JP2008096101A - Heat pump type hot water supply apparatus - Google Patents
Heat pump type hot water supply apparatus Download PDFInfo
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本発明は、液ガス熱交換器を用いたヒートポンプ式給湯装置に関するものである。 The present invention relates to a heat pump type hot water supply apparatus using a liquid gas heat exchanger.
ヒートポンプ式給湯装置の冷凍サイクルの途中に液ガス熱交換器を用いたのが提供されている。この液ガス熱交換器は、水熱交換器から流出して減圧機構に流入する高圧冷媒と、空気熱交換器から流出した低圧冷媒との熱交換を行なうものである。この液ガス熱交換器を設けることによって、水熱交換器（ガス冷却器）からの冷媒に過冷却を付与し、また、圧縮機に入る冷媒を加熱して、圧縮機の湿り圧縮を防止するようにしている。 It has been provided that a liquid gas heat exchanger is used in the middle of the refrigeration cycle of a heat pump hot water supply apparatus. This liquid gas heat exchanger performs heat exchange between the high-pressure refrigerant that flows out of the water heat exchanger and flows into the decompression mechanism, and the low-pressure refrigerant that flows out of the air heat exchanger. By providing this liquid gas heat exchanger, the refrigerant from the water heat exchanger (gas cooler) is supercooled, and the refrigerant entering the compressor is heated to prevent wet compression of the compressor. I am doing so.
図６に該液ガス熱交換器を用いたヒートポンプ式給湯装置の簡略図を示している（特許文献１参照）。このヒートポンプ式給湯装置は、貯湯タンク１を有するタンクユニット２と、冷凍サイクル３を有するヒートポンプユニット４とを備えている。そして、タンクユニット２の貯湯タンク１には、その底壁に給水口５が設けられると共に、その上壁に出湯口６が設けられている。この給水口５から貯湯タンク１に水道水が供給され、出湯口６から高温の温湯が出湯される。また、貯湯タンク１には、その底壁に取水口７が開設されると共に、側壁（周壁）の上部に湯入口８が開設され、取水口７と湯入口８とが循環路９にて連結されている。そして、この循環路９に水循環用ポンプ１０と熱交換路１１とが介設されている。すなわち、水循環用ポンプ１０が駆動すると、貯湯タンク１内の未加熱水が取水口７から循環路９に流出して、熱交換路１１を介して湯入口８から貯湯タンク１内に返流する。 FIG. 6 shows a simplified diagram of a heat pump type hot water supply apparatus using the liquid gas heat exchanger (see Patent Document 1). The heat pump type hot water supply apparatus includes a tank unit 2 having a hot water storage tank 1 and a heat pump unit 4 having a refrigeration cycle 3. The hot water storage tank 1 of the tank unit 2 is provided with a water supply port 5 on its bottom wall and a hot water outlet 6 on its upper wall. Tap water is supplied from the water supply port 5 to the hot water storage tank 1, and hot hot water is discharged from the hot water outlet 6. In addition, the hot water storage tank 1 has a water intake 7 at the bottom wall and a hot water inlet 8 at the top of the side wall (peripheral wall), and the water intake 7 and the hot water inlet 8 are connected by a circulation path 9. Has been. The circulation path 9 is provided with a water circulation pump 10 and a heat exchange path 11. That is, when the water circulation pump 10 is driven, unheated water in the hot water storage tank 1 flows out from the water intake 7 to the circulation path 9 and returns to the hot water storage tank 1 from the hot water inlet 8 through the heat exchange path 11. .
次に、冷凍サイクル３は、圧縮機１３と、上記熱交換路１１を構成する水熱交換器１４と、電動膨張弁（減圧機構）１５と、空気熱交換器１６とを順に接続して構成されている。すなわち、圧縮機１３の吐出口と水熱交換器１４とを冷媒通路１７にて接続し、水熱交換器１４と電動膨張弁１５とを冷媒通路１８、３６にて接続し、電動膨張弁１５と空気熱交換器１６とを冷媒通路１９にて接続し、空気熱交換器１６と圧縮機１３とを冷媒通路３７及び冷媒通路２１にて接続している。そして、冷媒としては、例えば、高圧側を超臨界圧力で使用する炭酸ガス等の自然冷媒が用いられる。 Next, the refrigeration cycle 3 is configured by connecting a compressor 13, a water heat exchanger 14 that constitutes the heat exchange path 11, an electric expansion valve (decompression mechanism) 15, and an air heat exchanger 16 in this order. Has been. That is, the discharge port of the compressor 13 and the water heat exchanger 14 are connected by the refrigerant passage 17, the water heat exchanger 14 and the electric expansion valve 15 are connected by the refrigerant passages 18 and 36, and the electric expansion valve 15 And the air heat exchanger 16 are connected by a refrigerant passage 19, and the air heat exchanger 16 and the compressor 13 are connected by a refrigerant passage 37 and a refrigerant passage 21. And as a refrigerant | coolant, natural refrigerant | coolants, such as a carbon dioxide gas which uses a high voltage | pressure side by a supercritical pressure, are used, for example.
また、冷凍サイクル３は、水熱交換器１４から流出した高圧冷媒を冷却する液ガス熱交換器２５を備えている。この場合、液ガス熱交換器２５は、水熱交換器１４から流出した高圧冷媒が通過する第１通路２６と、空気熱交換器１６から流出した低圧冷媒が通過する第２通路２７とを備えている。そして、第１通路２６を通過する高温高圧の冷媒と、第２通路２７を通過する低温低圧の冷媒との間で熱交換が行なわれる。 The refrigeration cycle 3 includes a liquid gas heat exchanger 25 that cools the high-pressure refrigerant that has flowed out of the water heat exchanger 14. In this case, the liquid gas heat exchanger 25 includes a first passage 26 through which the high-pressure refrigerant flowing out from the water heat exchanger 14 passes, and a second passage 27 through which the low-pressure refrigerant flowing out from the air heat exchanger 16 passes. ing. Then, heat exchange is performed between the high-temperature and high-pressure refrigerant passing through the first passage 26 and the low-temperature and low-pressure refrigerant passing through the second passage 27.
次に、このヒートポンプ式給湯装置の運転動作（湯沸かし運転）を説明する。圧縮機１３を駆動すると共に、水循環用ポンプ１０を駆動（作動）する。すると、貯湯タンク１の底部に設けた取水口７から貯溜水（温湯）が流出し、これが循環路９の熱交換路１１を流通する。また、圧縮機１３からの吐出冷媒が、水熱交換器１４、減圧機構１５、空気熱交換器１６とを順次経由して上記圧縮機１３へと返流する。そのため、循環路９の熱交換路１１を流通する水がガス冷却器である水熱交換器１４によって加熱され（沸き上げられ）、湯入口８から貯湯タンク１の上部に返流される。そして、このような動作を継続して行なうことによって、貯湯タンク１に高温の温湯が貯湯されることになる。なお、現状の電力料金制度は夜間の電力料金単価が昼間に比べて低く設定されているので、この運転は、低額である深夜時間帯に行ない、コストの低減を図るようにしている。 Next, the operation of the heat pump type hot water supply apparatus (water heater operation) will be described. The compressor 13 is driven and the water circulation pump 10 is driven (actuated). Then, stored water (hot water) flows out from the water intake 7 provided at the bottom of the hot water storage tank 1, and this flows through the heat exchange path 11 of the circulation path 9. Further, the refrigerant discharged from the compressor 13 returns to the compressor 13 via the water heat exchanger 14, the decompression mechanism 15, and the air heat exchanger 16 in order. Therefore, the water flowing through the heat exchange path 11 of the circulation path 9 is heated (boiling) by the water heat exchanger 14 that is a gas cooler, and returned to the upper part of the hot water storage tank 1 from the hot water inlet 8. Then, by continuously performing such an operation, hot hot water is stored in the hot water storage tank 1. In the current power rate system, the unit price of the nightly power rate is set lower than in the daytime, so this operation is performed in the low-night time zone, which is a low price, so as to reduce the cost.
ところで、上記ヒートポンプユニット４において、液ガス熱交換器２５が無ければ、熱交換路１１への入水温度が低温であるときには、図７（ａ）のＡのようなサイクルを構成するが、熱交換路１１への入水温度が高温であるときには、図７（ａ）のＢのようなサイクルとなる。すなわち、図７（ａ）のＡのサイクルと、図７（ａ）のＢのサイクルとでは水熱交換器１４である放熱器内の冷媒量差が大きく、熱交換路１１への入水温度が上昇すれば、放熱過程でのエンタルピ差が狭くなって、湯加熱能力及びＣＯＰが減少することになる。これに対して、液ガス熱交換器２５を備えている場合には、入水温度変化による高圧側の冷媒量差を吸収し、入水温度が高温時でも液ガス熱交換器２５の出口冷媒の密度が大きく、図７（ｂ）のＣのような正常のサイクルを形成する。 By the way, in the heat pump unit 4, if there is no liquid gas heat exchanger 25, a cycle such as A in FIG. 7A is configured when the temperature of water entering the heat exchange path 11 is low. When the incoming water temperature to the path 11 is high, the cycle is as shown in FIG. That is, there is a large refrigerant amount difference in the radiator that is the water heat exchanger 14 between the cycle A in FIG. 7A and the cycle B in FIG. 7A, and the temperature of water entering the heat exchange path 11 is high. If it rises, the enthalpy difference in the heat dissipation process will become narrow, and the hot water heating capacity and COP will decrease. On the other hand, when the liquid gas heat exchanger 25 is provided, the refrigerant amount difference on the high pressure side due to the change in the incoming water temperature is absorbed, and the density of the outlet refrigerant of the liquid gas heat exchanger 25 even when the incoming water temperature is high. Is large and forms a normal cycle as shown in FIG. 7B.
このように、上記ヒートポンプ式給湯装置では、水熱交換器１４から流出して減圧機構１５に流入する高圧冷媒と、空気熱交換器１６から流出した低圧冷媒との熱交換を行なう液ガス熱交換器２５を設けているので、水熱交換器（ガス冷却器）１４からの冷媒に過冷却を付与し、また、圧縮機１３に入る冷媒を加熱することができる。このため、圧縮機１３の湿り圧縮を防止することができ、安定した運転が可能となる。 As described above, in the heat pump hot water supply apparatus, liquid gas heat exchange is performed to exchange heat between the high-pressure refrigerant that flows out of the water heat exchanger 14 and flows into the decompression mechanism 15 and the low-pressure refrigerant that flows out of the air heat exchanger 16. Since the unit 25 is provided, supercooling can be given to the refrigerant from the water heat exchanger (gas cooler) 14 and the refrigerant entering the compressor 13 can be heated. For this reason, wet compression of the compressor 13 can be prevented, and stable operation is possible.
しかしながら、特許文献１に示す従来例においては、上記水熱交換器１４と液ガス熱交換器２５とが離れて配置されていたため、水熱交換器１４と液ガス熱交換器２５との間の距離が長く、そのため、水熱交換器１４と液ガス熱交換器２５との配管が煩雑であるという問題があった。 However, in the conventional example shown in Patent Document 1, since the water heat exchanger 14 and the liquid gas heat exchanger 25 are arranged apart from each other, the water heat exchanger 14 and the liquid gas heat exchanger 25 are arranged between them. The distance is long, so that there is a problem that the piping between the water heat exchanger 14 and the liquid gas heat exchanger 25 is complicated.
本発明は上述の問題点に鑑みて提供したものであって、水熱交換器と液ガス熱交換器との配管を容易にし、また、液ガス熱交換器の放熱ロスを低減することを目的としたヒートポンプ式給湯装置を提供するものである。 The present invention has been provided in view of the above-described problems, and it is an object of the present invention to facilitate piping between a water heat exchanger and a liquid gas heat exchanger and to reduce heat dissipation loss of the liquid gas heat exchanger. A heat pump type hot water supply apparatus is provided.
そこで、本発明の請求項１に記載のヒートポンプ式給湯装置では、圧縮機１３と水熱交換器１４と減圧機構１５と空気熱交換器１６とを順次接続したヒートポンプユニット４を備え、上記水熱交換器１４にて構成される熱交換路１１に未加熱水を供給してこの未加熱水を加熱する沸上運転を可能とし、上記水熱交換器１４から流出して減圧機構１５に流入する高圧冷媒と、上記空気熱交換器１６から流出した低圧冷媒との熱交換を行なう液ガス熱交換器２５を設けたヒートポンプ式給湯装置において、上記水熱交換器１４の近傍に上記液ガス熱交換器２５を配置していることを特徴としている。 Therefore, the heat pump hot water supply apparatus according to claim 1 of the present invention includes the heat pump unit 4 in which the compressor 13, the water heat exchanger 14, the decompression mechanism 15, and the air heat exchanger 16 are sequentially connected, and the water heat A boiling operation for supplying unheated water to the heat exchange path 11 constituted by the exchanger 14 to heat the unheated water is enabled, and the water is discharged from the water heat exchanger 14 and flows into the pressure reducing mechanism 15. In a heat pump hot water supply apparatus provided with a liquid gas heat exchanger 25 for performing heat exchange between the high pressure refrigerant and the low pressure refrigerant flowing out of the air heat exchanger 16, the liquid gas heat exchange is provided in the vicinity of the water heat exchanger 14. It is characterized in that a container 25 is arranged.
請求項２に記載のヒートポンプ式給湯装置では上記水熱交換器１４の高温部１４ａには液ガス熱交換器２５の高温部２５ａを、水熱交換器１４の低温部１４ｂには液ガス熱交換器２５の低温部２５ｂをそれぞれ対応させた位置に配置していることを特徴としている。 In the heat pump type hot water supply apparatus according to claim 2, the high temperature portion 14a of the water heat exchanger 14 has a high temperature portion 25a of the liquid gas heat exchanger 25, and the low temperature portion 14b of the water heat exchanger 14 has liquid gas heat exchange. The low-temperature part 25b of the vessel 25 is arranged at a corresponding position.
請求項３に記載のヒートポンプ式給湯装置では、上記液ガス熱交換器２５は、一対のパイプ状の第１通路２６及び第２通路２７を長手方向に平行に接触させて構成されており、該液ガス熱交換器２５を、略中央部分をヘアピン状に折り曲げていることを特徴としている。 In the heat pump type hot water supply apparatus according to claim 3, the liquid gas heat exchanger 25 is configured by contacting a pair of pipe-shaped first passage 26 and second passage 27 in parallel in the longitudinal direction, The liquid gas heat exchanger 25 is characterized in that a substantially central portion is bent into a hairpin shape.
請求項４に記載のヒートポンプ式給湯装置では、上部水熱交換器１４の周囲を囲むようにして上部液ガス熱交換器２５を配置していることを特徴としている。 The heat pump type hot water supply apparatus according to claim 4 is characterized in that the upper liquid gas heat exchanger 25 is arranged so as to surround the upper water heat exchanger 14.
本発明の請求項１に記載のヒートポンプ式給湯装置によれば、水熱交換器の近傍に液ガス熱交換器を配置しているので、水熱交換器と液ガス熱交換器との間の距離が短くなり、両者間の配管が簡易となる。 According to the heat pump type hot water supply apparatus of the first aspect of the present invention, since the liquid gas heat exchanger is disposed in the vicinity of the water heat exchanger, it is provided between the water heat exchanger and the liquid gas heat exchanger. The distance is shortened and piping between the two is simplified.
請求項２に記載のヒートポンプ式給湯装置によれば、水熱交換器の温度分布と液ガス熱交換器の温度分布とを対応させて配置しているので、液ガス熱交換器の放熱ロスの低減を図ることができる。 According to the heat pump type hot water supply apparatus according to claim 2, since the temperature distribution of the water heat exchanger and the temperature distribution of the liquid gas heat exchanger are arranged corresponding to each other, the heat dissipation loss of the liquid gas heat exchanger is reduced. Reduction can be achieved.
請求項３に記載のヒートポンプ式給湯装置によれば、液ガス熱交換器は、一対のパイプ状の第１通路及び第２通路を長手方向に平行に接触させて構成されており、該液ガス熱交換器を、略中央部分をヘアピン状折り曲げているので、パイプ状の液ガス熱交換器を複数本用いた形となって、液ガス熱交換器自体の距離を長くとることができ、そのため、高圧冷媒と低圧冷媒との熱交換を行なうべく必要な有効長をコンパクトに得ることができる。 According to the heat pump type hot water supply apparatus of claim 3, the liquid gas heat exchanger is configured by bringing a pair of pipe-shaped first passage and second passage into contact with each other in parallel in the longitudinal direction, and the liquid gas Because the heat exchanger is bent in the shape of a hairpin at the center, it becomes a form that uses multiple pipe-like liquid gas heat exchangers, and the distance of the liquid gas heat exchanger itself can be increased. The effective length necessary for heat exchange between the high-pressure refrigerant and the low-pressure refrigerant can be obtained in a compact manner.
請求項４に記載のヒートポンプ式給湯装置によれば、水熱交換器の周囲を囲むようにして液ガス熱交換器を配置しているので、液ガス熱交換器をコンパクトに配置できて、余分なスペースが不要となる。 According to the heat pump type hot water supply apparatus according to claim 4, since the liquid gas heat exchanger is disposed so as to surround the periphery of the water heat exchanger, the liquid gas heat exchanger can be disposed in a compact manner, and an extra space is provided. Is no longer necessary.
以下、本発明の実施の形態を図面を参照して詳細に説明する。なお、本発明は、液ガス熱交換器２５の配置構造に特徴を有するものであり、ヒートポンプ式給湯装置の配管構成は図６の場合と同様である。 Hereinafter, embodiments of the present invention will be described in detail with reference to the drawings. In addition, this invention has the characteristics in the arrangement | positioning structure of the liquid gas heat exchanger 25, and the piping structure of a heat pump type hot-water supply apparatus is the same as that of the case of FIG.
図１は主要な構成部材だけを表したヒートポンプユニット４の分解斜視図を示し、金属製の底板４０の上面に立設した仕切板４１の一方側を圧縮機１３等を配置している機械室４２とし、仕切板４１の他方側を空気熱交換器１６、ファン２２等が配置されるファン室４３としている。また、ファン２２の前面側には天板４４を一体化した前板４５が配置され、この略格子状の前板４５の内面側にベルマウス４６がネジ４７により固定されるようになっている。なお、ファン２２が回転駆動されることで、空気が前板４５、ベルマウス４６の円形の開口部４８を介して吹き出され、その風が空気熱交換器１６を通過することで、該空気熱交換器１６が冷却される。 FIG. 1 is an exploded perspective view of a heat pump unit 4 showing only main components, and a machine room in which a compressor 13 and the like are arranged on one side of a partition plate 41 erected on the upper surface of a metal bottom plate 40. 42, and the other side of the partition plate 41 is a fan chamber 43 in which the air heat exchanger 16, the fan 22, and the like are arranged. Further, a front plate 45 integrated with a top plate 44 is disposed on the front side of the fan 22, and a bell mouth 46 is fixed to the inner surface side of the substantially lattice-shaped front plate 45 with screws 47. . When the fan 22 is driven to rotate, air is blown out through the front opening 45 and the circular opening 48 of the bell mouth 46, and the air passes through the air heat exchanger 16 so that the air heat is The exchanger 16 is cooled.
図２は空気熱交換器１６の背面側から見た分解斜視図であり、図３は要部拡大断面図を示している。空気熱交換器１６は略Ｌ型に形成されており、この空気熱交換器１６を支持固定する支持板５１も略Ｌ型に形成されていて、この支持板５１の上面に空気熱交換器１６が支持固定されている。支持板５１の下部は、底板４０の端縁より立ち上がっているフランジ５２の内側に位置して該支持板５１が底板４０側に配置される。なお、図３に示すように、支持板５１の上片５３の上面に形成されている台座部５４の上面に空気熱交換器１６が位置決め固定されている。 FIG. 2 is an exploded perspective view of the air heat exchanger 16 as seen from the back side, and FIG. The air heat exchanger 16 is formed in a substantially L shape, and a support plate 51 for supporting and fixing the air heat exchanger 16 is also formed in a substantially L shape, and the air heat exchanger 16 is formed on the upper surface of the support plate 51. Is supported and fixed. The lower portion of the support plate 51 is located inside the flange 52 rising from the edge of the bottom plate 40, and the support plate 51 is disposed on the bottom plate 40 side. As shown in FIG. 3, the air heat exchanger 16 is positioned and fixed on the upper surface of the pedestal portion 54 formed on the upper surface of the upper piece 53 of the support plate 51.
また、図３に示すように、底板４０の上面であってファン室４３に位置する箇所（空気熱交換器１６の下部の位置）には水熱交換器１４が配置されており、この水熱交換器１４は、外殻が断熱材５５で構成されていて、この断熱材５５の内部にパイプ状で二重構造とした水熱交換器部材５６が上下方向に積層して配管されている。なお、水熱交換器部材５６の上部は、高温冷媒が流れるように配管され、水熱交換器部材５６の下部は低温冷媒が流れるように配管されている。ここで、水熱交換器部材５６に高温の冷媒が流れる水熱交換器１４の上部を高温部１４ａとし、水熱交換器部材５６に低温の冷媒が流れる水熱交換器１４の下部を低温部１４ｂとする。 Further, as shown in FIG. 3, the water heat exchanger 14 is disposed at a position (a position below the air heat exchanger 16) located on the upper surface of the bottom plate 40 and in the fan chamber 43. The exchanger 14 has an outer shell made of a heat insulating material 55, and a water heat exchanger member 56 having a pipe-like and double structure is laminated inside the heat insulating material 55 in the vertical direction. The upper part of the water heat exchanger member 56 is piped so that the high-temperature refrigerant flows, and the lower part of the water heat exchanger member 56 is piped so that the low-temperature refrigerant flows. Here, the upper part of the water heat exchanger 14 in which the high temperature refrigerant flows through the water heat exchanger member 56 is referred to as a high temperature part 14a, and the lower part of the water heat exchanger 14 in which the low temperature refrigerant flows through the water heat exchanger member 56 as a low temperature part. 14b.
液ガス熱交換器２５は、水熱交換器１４からの高圧冷媒（液）に過冷却を付与し、また、圧縮機１３に入る低圧冷媒（ガス）を加熱して、圧縮機１３の湿り圧縮を防止しているものであり、図５に示すように、液ガス熱交換器２５の第１通路２６に流入する高圧冷媒の温度は約２０℃であり、第１通路２６から流出する高圧冷媒の温度は約０℃である。また、空気熱交換器１６から液ガス熱交換器２５の第２通路２７に流入する低圧冷媒の温度は約０℃であり、第２通路２７から流出する低圧冷媒の温度は約５〜７℃である。 The liquid gas heat exchanger 25 provides supercooling to the high-pressure refrigerant (liquid) from the water heat exchanger 14 and heats the low-pressure refrigerant (gas) entering the compressor 13 to wet-compress the compressor 13. As shown in FIG. 5, the temperature of the high-pressure refrigerant flowing into the first passage 26 of the liquid gas heat exchanger 25 is about 20 ° C., and the high-pressure refrigerant flowing out of the first passage 26 The temperature is about 0 ° C. The temperature of the low-pressure refrigerant flowing from the air heat exchanger 16 into the second passage 27 of the liquid gas heat exchanger 25 is about 0 ° C., and the temperature of the low-pressure refrigerant flowing out of the second passage 27 is about 5 to 7 ° C. It is.
次に、この液ガス熱交換器２５の構成、配置位置について説明する。液ガス熱交換器２５は、図４に示すように、水熱交換器１４からの高圧冷媒が流れるパイプ状の第１通路２６と、この第１通路２６の径より大径としたパイプ状の第２通路２７とで構成されている。そして、第１通路２６及び第２通路２７は並設されていて、両通路２６、２７はロウ付けにて固着されている。液ガス熱交換器２５の略中央部分の折り返し部６０にて略コ字型であってヘアピン状に折り曲げられており、複数本となるような形で上下方向に両通路２６、２７が位置するように折曲してある。また、液ガス熱交換器２５は水熱交換器１４の周囲に囲むようにして配置すべく、液ガス熱交換器２５の途中の折曲部６１で略９０°に折曲されている。 Next, the configuration and arrangement position of the liquid gas heat exchanger 25 will be described. As shown in FIG. 4, the liquid gas heat exchanger 25 includes a pipe-shaped first passage 26 through which the high-pressure refrigerant from the water heat exchanger 14 flows, and a pipe-shaped pipe having a diameter larger than the diameter of the first passage 26. The second passage 27 is configured. The first passage 26 and the second passage 27 are arranged side by side, and both the passages 26 and 27 are fixed by brazing. The folded portion 60 at the substantially central portion of the liquid gas heat exchanger 25 is substantially U-shaped and is bent into a hairpin shape, and both passages 26 and 27 are positioned in the vertical direction so as to form a plurality. It is bent like this. Further, the liquid gas heat exchanger 25 is bent at approximately 90 ° at a bent portion 61 in the middle of the liquid gas heat exchanger 25 so as to be disposed so as to surround the water heat exchanger 14.
また、液ガス熱交換器２５の第１通路２６の一方の端部を液（高圧冷媒のこと、以下同じ）が流入する液側入口部６２とし、第１通路２６の他方の端部を液が流出する液側出口部６３としている。また、第２通路２７の一方の端部をガス（低圧冷媒のこと、以下同じ）が流入するガス側入口部６４とし、第２通路２７の他方の端部をガスが流出するガス側出口部６５としている。そして、液ガス熱交換器２５の第１通路２６の液が流れる方向と、第２通路２７のガスが流れる方向とが逆方向となるようにしている。 In addition, one end of the first passage 26 of the liquid gas heat exchanger 25 is a liquid side inlet portion 62 into which liquid (a high-pressure refrigerant, hereinafter the same) flows, and the other end of the first passage 26 is a liquid. The liquid side outlet portion 63 from which the liquid flows out. In addition, one end of the second passage 27 is a gas side inlet portion 64 through which gas (a low-pressure refrigerant, the same applies hereinafter) flows, and the other end of the second passage 27 is a gas side outlet portion through which gas flows out. 65. The direction in which the liquid in the first passage 26 of the liquid gas heat exchanger 25 flows is opposite to the direction in which the gas in the second passage 27 flows.
ヒートポンプユニット４の簡略図を示す図５において、冷媒通路１８が液ガス熱交換器２５の第１通路２６の液側入口部６２に接続され、冷媒通路３６が液側出口部６３に接続される。また、冷媒通路３７が液ガス熱交換器２５の第２通路２７のガス側入口部６４に接続され、ガス側出口部６５に冷媒通路２１が接続される。 In FIG. 5 showing a simplified diagram of the heat pump unit 4, the refrigerant passage 18 is connected to the liquid side inlet portion 62 of the first passage 26 of the liquid gas heat exchanger 25, and the refrigerant passage 36 is connected to the liquid side outlet portion 63. . The refrigerant passage 37 is connected to the gas side inlet portion 64 of the second passage 27 of the liquid gas heat exchanger 25, and the refrigerant passage 21 is connected to the gas side outlet portion 65.
また、図３に示すように、水熱交換器１４の近傍に液ガス熱交換器２５を配置しており、かかる場合、上下方向に第２通路２７、第１通路２６、及び折り返した第１通路２６、第２通路２７とが直線状となるように配置される。そして、図５に示す液ガス熱交換器２５の温度分布が一方が高温側となっていて、他方が低温側となっており、液ガス熱交換器２５の折り返し部６０で折り返した高温側の第２通路２７と第１通路２６とを上部に配置し、低温側の第１通路２６と第２通路２７を下部に配置している。ここで、上部に配置した高温側の第２通路２７と第１通路２６を高温部２５ａとし、下部に配置した低温側の第１通路２６と第２通路２７を低温部２５ｂとする。すなわち、水熱交換器１４側の高温部１４ａと、液ガス熱交換器２５側の高温部１４ａとを対応させて配置し、水熱交換器１４側の低温部１４ｂと液ガス熱交換器２５側の低温部２５ｂとを対応させて配置している。このようにして水熱交換器１４側の高低の温度分布に、液ガス熱交換器２５側の高低の温度分布を対応させることで、水熱交換器１４からの放熱ロスの低減を図っている。 Moreover, as shown in FIG. 3, the liquid gas heat exchanger 25 is arrange | positioned in the vicinity of the water heat exchanger 14, and in such a case, the 2nd channel | path 27, the 1st channel | path 26, and the 1st folded back | folded up and down. The passage 26 and the second passage 27 are arranged in a straight line. And the temperature distribution of the liquid gas heat exchanger 25 shown in FIG. 5 is one side of the high temperature side, and the other is the low temperature side. The second passage 27 and the first passage 26 are disposed in the upper portion, and the first passage 26 and the second passage 27 on the low temperature side are disposed in the lower portion. Here, the high temperature side second passage 27 and the first passage 26 arranged in the upper part are referred to as a high temperature portion 25a, and the low temperature side first passage 26 and the second passage 27 arranged in the lower portion are referred to as a low temperature portion 25b. That is, the high temperature part 14a on the water heat exchanger 14 side and the high temperature part 14a on the liquid gas heat exchanger 25 side are arranged in correspondence with each other, and the low temperature part 14b on the water heat exchanger 14 side and the liquid gas heat exchanger 25 are arranged. The low temperature part 25b of the side is arrange | positioned correspondingly. In this way, the heat loss from the water heat exchanger 14 is reduced by making the temperature distribution on the liquid gas heat exchanger 25 side correspond to the temperature distribution on the water heat exchanger 14 side. .
そして、一対のパイプ状の第１通路２６及び第２通路２７で構成される液ガス熱交換器２５は、全体形状としては、図２及び図４に示すように、略Ｌ型に形成されており、この略Ｌ型に形成されている液ガス熱交換器２５を水熱交換器１４の周囲を囲むように配置している。また、このように液ガス熱交換器２５を水熱交換器１４の背面から側面にかけて配置した場合、図３に示すように、支持板５１の内側面と水熱交換器１４との間に形成されるスペース６７に液ガス熱交換器２５が配置されることになり、スペース６７を有効に利用している。このように、水熱交換器１４の周囲を囲むようにして液ガス熱交換器２５を配置しているので、液ガス熱交換器２５をコンパクトに配置できて、余分なスペースが不要となる。 And the liquid gas heat exchanger 25 comprised by a pair of pipe-shaped 1st channel | path 26 and the 2nd channel | path 27 is formed in a substantially L shape as shown in FIG.2 and FIG.4 as a whole shape. The liquid gas heat exchanger 25 formed in the substantially L shape is arranged so as to surround the periphery of the water heat exchanger 14. Further, when the liquid gas heat exchanger 25 is arranged from the back surface to the side surface of the water heat exchanger 14 as described above, it is formed between the inner surface of the support plate 51 and the water heat exchanger 14 as shown in FIG. The liquid gas heat exchanger 25 is arranged in the space 67 to be used, and the space 67 is effectively used. Thus, since the liquid gas heat exchanger 25 is arranged so as to surround the water heat exchanger 14, the liquid gas heat exchanger 25 can be arranged in a compact manner, and an extra space becomes unnecessary.
このように、本実施形態では、水熱交換器１４の近傍に液ガス熱交換器２５を配置しているので、該水熱交換器１４と液ガス熱交換器２５との間の距離が短くなり、両者間の配管が簡易となる。また、一対のパイプ状の第１通路２６及び第２通路２７を長手方向に平行に接触させて構成した液ガス熱交換器２５を、略中央部分の折り返し部６０にてヘアピン状の折り曲げると共に、空気熱交換器１６の略Ｌ型の形状に対応させるように水熱交換器１４の背面側と側面側にかけて略Ｌ型に折曲しているので、パイプ状の液ガス熱交換器２５を複数本用いた形となって、液ガス熱交換器２５自体の距離を長くとることができ、そのため、高圧冷媒と低圧冷媒との熱交換を行なうべく必要な有効長をコンパクト得ることができる。さらには、液ガス熱交換器２５を水熱交換器１４の背面から側面にかけて配置した場合に、図３に示すように、液ガス熱交換器２５は空気熱交換器１６の下方に位置して配置されることになるので、ファン２２による風が液ガス熱交換器２５に当たることもなく、そのため、送風による液ガス熱交換器２５の放熱ロスを少なくすることができる。 Thus, in this embodiment, since the liquid gas heat exchanger 25 is arrange | positioned in the vicinity of the water heat exchanger 14, the distance between this water heat exchanger 14 and the liquid gas heat exchanger 25 is short. Therefore, piping between the two is simplified. In addition, the liquid gas heat exchanger 25 configured by bringing the pair of pipe-shaped first passage 26 and the second passage 27 into contact with each other in parallel in the longitudinal direction is bent in a hairpin shape at the folded portion 60 in the substantially central portion, Since it is bent into a substantially L shape over the back side and the side of the water heat exchanger 14 so as to correspond to the substantially L shape of the air heat exchanger 16, a plurality of pipe-like liquid gas heat exchangers 25 are provided. In this form, the distance between the liquid gas heat exchanger 25 itself can be increased, and therefore the effective length necessary for heat exchange between the high-pressure refrigerant and the low-pressure refrigerant can be obtained in a compact manner. Furthermore, when the liquid gas heat exchanger 25 is arranged from the back surface to the side surface of the water heat exchanger 14, the liquid gas heat exchanger 25 is positioned below the air heat exchanger 16, as shown in FIG. Therefore, the wind generated by the fan 22 does not hit the liquid gas heat exchanger 25, and therefore the heat radiation loss of the liquid gas heat exchanger 25 due to blowing can be reduced.
４ ヒートポンプユニット
１１ 熱交換路
１４ 水熱交換器
１４ａ 高温部
１４ｂ 低温部
１５ 減圧機構
１６ 空気熱交換器
２５ 液ガス熱交換器
２５ａ 高温部
２５ｂ 低温部
２６ 第１通路
２７ 第２通路
4 Heat Pump Unit 11 Heat Exchange Path 14 Water Heat Exchanger 14a High Temperature Part 14b Low Temperature Part 15 Decompression Mechanism 16 Air Heat Exchanger 25 Liquid Gas Heat Exchanger 25a High Temperature Part 25b Low Temperature Part 26 First Passage 27 Second Passage
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| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JP2009300000A (en) * | 2008-06-13 | 2009-12-24 | Sharp Corp | Refrigerator-freezer and cooling storage |
| JP2010085067A (en) * | 2008-10-02 | 2010-04-15 | Denso Corp | Refrigerating cycle device |
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|---|---|---|---|---|
| JP2002115924A (en) * | 2000-07-31 | 2002-04-19 | Daikin Ind Ltd | Heat pump type hot water heater apparatus |
| JP2003148803A (en) * | 2001-11-15 | 2003-05-21 | Hitachi Ltd | Heat pump-type water heater |
| JP2004085183A (en) * | 2002-06-24 | 2004-03-18 | Denso Corp | Vapor compression type refrigerator |
| JP2005147467A (en) * | 2003-11-13 | 2005-06-09 | Matsushita Electric Ind Co Ltd | Heat pump heat source machine |
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| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JP2002115924A (en) * | 2000-07-31 | 2002-04-19 | Daikin Ind Ltd | Heat pump type hot water heater apparatus |
| JP2003148803A (en) * | 2001-11-15 | 2003-05-21 | Hitachi Ltd | Heat pump-type water heater |
| JP2004085183A (en) * | 2002-06-24 | 2004-03-18 | Denso Corp | Vapor compression type refrigerator |
| JP2005147467A (en) * | 2003-11-13 | 2005-06-09 | Matsushita Electric Ind Co Ltd | Heat pump heat source machine |
Cited By (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JP2009300000A (en) * | 2008-06-13 | 2009-12-24 | Sharp Corp | Refrigerator-freezer and cooling storage |
| JP2010085067A (en) * | 2008-10-02 | 2010-04-15 | Denso Corp | Refrigerating cycle device |
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