JP2006010137A - Heat pump system - Google Patents

Heat pump system Download PDF

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JP2006010137A
JP2006010137A JP2004185407A JP2004185407A JP2006010137A JP 2006010137 A JP2006010137 A JP 2006010137A JP 2004185407 A JP2004185407 A JP 2004185407A JP 2004185407 A JP2004185407 A JP 2004185407A JP 2006010137 A JP2006010137 A JP 2006010137A
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hot water
heat
heat exchanger
circuit
path
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JP4229881B2 (en
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Shigeaki Narita
樹昭 成田
Kohachi Maga
幸八 真賀
Kosuke Niki
康介 仁木
Atsushi Okamoto
淳 岡本
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Sunpot Co Ltd
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Sunpot Co Ltd
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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
    • F25B2339/00—Details of evaporators; Details of condensers
    • F25B2339/04—Details of condensers
    • F25B2339/047—Water-cooled condensers

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  • Heat-Pump Type And Storage Water Heaters (AREA)

Abstract

<P>PROBLEM TO BE SOLVED: To provide a heat pump system having a high coefficient of performance of mutually using respective characteristics of a refrigerant circuit becoming a supercritical cycle and an ordinary refrigerating circuit. <P>SOLUTION: This heat pump system 1 has a hot water supply heat pump 2 using a carbon dioxide refrigerant and having a first heat exchanger 7 and a second heat exchanger 9, and an air-conditioning heat pump 3 using a general refrigerant and having a third heat exchanger 25 and a fourth heat exchanger 27. In this system, when performing hot water supply and heating, a coefficient of performance of the hot water supply heat pump 2 is increased by lowering the temperature of hot water supplied to the first heat exchanger 7 by cooling lower layer side hot water of a hot water storage tank 4 by a fifth heat exchanger 41. At the same time, a coefficient of performance of the air-conditioning heat pump 3 is increased by supplying hot water heated by the fifth heat exchanger 41 to the fourth heat exchanger. <P>COPYRIGHT: (C)2006,JPO&NCIPI

Description

本発明は、給湯を行うと共に冷暖房も行うヒートポンプシステムに関する。   The present invention relates to a heat pump system that supplies hot water and also performs cooling and heating.

近年では、ヒートポンプシステムの冷媒として環境への影響が少ない自然冷媒を用いる例が増加している。その自然冷媒の中でも二酸化炭素はオゾン層に影響を与えることがなく、毒性や可燃性もないため、近年では多く用いられるようになっている。   In recent years, an example of using a natural refrigerant that has little influence on the environment as the refrigerant of the heat pump system is increasing. Among these natural refrigerants, carbon dioxide has not been affected by the ozone layer and is not toxic or flammable.

ところが、冷媒として二酸化炭素を用いたヒートポンプは、サイクルの高圧側で冷媒が超臨界状態となり、気相から液相への相変化を生じない超臨界サイクルとなる。このため、低温の水を高温に加熱するような給湯を行う際には成績係数（ＣＯＰ）が優れているが、空調として使用する場合には熱交換を行う対象の温度差が小さくなるため成績係数が低下するという特性がある（下記特許文献１参照）。   However, a heat pump using carbon dioxide as a refrigerant has a supercritical cycle in which the refrigerant is in a supercritical state on the high pressure side of the cycle and does not cause a phase change from the gas phase to the liquid phase. For this reason, the coefficient of performance (COP) is excellent when performing hot water supply that heats low-temperature water to a high temperature. There is a characteristic that the coefficient decreases (see Patent Document 1 below).

従って、従来、二酸化炭素冷媒を用いたヒートポンプシステムは、給湯に多く使われており、空調用としてはあまり用いられていない。このため、各家庭やオフィス等の設置場所においては、二酸化炭素冷媒のヒートポンプシステムを給湯用として設置し、別個に一般の冷媒を用いたヒートポンプ式の空調機を設置することが行われていた。   Therefore, conventionally, a heat pump system using a carbon dioxide refrigerant is often used for hot water supply, and is not often used for air conditioning. For this reason, in installation places such as homes and offices, a carbon dioxide refrigerant heat pump system has been installed for hot water supply, and a heat pump type air conditioner using a general refrigerant has been separately installed.

このように、従来は２つのヒートポンプシステムが並設されたものであり、ぞれぞれ放熱及び採熱を行っていたため、設備全体からみると成績係数はさほど高くはなかった。
特開２００４−１０８５９７号公報（明細書００１９、図２） As described above, conventionally, two heat pump systems are arranged side by side, and each of them performs heat dissipation and heat collection, so that the coefficient of performance is not so high when viewed from the whole equipment.
JP 2004-108597 A (Description 0019, FIG. 2)

本発明は、ヒートポンプシステムの改良を目的とし、さらに詳しくは、二酸化炭素冷媒等のサイクルの高圧側で超臨界圧状態となる冷媒を利用したヒートポンプシステムと、サイクルの高圧側で相変化を生じる一般の冷媒を用いたヒートポンプシステムとのそれぞれの特性を相互に利用し、単にこれらが並設されたものに比べて成績係数が高いヒートポンプシステムを提供することを目的とする。   The present invention aims to improve a heat pump system, and more specifically, a heat pump system using a refrigerant that is in a supercritical pressure state on the high pressure side of a cycle, such as carbon dioxide refrigerant, and a phase change that occurs on the high pressure side of the cycle in general. The object is to provide a heat pump system having a high coefficient of performance as compared with a system in which these characteristics are mutually utilized by mutually utilizing the characteristics of the heat pump system using the refrigerant.

前記目的を達成するために、本発明のヒートポンプシステムは、圧縮機と、第１熱交換器と、膨張弁と、第２熱交換器とが介設され、該圧縮機から該膨張弁に至る高圧側で超臨界状態となる冷媒を循環させる給湯用冷媒回路と、圧縮機と、第３熱交換器と、膨張弁と、第４熱交換器とが介設され、該圧縮機から該膨張弁に至る高圧側で気相から液相に相変化する冷媒を循環させる空調用冷媒回路とを備えている。また、前記第１熱交換器により加熱された温水を貯湯タンクの上層に送る第１温水往路と、前記貯湯タンクの下層から前記第１熱交換器に温水を送る第１温水復路と、前記第２熱交換器により熱交換が行われた温水を給湯用採熱手段に送る第２温水往路と、前記給湯用採熱手段から前記第２熱交換器に温水を送る第２温水復路と、前記第３熱交換器で熱交換が行われた温水を熱負荷に送る第３温水往路と、前記熱負荷から前記第３熱交換器に温水を送る第３温水復路と、前記第４熱交換器で熱交換が行われた温水を空調用採熱手段に送る第４温水往路と、前記空調用採熱手段から前記第４熱交換器に温水を送る第４温水復路とを備えている。   In order to achieve the above object, a heat pump system according to the present invention includes a compressor, a first heat exchanger, an expansion valve, and a second heat exchanger, and extends from the compressor to the expansion valve. A hot water supply refrigerant circuit for circulating a supercritical refrigerant on the high-pressure side, a compressor, a third heat exchanger, an expansion valve, and a fourth heat exchanger are interposed, and the expansion is performed from the compressor. And an air conditioning refrigerant circuit that circulates a refrigerant that changes in phase from a gas phase to a liquid phase on the high pressure side leading to the valve. A first warm water forward path for sending warm water heated by the first heat exchanger to an upper layer of the hot water storage tank; a first hot water return path for sending warm water from the lower layer of the hot water storage tank to the first heat exchanger; A second hot water outgoing path for sending hot water having been subjected to heat exchange by the two heat exchangers to the hot water collecting means, a second hot water return path for sending hot water from the hot water collecting means to the second heat exchanger, A third warm water forward path for sending the hot water heat-exchanged by the third heat exchanger to the heat load, a third hot water return path for sending the warm water from the heat load to the third heat exchanger, and the fourth heat exchanger. And a fourth hot water return path for sending warm water from the air conditioning heat collecting means to the fourth heat exchanger.

また、前記第１温水復路と並列に設けられ前記貯湯タンクの下層からの温水を前記第４温水復路と熱交換を行う第５熱交換器を介して前記第１熱交換器に送る第５温水回路と、前記第１温水往路と前記第１温水復路との間で温水を循環させるか、又は前記第１温水往路と前記第５温水回路との間で温水を循環させるかを切り替える切替手段と、前記貯湯タンクの下層の温度が所定の閾値以下のときは前記第１温水往路と前記第１温水復路との間で温水を循環させ、前記貯湯タンクの下層の温度が前記閾値を越えたときは前記第１温水往路と前記第５温水回路との間で温水を循環させるように前記切替手段を切り替える制御手段とを備えていることを特徴とする。   Moreover, the 5th hot water which is provided in parallel with the said 1st hot water return path and sends the warm water from the lower layer of the said hot water storage tank to the said 1st heat exchanger via the 5th heat exchanger which heat-exchanges with the said 4th hot water return path. Switching means for switching between circulating a hot water between the circuit and the first warm water outbound path and the first warm water returning path, or circulating the warm water between the first warm water outbound path and the fifth warm water circuit; When the temperature of the lower layer of the hot water storage tank is below a predetermined threshold, hot water is circulated between the first hot water forward path and the first hot water return path, and the temperature of the lower layer of the hot water storage tank exceeds the threshold value. Comprises control means for switching the switching means so as to circulate hot water between the first warm water forward path and the fifth warm water circuit.

本発明のヒートポンプシステムにおいては、前記貯湯タンクの下層の温度が所定の閾値を越えたときは、前記切替手段を切り替えて前記第１温水往路と前記第５温水回路との間で温水を循環させる。これにより、前記第１熱交換器に送られる温水が前記第５温水回路の第５熱交換器で冷却される。このため、単に前記第１温水復路から温水が供給される場合に比べて給湯用冷媒回路の成績係数を上昇させることができる。また、前記空調用冷媒回路において暖房運転が行われているときは、前記第４温水復路の温水の温度は高いほど成績係数がよい。本発明では、前記第５熱交換器によって前記第４温水復路の温水の温度が上昇されるので、前記空調用冷媒回路における成績係数も上昇させることができる。このように、本発明では、前記給湯用冷媒回路と前記空調用冷媒回路の夫々の特性を生かしてシステム全体として成績係数を上昇させることができる。   In the heat pump system of the present invention, when the temperature of the lower layer of the hot water storage tank exceeds a predetermined threshold value, the switching means is switched to circulate hot water between the first hot water forward path and the fifth hot water circuit. . Thereby, the warm water sent to the first heat exchanger is cooled by the fifth heat exchanger of the fifth warm water circuit. For this reason, the coefficient of performance of the hot water supply refrigerant circuit can be increased as compared with the case where hot water is simply supplied from the first hot water return path. When the heating operation is performed in the air conditioning refrigerant circuit, the higher the temperature of the hot water in the fourth hot water return path, the better the coefficient of performance. In the present invention, since the temperature of the hot water in the fourth hot water return path is increased by the fifth heat exchanger, the coefficient of performance in the air conditioning refrigerant circuit can also be increased. Thus, in the present invention, the coefficient of performance of the entire system can be increased by taking advantage of the characteristics of the hot water supply refrigerant circuit and the air conditioning refrigerant circuit.

また、本発明のヒートポンプシステムにおいては、前記貯湯タンクの上層からの温水を前記第３温水往路と熱交換を行う第６熱交換器を介して前記貯湯タンクの下層に送る第６温水回路をさらに備え、前記制御手段は、前記熱負荷で要求される温水の温度が所定の第２閾値を越えているときは前記第６温水回路に温水を循環させ、前記熱負荷で要求される温水の温度が前記第２閾値以下の時は前記第６温水回路の温水の循環を停止させるものであることが好ましい。   The heat pump system of the present invention further includes a sixth hot water circuit for sending hot water from an upper layer of the hot water storage tank to a lower layer of the hot water storage tank via a sixth heat exchanger for exchanging heat with the third hot water outgoing path. And when the temperature of the hot water required by the thermal load exceeds a predetermined second threshold, the control means circulates the hot water in the sixth hot water circuit, and the temperature of the hot water required by the thermal load. When the value is less than or equal to the second threshold value, it is preferable that the circulation of the hot water in the sixth hot water circuit is stopped.

これによれば、前記熱負荷で要求される温水の温度が前記第２閾値を越えているとき、即ち前記熱負荷で高い温度の温水が要求されているときは、前記制御手段は前記貯湯タンクの上層から前記第６温水回路に高温の温水を供給する。これにより、前記第６熱交換器及び前記第３温水往路を介して前記熱負荷に高温の温水を供給できるため、前記空調用冷媒回路単体の能力以上の暖房を行うことができる。   According to this, when the temperature of the hot water required by the thermal load exceeds the second threshold value, that is, when the hot water at the high temperature is required by the thermal load, the control means is the hot water storage tank. Hot hot water is supplied from the upper layer to the sixth hot water circuit. Thereby, since hot water of high temperature can be supplied to the heat load via the sixth heat exchanger and the third hot water outbound route, heating exceeding the capacity of the air conditioning refrigerant circuit alone can be performed.

また、本発明のヒートポンプシステムにおいては、前記給湯用採熱手段は地熱を採熱する第１地中熱採熱管を有し、前記空調用採熱手段は地熱を採熱する第２地中熱採熱管を有し、前記第１地中熱採熱管と前記第２地中熱採熱管とは地中において近接して配設されていることが好ましい。   In the heat pump system of the present invention, the hot water collecting means has a first ground heat collecting pipe for collecting geothermal heat, and the air conditioning heat collecting means has a second ground heat for collecting geothermal heat. It is preferable to have a heat collection pipe, and the first underground heat collection pipe and the second underground heat collection pipe are arranged close to each other in the ground.

前記給湯用冷媒回路において給湯運転を行っているときは、前記第１地中熱採熱管には低温の温水が供給され、地中から地熱を採熱して昇温させている。一方、前記空調用冷媒回路において冷房運転を行っているときは、前記第２地中熱採熱管には高温の温水が供給され、地中から低温の地熱を採熱して温度を低下させている。即ち、前記第２地中熱採熱管では冷房の際に発生する排熱が地中内に排出される。本発明では、前記第１地中熱採熱管と前記第２地中熱採熱管とは地中において近接して配設されているため、前記給湯用冷媒回路で給湯を行う際に前記空調用冷媒回路の冷房排熱を採熱して利用することができるので、給湯用冷媒回路の成績係数を高めることができる。また、空調用冷媒回路においては、冷房の排熱を地中内に排出しても前記第１地中熱採熱管で採熱が行われるため、地中内が過熱状態となることがないので安定した冷房能力を保つことができる。   When the hot water supply operation is performed in the hot water supply refrigerant circuit, low-temperature hot water is supplied to the first geothermal heat collection pipe, and the temperature is raised by collecting geothermal heat from the ground. On the other hand, when the air-conditioning refrigerant circuit is performing a cooling operation, high-temperature hot water is supplied to the second geothermal heat collection pipe, and low-temperature geothermal heat is collected from the ground to lower the temperature. . That is, in the second underground heat collection pipe, exhaust heat generated during cooling is discharged into the ground. In the present invention, since the first geothermal heat collecting pipe and the second geothermal heat collecting pipe are disposed close to each other in the ground, the hot water supply refrigerant circuit is used for the air conditioning. Since the cooling exhaust heat of the refrigerant circuit can be collected and used, the coefficient of performance of the hot water supply refrigerant circuit can be increased. Further, in the air conditioning refrigerant circuit, even if the exhaust heat of the cooling is discharged into the ground, the ground is not overheated because the heat is collected by the first ground heat collecting pipe. Stable cooling capacity can be maintained.

次に、本発明のヒートポンプシステムの実施形態の一例について、図１乃至図６を参照して説明する。本実施形態のヒートポンプシステム１は、図１に示すように、給湯用ヒートポンプ２と空調用ヒートポンプ３とが１個の筐体Ｃに内蔵されているデュアルヒートポンプシステムとなっている。   Next, an example of an embodiment of the heat pump system of the present invention will be described with reference to FIGS. As shown in FIG. 1, the heat pump system 1 of the present embodiment is a dual heat pump system in which a hot water supply heat pump 2 and an air conditioning heat pump 3 are built in one housing C.

給湯用ヒートポンプ２は、貯湯タンク４内の温水を加熱するものであり、給湯用冷媒回路５を備えている。給湯用冷媒回路５は、圧縮機６と、凝縮器である第１熱交換器７と、膨張弁８と、蒸発器である第２熱交換器９とが順に接続されており、冷媒には二酸化炭素が用いられている。この二酸化炭素冷媒は、給湯用冷媒回路５の圧縮機６、第１熱交換器７及び膨張弁８に亘って超臨界状態となる。   The hot water supply heat pump 2 heats the hot water in the hot water storage tank 4 and includes a hot water supply refrigerant circuit 5. The hot water supply refrigerant circuit 5 includes a compressor 6, a first heat exchanger 7 that is a condenser, an expansion valve 8, and a second heat exchanger 9 that is an evaporator, which are connected in order. Carbon dioxide is used. This carbon dioxide refrigerant is in a supercritical state across the compressor 6, the first heat exchanger 7, and the expansion valve 8 of the hot water supply refrigerant circuit 5.

また、第１熱交換器７と貯湯タンク４の上層４ａとは第１温水往路１０によって接続されており、貯湯タンク４の下層４ｂと第１熱交換器７とは第１三方弁１１及び第１循環ポンプ１２を介設した第１温水復路１３によって接続されている。また、貯湯タンク４の上層４ａには内部の温水の温度を検出する第１温度センサＴ１が設けられ、貯湯タンク４の下層４ｂには内部の温水の温度を検出する第２温度センサＴ２が設けられている。また、貯湯タンク４の下層４ｂからは給水が行われ、上層４ａから給湯が行われる。   The first heat exchanger 7 and the upper layer 4a of the hot water storage tank 4 are connected by the first hot water outgoing path 10, and the lower layer 4b of the hot water storage tank 4 and the first heat exchanger 7 are connected to the first three-way valve 11 and the first heat exchanger 7. It is connected by a first hot water return path 13 provided with one circulation pump 12. The upper layer 4a of the hot water storage tank 4 is provided with a first temperature sensor T1 for detecting the temperature of the internal hot water, and the lower layer 4b of the hot water storage tank 4 is provided with a second temperature sensor T2 for detecting the temperature of the internal hot water. It has been. Further, water is supplied from the lower layer 4b of the hot water storage tank 4, and hot water is supplied from the upper layer 4a.

第２熱交換器９は、第２温水往路１４及び第２温水復路１５によって採熱手段に接続されている。本実施形態においては、採熱手段として、第１地中熱採熱管１６と、熱交換器とファンとを有する室外ファンユニット１７と、太陽熱集熱器１８とを備えている。また、これらは第２三方弁１９及び第３三方弁２０によって接続されている。この第３三方弁２０と第２熱交換器９との間の第２温水復路１５には、温水を循環させる第２循環ポンプ２１が設けられている。また、室外ファンユニット１７には外気温を検出する外気温センサＴｏが設けられている。   The second heat exchanger 9 is connected to the heat collecting means by a second warm water forward path 14 and a second warm water return path 15. In this embodiment, the heat collecting means includes a first underground heat collecting pipe 16, an outdoor fan unit 17 having a heat exchanger and a fan, and a solar heat collector 18. These are connected by a second three-way valve 19 and a third three-way valve 20. A second circulation pump 21 that circulates the warm water is provided in the second warm water return path 15 between the third three-way valve 20 and the second heat exchanger 9. The outdoor fan unit 17 is provided with an outside air temperature sensor To that detects the outside air temperature.

空調用ヒートポンプ３は、各熱負荷に熱（温熱又は冷熱）を供給するものであり、空調用冷媒回路２２を備えている。空調用冷媒回路２２は、圧縮機２３と、暖房時と冷房時で冷媒の流れを切り替える四方弁２４と、暖房の際には蒸発器になり冷房の際には凝縮器となる第３熱交換器２５と、膨張弁２６と、暖房の際には凝縮器となり冷房の際には蒸発器となる第４熱交換器２７とが順に接続されている。この空調用冷媒回路２２に用いられている冷媒は、一般に用いられているＲ４１０Ａとなっている。   The air conditioning heat pump 3 supplies heat (hot or cold) to each heat load, and includes an air conditioning refrigerant circuit 22. The air conditioning refrigerant circuit 22 includes a compressor 23, a four-way valve 24 for switching the refrigerant flow during heating and cooling, and a third heat exchange functioning as an evaporator during heating and as a condenser during cooling. The heater 25, the expansion valve 26, and a fourth heat exchanger 27 that is a condenser during heating and an evaporator during cooling are sequentially connected. The refrigerant used in the air conditioning refrigerant circuit 22 is generally used R410A.

また、第３熱交換器２５と各熱負荷とは第３温水往路２８によって接続されており、各熱負荷と第３熱交換器２５とは第３循環ポンプ２９を介設した第３温水復路３０によって接続されている。本実施形態における熱負荷は、室内用放熱器３１と、屋根裏スペースに設置された換気用空調ユニット３２と、第５循環ポンプ３３によって融雪路盤３４に送られる温水を加熱する融雪用熱交換器３５である。この室内用放熱器３１の入口には、室内用放熱器３１に供給される温水の温度を検出する第３温度センサＴ３が設けられている。また、融雪用熱交換器３５と融雪路盤３４とは融雪回路３６によって接続されている。また、第４熱交換器２７は第４温水往路３７及び第４温水復路３８によって採熱手段である第２地中熱採熱管３９に接続されている。また、第４温水復路３８には第４循環ポンプ４０が設けられている。   In addition, the third heat exchanger 25 and each heat load are connected by a third hot water forward path 28, and each heat load and the third heat exchanger 25 are connected by a third hot water return path via a third circulation pump 29. 30 is connected. The heat load in the present embodiment includes the indoor radiator 31, the ventilation air conditioning unit 32 installed in the attic space, and the snow-melting heat exchanger 35 that heats the hot water sent to the snow-melting roadbed 34 by the fifth circulation pump 33. It is. A third temperature sensor T <b> 3 that detects the temperature of the hot water supplied to the indoor radiator 31 is provided at the entrance of the indoor radiator 31. The snow melting heat exchanger 35 and the snow melting roadbed 34 are connected by a snow melting circuit 36. The fourth heat exchanger 27 is connected to a second underground heat collecting pipe 39 as a heat collecting means by a fourth warm water forward path 37 and a fourth warm water return path 38. A fourth circulation pump 40 is provided in the fourth hot water return path 38.

本実施形態においては、空調用冷媒回路２２の第４温水復路３８に第５熱交換器４１が設けられている。この第５熱交換器４１は、第４温水復路３８内の温水と、貯湯タンク４の下層４ｂから第１熱交換器７まで温水を循環させる第５温水回路４２内の温水との間で熱交換を行う。また、第３温水往路２８には第６熱交換器４３が設けられている。この第６熱交換器４３は、第３温水往路２８内の温水と、貯湯タンク４の上層４ａから下層４ｂまで第６循環ポンプ４４によって温水を循環させる第６温水回路４５内の温水との間で熱交換を行う。さらに、第１地中熱採熱管１６と第２地中熱採熱管３９は、内部に砂又は水等が収納された地中管４６内に近接して設けられている。   In the present embodiment, a fifth heat exchanger 41 is provided in the fourth hot water return path 38 of the air conditioning refrigerant circuit 22. The fifth heat exchanger 41 heats between the hot water in the fourth hot water return path 38 and the hot water in the fifth hot water circuit 42 that circulates the hot water from the lower layer 4b of the hot water storage tank 4 to the first heat exchanger 7. Exchange. Further, a sixth heat exchanger 43 is provided in the third warm water forward path 28. This sixth heat exchanger 43 is between the hot water in the third hot water outbound path 28 and the hot water in the sixth hot water circuit 45 that circulates the hot water from the upper layer 4a to the lower layer 4b of the hot water storage tank 4 by the sixth circulation pump 44. Perform heat exchange at. Further, the first underground heat collecting pipe 16 and the second underground heat collecting pipe 39 are provided close to the inside of the underground pipe 46 in which sand or water is stored.

次に、本実施形態のヒートポンプシステム１の機能的構成について図２を参照して説明する。ヒートポンプシステム１は、図２に示すように、給湯用ヒートポンプ２と空調用ヒートポンプ３とを１台のコントローラ４７によって制御している。給湯用ヒートポンプ２において制御がなされるのは、圧縮機６、膨張弁８、第１循環ポンプ１２、第２循環ポンプ２１、第６循環ポンプ４４、第１三方弁１１、第２三方弁１９、及び第３三方弁２０である。また、コントローラ４７は、給湯用ヒートポンプ２に関連する機器として、第１温度センサＴ１、第２温度センサＴ２及び外気温センサＴｏから検出値を受信し、室外ファンユニット１７の制御を行う。   Next, a functional configuration of the heat pump system 1 of the present embodiment will be described with reference to FIG. In the heat pump system 1, as shown in FIG. 2, the hot water supply heat pump 2 and the air conditioning heat pump 3 are controlled by a single controller 47. The hot water supply heat pump 2 is controlled by the compressor 6, the expansion valve 8, the first circulation pump 12, the second circulation pump 21, the sixth circulation pump 44, the first three-way valve 11, the second three-way valve 19, And the third three-way valve 20. The controller 47 receives detection values from the first temperature sensor T1, the second temperature sensor T2, and the outside air temperature sensor To as devices related to the hot water supply heat pump 2, and controls the outdoor fan unit 17.

空調用ヒートポンプ３においてコントローラ４７により制御がなされるのは、圧縮機２３、膨張弁２６、四方弁２４、第３循環ポンプ２９、及び第４循環ポンプ４０である。また、コントローラ４７は、空調用ヒートポンプ３に関連する機器として、第３温度センサＴ３から検出値を受信し、室内用放熱器３１、換気用空調ユニット３２及び第５循環ポンプ３３の制御を行う。   In the air conditioning heat pump 3, the controller 47 controls the compressor 23, the expansion valve 26, the four-way valve 24, the third circulation pump 29, and the fourth circulation pump 40. The controller 47 receives a detection value from the third temperature sensor T3 as a device related to the air conditioning heat pump 3, and controls the indoor radiator 31, the ventilation air conditioning unit 32, and the fifth circulation pump 33.

また、コントローラ４７は、第２温度センサＴ２の検出値の閾値として４０℃という値を記憶している。そして、給湯用ヒートポンプ２によって給湯運転を行うと共に空調用ヒートポンプ３によって暖房運転を行っている際に、貯湯タンク４の下層４ｂの温度が閾値である４０℃以下であるときは第１三方弁１１によって第１温水往路１０と第１温水復路１３とを接続し、第５温水回路４２は閉じた状態とする（図３参照）。一方、貯湯タンク４の下層４ｂの温度が閾値である４０℃を越えているときは、第１三方弁１１によって第１温水往路１０と第５温水回路４２とを接続し、第１温水復路１３は閉じた状態とするように制御する（図４参照）。   In addition, the controller 47 stores a value of 40 ° C. as a threshold value of the detection value of the second temperature sensor T2. When the hot water supply operation is performed by the hot water supply heat pump 2 and the heating operation is performed by the air conditioning heat pump 3, the first three-way valve 11 is used when the temperature of the lower layer 4b of the hot water storage tank 4 is 40 ° C. or less which is a threshold value. Thus, the first warm water forward path 10 and the first warm water return path 13 are connected, and the fifth warm water circuit 42 is closed (see FIG. 3). On the other hand, when the temperature of the lower layer 4b of the hot water storage tank 4 exceeds the threshold value of 40 ° C., the first three-way valve 11 connects the first warm water forward path 10 and the fifth warm water circuit 42 to the first warm water return path 13. Is controlled to be in a closed state (see FIG. 4).

また、コントローラ４７は、第３温度センサＴ３の検出値の閾値として７５℃という値を記憶している。そして、空調用ヒートポンプ３によって暖房運転を行っている際に、貯湯タンク４の上層４ａの温度がこの７５℃を越えており、且つ、室内用放熱器３１によって要求されている温水の温度が閾値である７５℃を越えているときは、第６循環ポンプ４４を作動させて貯湯タンク４の上層４ａから第６温水回路４５を介して第６熱交換器４３に温水を送り、この第６熱交換器４３で室内用放熱器３１に送られる温水を加熱するように制御する（図５参照）。一方、貯湯タンク４の上層４ａの温度が７５℃以下のとき、又は室内用放熱器３１によって要求されている温水の温度が閾値である７５℃以下のときは、コントローラ４７は第６循環ポンプ４４の作動を停止させ、第６温水回路４５内の温水の循環を停止させるように制御する。   The controller 47 stores a value of 75 ° C. as a threshold value of the detection value of the third temperature sensor T3. When the heating operation is performed by the air conditioning heat pump 3, the temperature of the upper layer 4a of the hot water storage tank 4 exceeds 75 ° C., and the temperature of the hot water required by the indoor radiator 31 is the threshold value. When the temperature exceeds 75 ° C., the sixth circulation pump 44 is operated to send hot water from the upper layer 4a of the hot water storage tank 4 to the sixth heat exchanger 43 via the sixth hot water circuit 45. The exchanger 43 is controlled to heat the hot water sent to the indoor radiator 31 (see FIG. 5). On the other hand, when the temperature of the upper layer 4a of the hot water storage tank 4 is 75 ° C. or lower, or when the temperature of the hot water requested by the indoor radiator 31 is 75 ° C. or lower, which is the threshold value, the controller 47 controls the sixth circulation pump 44. Is controlled to stop the circulation of the hot water in the sixth hot water circuit 45.

次に、本実施形態のヒートポンプシステム１の作動について、図３乃至図６を参照して説明する。尚、図３乃至図６において、実線で表している回路は作動中のものを示し、点線で表している回路は閉じられている回路を示す。   Next, the operation of the heat pump system 1 of the present embodiment will be described with reference to FIGS. 3 to 6. 3 to 6, a circuit indicated by a solid line indicates an active circuit, and a circuit indicated by a dotted line indicates a closed circuit.

まず、図３及び図４を参照して、冬季において、給湯用ヒートポンプ２で給湯運転を行い、空調用ヒートポンプ３で暖房運転を行う場合について説明する。給湯用ヒートポンプ２で給湯運転うときは、コントローラ４７は圧縮機６を作動させて冷媒である二酸化炭素を圧縮し給湯用冷媒回路５内を循環させる。また、第１循環ポンプ１２及び第２循環ポンプ２１を作動させる。ここで、第２温度センサＴ２により検出される貯湯タンク４の下層４ｂの温度が閾値である４０℃以下であるときは、第１三方弁１１によって第１温水往路１０と第１温水復路１３とを接続する。また、室内用放熱器３１に設けられた第３温度センサＴ３で要求される温水の温度が７５℃以下であるときは、第６循環ポンプ４４は作動させないため、第６温水回路４５内には温水は流れない。また、外気温センサＴｏの検出値が５℃を越えているときは、第２三方弁１９及び第３三方弁２０によって第１地中熱採熱管１６を介さずに室外ファンユニット１７及び太陽熱集熱器１８によって採熱を行う。さらに、外気温センサＴｏの検出値が５℃を越えている状態では、第５循環ポンプ３３は作動させないようにしており、融雪回路３６には温水は循環していない。   First, with reference to FIG. 3 and FIG. 4, the case where the hot water supply operation is performed by the hot water supply heat pump 2 and the heating operation is performed by the air conditioning heat pump 3 in winter will be described. When a hot water supply operation is performed by the hot water supply heat pump 2, the controller 47 operates the compressor 6 to compress carbon dioxide as a refrigerant and circulate the refrigerant in the hot water supply refrigerant circuit 5. Further, the first circulation pump 12 and the second circulation pump 21 are operated. Here, when the temperature of the lower layer 4b of the hot water storage tank 4 detected by the second temperature sensor T2 is equal to or lower than 40 ° C. which is a threshold value, the first three-way valve 11 causes the first warm water forward path 10 and the first warm water return path 13 to Connect. Further, when the temperature of the hot water required by the third temperature sensor T3 provided in the indoor radiator 31 is 75 ° C. or less, the sixth circulation pump 44 is not operated, Hot water does not flow. Further, when the detected value of the outside air temperature sensor To exceeds 5 ° C., the outdoor fan unit 17 and the solar heat collection are not caused by the second three-way valve 19 and the third three-way valve 20 without passing through the first underground heat collection pipe 16. Heat is collected by the heater 18. Further, in a state where the detected value of the outside air temperature sensor To exceeds 5 ° C., the fifth circulation pump 33 is not operated, and hot water is not circulated in the snow melting circuit 36.

給湯用冷媒回路５において、圧縮機６によって圧縮された冷媒は、凝縮器である第１熱交換器７で放熱がおこなわれ、膨張弁８で減圧された後、蒸発器である第２熱交換器９で採熱が行われ、圧縮機６の入口まで戻される。また、第１循環ポンプ１２により送られる温水は、第１熱交換器７で熱交換を行って加熱され、第１温水往路１０を介して貯湯タンク４の上層４ａに送られる。本実施形態では、この第１熱交換器７によって温水が９０℃まで加熱されるようになっている。また、貯湯タンク４の下層４ｂからの温水は第１温水復路１３を介して第１熱交換器７に戻される。また、第２循環ポンプ２１により送られる温水は、第２熱交換器９で熱交換を行って冷却され、第２三方弁１９を介して室外ファンユニット１７及び太陽熱集熱器１８に送られて採熱が行われ、第３三方弁２０を介して第２循環ポンプ２１に戻される。   In the hot water supply refrigerant circuit 5, the refrigerant compressed by the compressor 6 is radiated by the first heat exchanger 7 that is a condenser, depressurized by the expansion valve 8, and then the second heat exchange that is an evaporator. Heat is collected in the vessel 9 and returned to the inlet of the compressor 6. The hot water sent by the first circulation pump 12 is heated by exchanging heat in the first heat exchanger 7 and sent to the upper layer 4 a of the hot water storage tank 4 through the first hot water outgoing path 10. In the present embodiment, the hot water is heated to 90 ° C. by the first heat exchanger 7. Further, the hot water from the lower layer 4 b of the hot water storage tank 4 is returned to the first heat exchanger 7 through the first hot water return path 13. The hot water sent by the second circulation pump 21 is cooled by exchanging heat in the second heat exchanger 9 and sent to the outdoor fan unit 17 and the solar heat collector 18 via the second three-way valve 19. Heat is collected and returned to the second circulation pump 21 via the third three-way valve 20.

一方、空調用冷媒回路２２においては、圧縮機２３によって圧縮された冷媒は、四方弁２４を通過して凝縮器である第３熱交換器２５で放熱が行われ、膨張弁２６で減圧された後、蒸発器である第４熱交換器２７で採熱が行われ、四方弁２４を介して圧縮機２３の入口まで戻される。また、第３循環ポンプ２９により送られる温水は、第３熱交換器２５、第６熱交換器４３、室内用放熱器３１、換気用空調ユニット３２、及び融雪用熱交換器３５を通過して第３循環ポンプ２９に戻される。このとき、第６温水回路４５内の温水は循環されていないため、第６熱交換器４３では熱交換は行われない。また、第５循環ポンプ３３も作動していないため、融雪用熱交換器３５においても熱交換は行われない。また、第４循環ポンプ４０により送られる温水は、第４熱交換器２７、第２地中熱採熱管３９及び第５熱交換器４１を通過して第４循環ポンプ４０に戻される。このとき、第５温水回路４２内の温水は循環されていないため、第５熱交換器４１においては熱交換は行われない。   On the other hand, in the air conditioning refrigerant circuit 22, the refrigerant compressed by the compressor 23 passes through the four-way valve 24, dissipates heat in the third heat exchanger 25 that is a condenser, and is decompressed by the expansion valve 26. Thereafter, heat is collected by the fourth heat exchanger 27 that is an evaporator, and returned to the inlet of the compressor 23 through the four-way valve 24. The warm water sent by the third circulation pump 29 passes through the third heat exchanger 25, the sixth heat exchanger 43, the indoor radiator 31, the ventilation air conditioning unit 32, and the snow melting heat exchanger 35. Returned to the third circulation pump 29. At this time, since the hot water in the sixth hot water circuit 45 is not circulated, the sixth heat exchanger 43 does not perform heat exchange. In addition, since the fifth circulation pump 33 is not operated, heat exchange is not performed in the snow melting heat exchanger 35. Further, the hot water sent by the fourth circulation pump 40 passes through the fourth heat exchanger 27, the second underground heat collection pipe 39 and the fifth heat exchanger 41 and is returned to the fourth circulation pump 40. At this time, since the hot water in the fifth hot water circuit 42 is not circulated, heat exchange is not performed in the fifth heat exchanger 41.

以上の状態で、ヒートポンプシステム１の運転が行われると、貯湯タンク４内の温水の温度が上昇し、各熱負荷において暖房が行われる。そして、第２温度センサＴ２によって検知される温水の温度、即ち貯湯タンク４の下層４ｂにおける温水の温度が上昇して閾値である４０℃を越えたときは、コントローラ４７は、第１三方弁１１の切替を行う。具体的には、図４に示すように、第１循環ポンプ１２に戻される温水の経路を、第１温水復路１３から第５温水回路４２に切り替える。すると、第１循環ポンプ１２により送られる温水は、第１熱交換器７、貯湯タンク４の上層４ａから下層４ｂを経て、第５温水回路４２内を通って第５熱交換器４１により熱交換を行った後、第１三方弁１１を介して第１循環ポンプ１２に戻されることになる。   When the operation of the heat pump system 1 is performed in the above state, the temperature of the hot water in the hot water storage tank 4 rises and heating is performed at each heat load. When the temperature of the hot water detected by the second temperature sensor T2, that is, the temperature of the hot water in the lower layer 4b of the hot water storage tank 4 rises and exceeds the threshold value of 40 ° C., the controller 47 sets the first three-way valve 11 Is switched. Specifically, as shown in FIG. 4, the path of the hot water returned to the first circulation pump 12 is switched from the first hot water return path 13 to the fifth hot water circuit 42. Then, the hot water sent by the first circulation pump 12 passes through the fifth hot water circuit 42 through the first heat exchanger 7 and the upper layer 4a to the lower layer 4b of the hot water storage tank 4, and is exchanged by the fifth heat exchanger 41. Is performed, the first three-way valve 11 is returned to the first circulation pump 12.

第５熱交換器４１においては、第５温水回路４２内の温水の温度（４０℃を越える温度）が第４温水復路３８内の温水温度（約３０℃）よりも高いため、第５温水回路４２内の温水は冷却され、第４温水復路３８内の温水は加熱される。二酸化炭素冷媒を用いた給湯用冷媒回路５では、第１熱交換器７の入口温度と出口温度との差が大きい方が給湯用冷媒回路５の成績係数がよい。従って、本実施形態のように第１熱交換器７に供給される温水が冷却されたときは、貯湯タンク４の下層４ｂの温水をそのまま第１熱交換器７に送る場合に比べて給湯用冷媒回路５の成績係数がよくなる。一方、空調用冷媒回路２２においては、暖房時に第４熱交換器２７に供給される温水の温度が高い方が成績係数が向上する。従って、本実施形態のように第４熱交換器２７に送られる温水が第５熱交換器４１によって加熱されたときは、第２地中熱採熱管３９からの温水をそのまま送る場合に比べて空調用冷媒回路２２の成績係数が向上する。   In the fifth heat exchanger 41, the temperature of the hot water in the fifth hot water circuit 42 (temperature exceeding 40 ° C.) is higher than the temperature of the hot water in the fourth hot water return path 38 (about 30 ° C.). The warm water in 42 is cooled, and the warm water in the fourth warm water return path 38 is heated. In the hot water supply refrigerant circuit 5 using carbon dioxide refrigerant, the coefficient of performance of the hot water supply refrigerant circuit 5 is better when the difference between the inlet temperature and the outlet temperature of the first heat exchanger 7 is larger. Accordingly, when the hot water supplied to the first heat exchanger 7 is cooled as in the present embodiment, the hot water in the lower layer 4b of the hot water storage tank 4 is used for hot water supply compared to the case where the hot water is sent to the first heat exchanger 7 as it is. The coefficient of performance of the refrigerant circuit 5 is improved. On the other hand, in the refrigerant circuit 22 for air conditioning, the coefficient of performance improves when the temperature of the hot water supplied to the fourth heat exchanger 27 during heating is higher. Therefore, when the hot water sent to the 4th heat exchanger 27 is heated by the 5th heat exchanger 41 like this embodiment, compared with the case where the warm water from the 2nd underground heat collection pipe 39 is sent as it is. The coefficient of performance of the air conditioning refrigerant circuit 22 is improved.

次に、図５を参照して、暖房用の熱負荷において高い能力が求められている場合のヒートポンプシステム１の作動について説明する。室内用放熱器３１において急速暖房運転や高負荷運転を必要とする場合、第３温水往路２８に供給される温水の温度を高くする必要がある。本実施形態では、第３温度センサＴ３の検出値の閾値である７５℃を越える場合が当該高負荷運転に相当する。このように、室内用放熱器３１の操作パネル（図示せず）等によって高負荷運転の指示がなされ、室内用放熱器３１によって要求される温水の温度が閾値である７５℃を越えたときは、コントローラ４７は以下のようにヒートポンプシステム１の制御を行う。尚、以下の例では融雪回路３６の作動も同時に行う場合について説明する。   Next, with reference to FIG. 5, the operation of the heat pump system 1 when a high capacity is required in the heat load for heating will be described. When the indoor radiator 31 requires rapid heating operation or high load operation, the temperature of the hot water supplied to the third hot water outgoing path 28 needs to be increased. In the present embodiment, the case where the temperature exceeds 75 ° C. which is the threshold value of the detection value of the third temperature sensor T3 corresponds to the high load operation. As described above, when an instruction for high load operation is given by an operation panel (not shown) or the like of the indoor radiator 31 and the temperature of the hot water required by the indoor radiator 31 exceeds the threshold of 75 ° C. The controller 47 controls the heat pump system 1 as follows. In the following example, the case where the operation of the snow melting circuit 36 is also performed will be described.

室内用放熱器３１によって要求される温水の温度が閾値である７５℃を越えたときは、コントローラ４７は、第６循環ポンプ４４を作動させて第６温水回路４５内に温水を循環させる。この第６温水回路４５には貯湯タンク４の上層４ａから温水が供給されるため、第６温水回路４５内を循環する温水は高温となっている。このように、第６温水回路４５内を高温の温水が循環すると、第６熱交換器４３において第３温水往路２８内を流れる温水が加熱される。本実施形態においては、室内用放熱器３１に供給される温水の温度が７５℃以上になるように設定されている。   When the temperature of the hot water required by the indoor radiator 31 exceeds the threshold value of 75 ° C., the controller 47 operates the sixth circulation pump 44 to circulate the hot water in the sixth hot water circuit 45. Since the hot water is supplied to the sixth hot water circuit 45 from the upper layer 4a of the hot water storage tank 4, the hot water circulating in the sixth hot water circuit 45 is at a high temperature. As described above, when high-temperature hot water circulates in the sixth hot water circuit 45, the hot water flowing in the third hot water outgoing path 28 is heated in the sixth heat exchanger 43. In the present embodiment, the temperature of the hot water supplied to the indoor radiator 31 is set to 75 ° C. or higher.

このとき、室内用放熱器３１に供給される高温の温水は、換気用空調ユニット３２及び融雪用熱交換器３５を介して第３循環ポンプ２９に戻される。このとき、第５循環ポンプ３３が作動され、融雪回路３６内に温水が循環しているため、融雪回路３６内の温水は融雪用熱交換器３５によって加熱され、この加熱された温水が融雪路盤３４に送られて融雪が行われる。   At this time, the hot water supplied to the indoor radiator 31 is returned to the third circulation pump 29 via the ventilation air conditioning unit 32 and the snow melting heat exchanger 35. At this time, since the fifth circulation pump 33 is operated and the hot water is circulating in the snow melting circuit 36, the hot water in the snow melting circuit 36 is heated by the snow melting heat exchanger 35, and the heated hot water is heated to the snow melting roadbed. 34 is sent to snowmelt.

このように、本実施形態においては、熱負荷において高い能力が求められている場合であっても、求められた高い能力に対応することができる。具体的には、通常のＲ４１０Ａ冷媒を用いたヒートポンプでは得ることができない高い温度の温水を各熱負荷に供給することができる。   As described above, in the present embodiment, even when a high capability is required in the heat load, the required high capability can be handled. Specifically, high-temperature hot water that cannot be obtained by a heat pump using a normal R410A refrigerant can be supplied to each heat load.

次に、図６を参照して、夏季において空調用ヒートポンプ３で冷房運転が行われ、同時に給湯用ヒートポンプ２で給湯運転が行われている際の作動について説明する。空調用ヒートポンプ３で冷房運転が行われているときは、空調用冷媒回路２２において、圧縮機２３により圧縮された冷媒が四方弁２４を介して第４熱交換器２７に送られ、膨張弁２６を介して第３熱交換器２５に送られ、さらに四方弁２４を介して圧縮機２３に戻される。このとき、第４熱交換器２７が凝縮器となり、第３熱交換器２５が蒸発器となっている。   Next, with reference to FIG. 6, the operation when the cooling operation is performed by the air conditioning heat pump 3 and the hot water supply operation is performed by the hot water supply heat pump 2 in the summer will be described. When the air conditioning heat pump 3 is performing a cooling operation, the refrigerant compressed by the compressor 23 in the air conditioning refrigerant circuit 22 is sent to the fourth heat exchanger 27 via the four-way valve 24, and the expansion valve 26. To the third heat exchanger 25, and then returned to the compressor 23 via the four-way valve 24. At this time, the fourth heat exchanger 27 is a condenser, and the third heat exchanger 25 is an evaporator.

また、冷房運転が行われているときは、熱負荷に供給される温水が第３熱交換器２５によって冷却されるため、第３温水往路２８及び第３温水復路３０内には低温の冷水が循環している。一方、第４熱交換器２７においては、第４循環ポンプ４０により送られた温水が加熱され、第４温水往路３７を介して第２地中熱採熱管３９に温水が送られ、この第２地中熱採熱管３９において地中に冷房時の排熱が排出され、第４温水復路３８を介して第４循環ポンプ４０に温水が戻される。   Further, when the cooling operation is performed, since the hot water supplied to the heat load is cooled by the third heat exchanger 25, low-temperature cold water is contained in the third hot water forward path 28 and the third hot water return path 30. It is circulating. On the other hand, in the 4th heat exchanger 27, the warm water sent by the 4th circulation pump 40 is heated, and warm water is sent to the 2nd underground heat collection pipe 39 via the 4th warm water going way 37, and this 2nd In the underground heat collecting pipe 39, the exhaust heat at the time of cooling is discharged into the ground, and the warm water is returned to the fourth circulation pump 40 via the fourth warm water return path 38.

このとき、給湯用ヒートポンプ２においては、給湯用冷媒回路５が運転され、第２循環ポンプ２１により送られた温水は、第２熱交換器９によって熱交換が行われて冷却され、第１温水往路１０、第２三方弁１９を介して第１地中熱採熱管１６に送られる。そして、この第１地中熱採熱管１６内で地中熱の採熱を行って温水を加熱し、加熱された温水を第１温水復路１３、第３三方弁２０を介して第２循環ポンプ２１に戻している。   At this time, in the hot water supply heat pump 2, the hot water supply refrigerant circuit 5 is operated, and the hot water sent by the second circulation pump 21 is cooled by the heat exchange performed by the second heat exchanger 9. It is sent to the first underground heat collecting pipe 16 through the forward path 10 and the second three-way valve 19. Then, geothermal heat is collected in the first geothermal heat collecting pipe 16 to heat the hot water, and the heated hot water is supplied to the second circulation pump via the first hot water return path 13 and the third three-way valve 20. Return to 21.

このように、本実施形態においては、空調用ヒートポンプ３において冷房運転が行われ、同時に給湯用ヒートポンプ２において給湯運転が行われているときは、冷房によって生じる空調用ヒートポンプ３の冷房排熱が第２地中熱採熱管３９を介して地中に設置された地中管４６内に排出され、同時に第１地中熱採熱管１６によって地中管４６内の熱を採熱している。したがって、空調用ヒートポンプ３によって生じた冷房排熱を給湯用ヒートポンプ２における給湯運転に利用することができるため、ヒートポンプシステム１全体の成績係数を上昇させることができる。   Thus, in the present embodiment, when the cooling operation is performed in the air conditioning heat pump 3, and at the same time the hot water supply operation is performed in the hot water supply heat pump 2, the cooling exhaust heat of the air conditioning heat pump 3 generated by the cooling is first. 2 It is discharged into the underground pipe 46 installed underground through the underground heat collecting pipe 39, and at the same time, the heat in the underground pipe 46 is collected by the first underground heat collecting pipe 16. Therefore, since the cooling exhaust heat generated by the air conditioning heat pump 3 can be used for the hot water supply operation in the hot water supply heat pump 2, the coefficient of performance of the entire heat pump system 1 can be increased.

尚、上記実施形態においては、第２温度センサＴ２の検出値の閾値として４０℃という値を用いているが、これに限らずヒートポンプシステム１の設置された環境に応じて適宜定めることができる。同様に、熱負荷によって要求される高負荷運転時の温水の温度についても、上記実施形態のように７５℃ではなく、他の値にすることができる。また、給湯用冷媒回路５においては、二酸化炭素を冷媒として用いているが、これに限らず、サイクルの高圧側が超臨界状態となる冷媒であれば、他の冷媒を用いてもよい。また、空調用冷媒回路２２における冷媒もＲ４１０Ａ以外の冷媒を用いてもよい。   In the above embodiment, a value of 40 ° C. is used as the threshold value of the detection value of the second temperature sensor T2, but the value is not limited to this and can be determined as appropriate according to the environment in which the heat pump system 1 is installed. Similarly, the temperature of the hot water at the time of high load operation required by the heat load can be set to other values instead of 75 ° C. as in the above embodiment. Further, in the hot water supply refrigerant circuit 5, carbon dioxide is used as a refrigerant. However, the present invention is not limited to this, and other refrigerants may be used as long as the high pressure side of the cycle is in a supercritical state. Further, a refrigerant other than R410A may be used as the refrigerant in the air conditioning refrigerant circuit 22.

本発明のヒートポンプシステムの実施形態の一例を示す回路図。The circuit diagram which shows an example of embodiment of the heat pump system of this invention. 本実施形態のヒートポンプシステムの機能的構成を示すブロック図。The block diagram which shows the functional structure of the heat pump system of this embodiment. 図１のヒートポンプシステムにおいて給湯運転と暖房運転を行っている状態を示す説明図。Explanatory drawing which shows the state which is performing hot water supply operation and heating operation in the heat pump system of FIG. 図３の状態から条件が変化した状態を示す説明図。Explanatory drawing which shows the state from which the condition changed from the state of FIG. 図１のヒートポンプシステムにおいて高負荷暖房運転を行っている状態を示す説明図。Explanatory drawing which shows the state which is performing high load heating operation in the heat pump system of FIG. 図１のヒートポンプシステムにおいて給湯運転と冷房運転を行っている状態を示す説明図。Explanatory drawing which shows the state which is performing hot water supply operation and cooling operation in the heat pump system of FIG.

符号の説明Explanation of symbols

１…ヒートポンプシステム、４…貯湯タンク、５…給湯用冷媒回路、６…圧縮機、７…第１熱交換器、８…膨張弁、９…第２熱交換器、１０…第１温水往路、１１…第１三方弁（切替手段）、１３…第１温水復路、１４…第２温水往路、１５…第２温水復路、１６，１７，１８…給湯用採熱手段、２２…空調用冷媒回路、圧縮機２３…、２５…第３熱交換器、２６…膨張弁、２７…第４熱交換器、２８…第３温水往路、３０…第３温水復路、３１，３２，３５…熱負荷、３７…第４温水往路、３８…第４温水復路、３９…空調用採熱手段、４１…第５熱交換器、４２…第５温水回路、４７…コントローラ（制御手段）。   DESCRIPTION OF SYMBOLS 1 ... Heat pump system, 4 ... Hot water storage tank, 5 ... Refrigerant circuit for hot water supply, 6 ... Compressor, 7 ... 1st heat exchanger, 8 ... Expansion valve, 9 ... 2nd heat exchanger, 10 ... 1st hot water outgoing path, DESCRIPTION OF SYMBOLS 11 ... 1st three-way valve (switching means), 13 ... 1st warm water return path, 14 ... 2nd warm water return path, 15 ... 2nd warm water return path, 16, 17, 18 ... Hot water supply heat collecting means, 22 ... Air conditioning refrigerant circuit , Compressors 23 ..., 25 ... third heat exchanger, 26 ... expansion valve, 27 ... fourth heat exchanger, 28 ... third hot water outbound path, 30 ... third hot water return path, 31, 32, 35 ... heat load, 37... 4th warm water outbound path, 38... 4th warm water return path, 39... Air conditioning heat collecting means, 41... 5th heat exchanger, 42.

Claims (3)

圧縮機と、第１熱交換器と、膨張弁と、第２熱交換器とが介設され、該圧縮機から該膨張弁に至る高圧側で超臨界状態となる冷媒を循環させる給湯用冷媒回路と、
圧縮機と、第３熱交換器と、膨張弁と、第４熱交換器とが介設され、該圧縮機から該膨張弁に至る高圧側で気相から液相に相変化する冷媒を循環させる空調用冷媒回路と、
前記第１熱交換器により加熱された温水を貯湯タンクの上層に送る第１温水往路と、前記貯湯タンクの下層から前記第１熱交換器に温水を送る第１温水復路と、
前記第２熱交換器により熱交換が行われた温水を給湯用採熱手段に送る第２温水往路と、前記給湯用採熱手段から前記第２熱交換器に温水を送る第２温水復路と、
前記第３熱交換器で熱交換が行われた温水を熱負荷に送る第３温水往路と、前記熱負荷から前記第３熱交換器に温水を送る第３温水復路と、
前記第４熱交換器で熱交換が行われた温水を空調用採熱手段に送る第４温水往路と、前記空調用採熱手段から前記第４熱交換器に温水を送る第４温水復路と、
前記第１温水復路と並列に設けられ前記貯湯タンクの下層からの温水を前記第４温水復路と熱交換を行う第５熱交換器を介して前記第１熱交換器に送る第５温水回路と、
前記第１温水往路と前記第１温水復路との間で温水を循環させるか、又は前記第１温水往路と前記第５温水回路との間で温水を循環させるかを切り替える切替手段と、
前記貯湯タンクの下層の温度が所定の閾値以下のときは前記第１温水往路と前記第１温水復路との間で温水を循環させ、前記貯湯タンクの下層の温度が前記閾値を越えたときは前記第１温水往路と前記第５温水回路との間で温水を循環させるように前記切替手段を切り替える制御手段とを備えていることを特徴とするヒートポンプシステム。 A hot water supply refrigerant in which a compressor, a first heat exchanger, an expansion valve, and a second heat exchanger are interposed to circulate a refrigerant that is in a supercritical state on the high pressure side from the compressor to the expansion valve Circuit,
A compressor, a third heat exchanger, an expansion valve, and a fourth heat exchanger are interposed, and a refrigerant that changes phase from a gas phase to a liquid phase is circulated on the high pressure side from the compressor to the expansion valve. A refrigerant circuit for air conditioning
A first hot water forward path for sending hot water heated by the first heat exchanger to an upper layer of the hot water storage tank; a first hot water return path for sending hot water from the lower layer of the hot water storage tank to the first heat exchanger;
A second hot water outgoing path for sending the hot water heat-exchanged by the second heat exchanger to the hot water collecting means, and a second hot water return path for sending the hot water from the hot water collecting means to the second heat exchanger; ,
A third warm water forward path for sending warm water having been subjected to heat exchange in the third heat exchanger to a heat load; a third warm water return path for sending warm water from the heat load to the third heat exchanger;
A fourth warm water forward path for sending the hot water heat-exchanged in the fourth heat exchanger to the air conditioning heat collecting means, and a fourth hot water return path for sending the hot water from the air conditioning heat collecting means to the fourth heat exchanger; ,
A fifth hot water circuit that is provided in parallel with the first hot water return path and sends hot water from a lower layer of the hot water storage tank to the first heat exchanger via a fifth heat exchanger that exchanges heat with the fourth hot water return path; ,
Switching means for switching between circulating the warm water between the first warm water outbound path and the first warm water return path, or circulating the warm water between the first warm water outbound path and the fifth warm water circuit;
When the temperature of the lower layer of the hot water storage tank is equal to or lower than a predetermined threshold, hot water is circulated between the first warm water forward path and the first hot water return path, and when the temperature of the lower layer of the hot water storage tank exceeds the threshold value A heat pump system comprising: control means for switching the switching means so as to circulate hot water between the first hot water outgoing path and the fifth hot water circuit. 前記貯湯タンクの上層からの温水を前記第３温水往路と熱交換を行う第６熱交換器を介して前記貯湯タンクの下層に送る第６温水回路をさらに備え、
前記制御手段は、前記熱負荷で要求される温水の温度が所定の第２閾値を越えているときは前記第６温水回路に温水を循環させ、前記熱負荷で要求される温水の温度が前記第２閾値以下の時は前記第６温水回路の温水の循環を停止させるものであることを特徴とする請求項１に記載のヒートポンプシステム。 A sixth hot water circuit for sending the hot water from the upper layer of the hot water storage tank to the lower layer of the hot water storage tank through a sixth heat exchanger for exchanging heat with the third hot water outbound path;
The control means circulates hot water in the sixth hot water circuit when the temperature of the hot water required by the heat load exceeds a predetermined second threshold, and the temperature of the hot water required by the heat load is 2. The heat pump system according to claim 1, wherein when the temperature is equal to or less than a second threshold value, circulation of hot water in the sixth hot water circuit is stopped. 前記給湯用採熱手段は地熱を採熱する第１地中熱採熱管を有し、前記空調用採熱手段は地熱を採熱する第２地中熱採熱管を有し、前記第１地中熱採熱管と前記第２地中熱採熱管とは地中において近接して配設されていることを特徴とする請求項１又は２に記載のヒートポンプシステム。   The hot water supply heat collecting means has a first geothermal heat collecting pipe for collecting geothermal heat, the air conditioning heat collecting means has a second geothermal heat collecting pipe for collecting geothermal heat, and the first ground heat collecting pipe. The heat pump system according to claim 1 or 2, wherein the intermediate heat collection pipe and the second underground heat collection pipe are arranged close to each other in the ground.
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