過頃から空気冷媒熱交換器の熱交換性能が低下し加熱能力が低下する。運転初期の加熱能力を１００％とした場合、約１時間経過後には５０％以下に低下してしまうこともあり、除霜運転が必要となる。 FIG. 5 is a table showing temporal changes in heating capacity when a general heat pump water heater is operated continuously in winter. Line A in FIG. 5 shows changes in operating time and heating capacity when continuously operating at low temperatures in winter (ambient temperature of about −7 ° C. to + 7 ° C.). As the operating time elapses, the air refrigerant heat exchangers 4a and 4b are frosted on the surface, and the heat exchange performance of the air refrigerant heat exchanger is lowered and the heating capacity is lowered after about 30 minutes. When the heating capacity at the initial stage of operation is set to 100%, it may be reduced to 50% or less after the lapse of about 1 hour, and a defrosting operation is necessary.

給湯運転の途中に除霜運転を行なえば再び初期の加熱能力に回復するが、除霜運転は給湯を停止するので、給湯量ゼロの状態で消費電力を必要とし、加熱効率の低下につながるため、３０分以上の連続給湯運転する場合は、途中に除霜運転を行なうか、除霜運転を行なわずに加熱能力が低下したまま給湯運転を続けるかを判断するのは、使用条件や給湯運転時間など複雑に絡んだ難しい課題である。 If the defrosting operation is performed during the hot water supply operation, the initial heating capacity is restored again, but the defrosting operation stops the hot water supply, requiring power consumption with no hot water supply, leading to a decrease in heating efficiency. In the case of continuous hot water supply operation for 30 minutes or more, whether to perform defrosting operation in the middle or whether to continue hot water supply operation with reduced heating capacity without performing defrosting operation depends on usage conditions and hot water supply operation It is a difficult task involving time and complexity.

本実施形態は、この課題に対し最適な運転制御方法として、図４に示す最適運転制御判定基準によって、１５０Ｌ以上のタンク貯湯時、及び使用条件や学習制御により推定給湯時間が１時間以上と判断した場合は中間除霜運転Ｃを選択し、推定給湯時間の約１／２時間給湯運転経過時に除霜運転を行なうものである。ここで、推定運転時間が６０分以上の給湯モードというのは、例えば、或る給湯モードで午後６時になると決まって６０分以上給湯するという状況を毎日の経験で学習すると、当日の午後６時になって当該或る給湯モードが開始されると、学習効果で６０分以上の給湯モードであると推定される。 In the present embodiment, as an optimal operation control method for this problem, it is determined that the estimated hot water supply time is 1 hour or more when storing tanks of 150 L or more, and by use conditions and learning control, based on the optimal operation control criteria shown in FIG. In this case, the intermediate defrosting operation C is selected, and the defrosting operation is performed when the hot water supply operation has elapsed for about 1/2 hour of the estimated hot water supply time. Here, the hot water supply mode in which the estimated operation time is 60 minutes or more is, for example, that if it is learned from a daily experience that a hot water supply is 60 minutes or longer in a certain hot water mode, Thus, when the certain hot water supply mode is started, it is estimated that the hot water supply mode is 60 minutes or longer due to the learning effect.

図６は本実施形態に係るヒートポンプ給湯機において冬期で推定給湯時間が長い場合の連続運転と中間除霜運転とでの加熱量の比較を示す説明図である。図６では、推定給湯時間が約７０分の場合の加熱能力変化を示すもので、連続給湯運転を行った場合は線Ａ１のようになり、線Ａ1の下側面積が７０分間の合計加熱量となる。 FIG. 6 is an explanatory diagram showing a comparison of heating amounts between the continuous operation and the intermediate defrosting operation when the estimated hot water supply time is long in winter in the heat pump water heater according to the present embodiment. FIG. 6 shows the change in heating capacity when the estimated hot water supply time is about 70 minutes. When the continuous hot water supply operation is performed, the heating capacity changes as shown by line A1, and the total heating amount for the lower area of line A1 is 70 minutes. It becomes.

本実施形態においては、推定給湯時間が６０分以上なので中間除霜運転と判定し、線Ｂ1と線Ｂ２の破線で示すように約１／２経過時の３０分過ぎに除霜運転を行ない、線Ｂ1及び線Ｂ２の下側面積が７０分間の合計加熱量となる。ここで、７０分間の合計加熱量を比較した場合、図６からも明らかなように、連続給湯運転時の着霜による加熱量低下分Ｅ（Ｂ２の破線からＡ１の実線部分を減算した分）よりも、除霜運転による加熱量低下分Ｄ（３０分経過後の除霜運転で加熱量が無くなった分）の方が少ないため、中間除霜運転（Ｂ１とＢ２）の方が連続運転（Ａ１）よりも加熱量が多くなり、運転の全体として加熱効率が良いことになる。 In this embodiment, since the estimated hot water supply time is 60 minutes or more, it is determined as an intermediate defrosting operation, and the defrosting operation is performed after about 30 minutes at the time of about ½ as shown by the broken lines of lines B1 and B2. The lower area of line B1 and line B2 is the total heating amount for 70 minutes. Here, when the total heating amount for 70 minutes is compared, as is clear from FIG. 6, the heating amount decrease E due to frost formation during continuous hot water supply operation (the amount obtained by subtracting the solid line portion of A1 from the broken line of B2) Since there is less heating amount decrease D due to the defrosting operation (the amount of heating lost in the defrosting operation after 30 minutes), the intermediate defrosting operation (B1 and B2) is the continuous operation ( The amount of heating is larger than in A1), and the heating efficiency is good as a whole of the operation.

図７は本実施形態に係るヒートポンプ給湯機において冬期で推定給湯時間が短い場合の連続運転と中間除霜運転とでの加熱量の比較を示す説明図である。図７では、推定給湯時間が６０分未満の例として５０分の場合について説明する。連続給湯運転を行った場合は線Ａ２のように、時間が短い分加熱能力低下分Ｅが少なくなり、中間に除霜運転を行なった場合の除霜による加熱量低下分Ｄよりも少なくなる。従って、線Ａ２の下側面積で表わされる連続運転による合計加熱量は、線Ｃ１，Ｃ２の下側面積で表わされる中間除霜運転による合計加熱量よりも多く、連続運転の方が中間除霜運転よりも加熱効率が良いことになる。 FIG. 7 is an explanatory diagram showing a comparison of heating amounts between the continuous operation and the intermediate defrosting operation when the estimated hot water supply time is short in winter in the heat pump water heater according to the present embodiment. In FIG. 7, a case where the estimated hot water supply time is 50 minutes will be described as an example of less than 60 minutes. When the continuous hot water supply operation is performed, as shown by line A2, the heating capacity decrease E decreases as the time is short, and the heating amount decrease D due to defrosting decreases when the defrost operation is performed in the middle. Therefore, the total heating amount by the continuous operation represented by the lower area of the line A2 is larger than the total heating amount by the intermediate defrosting operation represented by the lower area of the lines C1 and C2, and the continuous operation is more intermediate defrosting. Heating efficiency is better than operation.

以上説明したように、本発明の実施形態の特徴は、周囲温度、空気冷媒熱交換器温度、給湯モードを判定基準として最適運転手段を判定し、前記判定に基づき加熱効率優先運転、加熱能力優先運転、中間除霜運転のうち最適な運転手段を選択して総合的に最適な運転制御を行ない、必要とする加熱能力の確保、加熱効率の向上及び省エネを図るものである。その特徴の具体的な構成は、圧縮機、水と冷媒との熱交換を行なう水冷媒熱交換器、膨張弁、空気と冷媒との熱交換を行なう空気冷媒熱交換器を、冷媒配管を介して順次接続したヒートポンプ冷媒回路と、前記水冷媒熱交換器、給湯混合弁、水冷媒熱交換器で加熱した温水を貯めておくための貯湯タンク、機内循環ポンプ、及びこれらの部品間を接続する水配管からなる貯湯回路と、給水金具、前記貯湯タンク、給湯混合弁、湯水混合弁、流量調整弁、出湯金具、及びこれらの部品間を接続する水配管からなるタンク給湯回路と、前記圧縮機、膨張弁、給湯混合弁、機内循環ポンプ、湯水混合弁、流量調整弁、等の動作を制御する運転制御手段と、を備え、前記運転制御手段は、周囲温度または空気冷媒熱交換器温度、及び給湯モードに準拠した最適運転手段の判定基準により最適運転手段を判定し、前記最適運転手段として、少なくとも加熱効率優先運転、加熱能力優先運転、及び中間除霜運転の３種類の運転手段を設けた最適運転制御手段を有するものである。 As described above, the feature of the embodiment of the present invention is that the optimum operation means is determined based on the ambient temperature, the air refrigerant heat exchanger temperature, and the hot water supply mode as the determination criteria, and the heating efficiency priority operation and the heating capacity priority are based on the determination. The optimum operation means is selected from the operation and the intermediate defrosting operation, and the optimum operation control is performed comprehensively to ensure the necessary heating capacity, improve the heating efficiency, and save energy. The specific configuration of the features includes a compressor, a water refrigerant heat exchanger that performs heat exchange between water and refrigerant, an expansion valve, and an air refrigerant heat exchanger that performs heat exchange between air and refrigerant via a refrigerant pipe. The heat pump refrigerant circuit sequentially connected to the water refrigerant heat exchanger, the hot water supply mixing valve, the hot water storage tank for storing hot water heated by the water refrigerant heat exchanger, the in-machine circulation pump, and these components are connected to each other. Hot water storage circuit consisting of water piping, water supply fitting, hot water storage tank, hot water supply mixing valve, hot water mixing valve, flow rate adjustment valve, outlet metal fitting, and tank hot water supply circuit consisting of water piping connecting these components, and the compressor An operation control means for controlling the operation of an expansion valve, a hot water supply mixing valve, an in-machine circulation pump, a hot water mixing valve, a flow rate adjustment valve, etc., and the operation control means comprises an ambient temperature or an air refrigerant heat exchanger temperature, And hot water supply mode Optimal operation means is determined based on the determination criteria of the optimum operation means, and at least three types of operation means of heating efficiency priority operation, heating capacity priority operation, and intermediate defrost operation are provided as the optimum operation means. It is what has.

このように、本実施形態の運転制御手段は、推定給湯時間により、給湯時間が長くて中間除霜運転の方が効率の良い場合は中間除霜運転を行ない、給湯時間が短く連続運転した方が効率の良い場合は連続運転を行なうもので、着霜期における最適運転を行なうことができることが具体的特徴の１つである。そして、本実施形態の運転制御手段は、周囲温度（外気温度）、空気冷媒熱交換器温度、及び給湯モードに準拠した最適運転手段の判定基準により、加熱効率優先運転、加熱能力優先運転、及び中間除霜運転を判定して最適運転手段を選択するものであり、本実施形態では直接給湯運転を行なう瞬間式ヒートポンプ給湯機に適用した場合について説明したが、貯湯式ヒートポンプ給湯機においても、貯湯タンクの容量が大きく学習制御により日々貯湯量を変えて使用する場合等には本実施形態を適用することにより瞬間式同様の効果を得ることができる。 Thus, the operation control means of this embodiment performs the intermediate defrosting operation when the hot water supply time is longer and the intermediate defrosting operation is more efficient due to the estimated hot water supply time, and the hot water supply time is shorter and continuously operated. However, one of the specific features is that the continuous operation is performed when the efficiency is high, and the optimal operation in the frosting period can be performed. And the operation control means of this embodiment is a heating efficiency priority operation, a heating capacity priority operation, and an optimum operation means determination standard based on the ambient temperature (outside air temperature), the air refrigerant heat exchanger temperature, and the hot water supply mode, and The intermediate defrosting operation is determined and the optimum operation means is selected. In this embodiment, the case where the present invention is applied to an instantaneous heat pump water heater that performs a direct hot water supply operation has been described. When the capacity of the tank is large and the hot water storage amount is changed every day by learning control, the same effect as that of the instantaneous type can be obtained by applying this embodiment.

本発明の実施形態に係るヒートポンプ給湯機の構成要素と接続経路を示す全体構成図である。It is a whole block diagram which shows the component and connection path | route of a heat pump water heater which concern on embodiment of this invention. 本発明の実施形態に係るヒートポンプ給湯機における、台所蛇口を開けて湯水を使用した場合の給湯運転の流れを示すフローチャートである。It is a flowchart which shows the flow of the hot water supply operation | movement at the time of opening a kitchen faucet and using hot water in the heat pump water heater which concerns on embodiment of this invention. 一般的なヒートポンプ給湯機における加熱能力と加熱効率の関係を示す表である。It is a table | surface which shows the relationship between the heating capability and heating efficiency in a general heat pump water heater. 本実施形態に係るヒートポンプ給湯機における最適運転手段を決定する判定条件と判定基準を示す表である。It is a table | surface which shows the determination conditions and determination criteria which determine the optimal driving | operation means in the heat pump water heater which concerns on this embodiment. 一般的なヒートポンプ給湯機における冬期連続運転した場合の加熱能力の時間的変化を表す表である。It is a table | surface showing the time change of the heating capability at the time of the winter continuous operation in a general heat pump water heater. 本実施形態に係るヒートポンプ給湯機において冬期で推定給湯時間が長い（例、７０分）場合の連続運転と中間除霜運転の加熱量の比較を示す説明図である。In the heat pump water heater which concerns on this embodiment, it is explanatory drawing which shows the comparison of the heating amount of a continuous driving | operation and intermediate | middle defrosting operation in case the estimated hot water supply time is long in winter (for example, 70 minutes). 本実施形態に係るヒートポンプ給湯機において冬期で推定給湯時間が短い（例、５０分）場合の連続運転と中間除霜運転の加熱量の比較を示す説明図である。In the heat pump water heater which concerns on this embodiment, it is explanatory drawing which shows the comparison of the heating amount of a continuous driving | operation and intermediate | middle defrosting operation in case the estimated hot water supply time is short (for example, 50 minutes) in winter.

符号の説明Explanation of symbols

１ａ，１ｂ圧縮機
２水冷媒熱交換器
３a，３ｂ膨張弁
４ａ，４ｂ空気冷媒熱交換器
６給水金具
７減圧弁
８給水水量センサ
１１給湯混合弁
１２湯水混合弁
１３流量調整弁
１４台所出湯金具
１５台所蛇口
１６貯湯タンク
１７機内循環ポンプ
１８風呂注湯弁
２０風呂循環ポンプ
２４浴槽
２５風呂蛇口
２７風呂用熱交換器
２８温水開閉弁
３０ヒートポンプ冷媒回路
４０給湯回路
５０運転制御手段 DESCRIPTION OF SYMBOLS 1a, 1b Compressor 2 Water refrigerant heat exchanger 3a, 3b Expansion valve 4a, 4b Air refrigerant heat exchanger 6 Water supply metal fitting 7 Pressure reducing valve 8 Water supply amount sensor 11 Hot water mixing valve 12 Hot water mixing valve 13 Flow rate adjusting valve 14 Kitchen outlet metal fitting DESCRIPTION OF SYMBOLS 15 Kitchen faucet 16 Hot water storage tank 17 In-machine circulation pump 18 Bath pouring valve 20 Bath circulation pump 24 Bathtub 25 Bath faucet 27 Bath heat exchanger 28 Hot water on-off valve 30 Heat pump refrigerant circuit 40 Hot water supply circuit 50 Operation control means

Claims

冷媒を圧縮する圧縮機、水と冷媒との熱交換を行なう水冷媒熱交換器、膨張弁、空気と冷媒との熱交換を行なう空気冷媒熱交換器、冷媒配管、を有するヒートポンプ冷媒回路と、
前記水冷媒熱交換器で加熱した温水を貯めて置く貯湯タンク、機内循環ポンプ、給湯混合弁、前記水冷媒熱交換器で加熱した温水との熱交換を行う風呂用熱交換器、風呂循環用ポンプ、湯水混合弁、水配管、を有して、前記貯湯タンクに高温水を貯める貯湯回路、前記水冷媒熱交換器で加熱した温水を出湯箇所に直接給湯する直接給湯回路、前記貯湯タンクからの温水を出湯箇所に給湯するタンク給湯回路、前記水冷媒熱交換器で加熱した温水を前記風呂循環用ポンプで風呂に給湯する風呂湯張り回路、前記風呂用熱交換器からの温水を前記風呂循環用ポンプで風呂に給湯する風呂追焚回路、を形成する給湯回路と、
出湯箇所リモコンと風呂リモコンの操作設定で、各構成要素を制御して貯湯運転、直接給湯運転、タンク給湯運転、風呂湯張り運転、風呂追焚運転を行う運転制御部と、を備えたヒートポンプ給湯機であって、
前記運転制御部は、ヒートポンプ給湯機の周囲温度と、前記空気冷媒熱交換器の温度と、及びタンクへの貯湯、出湯箇所への給湯、風呂湯張り、所定時間以上の運転での給湯、を含む給湯・貯湯モードと、を判定基準として、加熱効率優先運転、加熱能力優先運転、中間除霜運転、の３種類の運転手段のいずれかを判定する最適運転制御を行う
ことを特徴とするヒートポンプ給湯機。 A heat pump refrigerant circuit having a compressor for compressing refrigerant, a water refrigerant heat exchanger for exchanging heat between water and refrigerant, an expansion valve, an air refrigerant heat exchanger for exchanging heat between air and refrigerant, and a refrigerant pipe;
Hot water storage tank for storing hot water heated by the water refrigerant heat exchanger, in-machine circulation pump, hot water mixing valve, bath heat exchanger for exchanging heat with hot water heated by the water refrigerant heat exchanger, for bath circulation A hot water storage circuit for storing hot water in the hot water storage tank, a direct hot water supply circuit for directly supplying hot water heated by the water refrigerant heat exchanger to a hot water outlet, A hot water supply circuit for supplying hot water to a hot water outlet, a hot water heating circuit for supplying hot water heated by the water-refrigerant heat exchanger to the bath with the pump for circulating the bath, and hot water from the heat exchanger for bath to the bath A hot water supply circuit forming a bath memorial circuit for supplying hot water to the bath with a circulation pump;
A heat pump hot water supply comprising an operation control unit for controlling hot water storage operation, direct hot water supply operation, tank hot water supply operation, bath hot water operation, and bath memorial operation by controlling each component by operating settings of the hot water remote control and bath remote control Machine,
The operation control unit includes an ambient temperature of the heat pump water heater, a temperature of the air refrigerant heat exchanger, hot water storage in a tank, hot water supply to a hot water outlet, bath hot water filling, hot water supply in operation for a predetermined time or more. A heat pump that performs optimum operation control to determine one of three types of operation means: heating efficiency priority operation, heating capacity priority operation, and intermediate defrosting operation, using the hot water supply / storage mode including Water heater.

請求項１において、
前記運転制御部は、前記加熱効率優先運転と判定した場合は加熱効率が最大となるような圧縮機回転数で運転し、前記加熱能力優先運転と判定した場合は加熱能力が最大となるような圧縮機回転数で運転し、前記中間除霜運転と判定した場合は加熱能力が最大となるような圧縮機回転数で運転し且つ推定されるヒートポンプ運転時間の約１／２の時間経過後に除霜運転を行なう
ことを特徴とするヒートポンプ給湯機。 In claim 1,
The operation control unit operates at a compressor rotation speed that maximizes the heating efficiency when it is determined as the heating efficiency priority operation, and the heating capacity is maximized when it is determined as the heating capacity priority operation. If the operation is performed at the compressor speed and the intermediate defrosting operation is determined, the operation is performed at the compressor speed at which the heating capacity is maximized, and the removal is performed after about half of the estimated heat pump operation time. A heat pump water heater characterized by performing frost operation.

請求項１または２において、
前記運転制御部は、前記判定基準として、前記周囲温度を約＋７℃以上または約−7℃以下と、約−7℃〜＋７℃の少なくとも２つ以上に区分する
ことを特徴とするヒートポンプ給湯機。 In claim 1 or 2,
The operation control unit divides the ambient temperature into at least two of about + 7 ° C. or more and about −7 ° C. or less and about −7 ° C. to + 7 ° C. as the determination criterion. .

請求項１または２において、
前記運転制御部は、前記判定基準として、前記空気冷媒熱交換器温度を約０℃以上と約０℃未満の２つに区分する
ことを特徴とするヒートポンプ給湯機。 In claim 1 or 2,
The operation control unit divides the air refrigerant heat exchanger temperature into two, that is, about 0 ° C. or more and less than about 0 ° C. as the determination criterion.

請求項１または２において、
前記運転制御部は、前記判定基準として、給湯モード毎にヒートポンプ運転時間を学習し、推定運転時間が約６０分以上の給湯モードの場合、最適運転制御として中間除霜運転と判定する
ことを特徴とするヒートポンプ給湯機。 In claim 1 or 2,
The operation control unit learns the heat pump operation time for each hot water supply mode as the determination criterion, and determines the intermediate defrost operation as the optimum operation control in the hot water supply mode with an estimated operation time of about 60 minutes or more. Heat pump water heater.

請求項１ないし５のいずれか１つの請求項において、
前記運転制御部は、ヒートポンプ運転による加熱運転終了後に前記空気冷媒熱交換器の着霜判定を行ない、
着霜していると判定した場合は除霜運転を行なってからヒートポンプ運転を停止し、着霜していないと判定した場合は除霜運転を行なわずにヒートポンプ運転を停止する
ことを特徴とするヒートポンプ給湯機。 In any one of claims 1 to 5,
The operation control unit performs frosting determination of the air refrigerant heat exchanger after completion of the heating operation by the heat pump operation,
If it is determined that frost formation has occurred, the heat pump operation is stopped after performing the defrost operation. If it is determined that frost formation has not been performed, the heat pump operation is stopped without performing the defrost operation. Heat pump water heater.

請求項１ないし６のいずれか１つの請求項において、
前記ヒートポンプ冷媒回路は、前記圧縮機、前記水冷媒熱交換器、前記膨張弁、前記空気冷媒熱交換器、前記冷媒配管をそれぞれ２個使用する２サイクルヒートポンプ冷媒回路であることを特徴とするヒートポンプ給湯機。 In any one of claims 1 to 6,
The heat pump refrigerant circuit is a two-cycle heat pump refrigerant circuit using two each of the compressor, the water refrigerant heat exchanger, the expansion valve, the air refrigerant heat exchanger, and the refrigerant pipe. Water heater.